CN100564091C

CN100564091C - The control convenience of Vehicular drive system

Info

Publication number: CN100564091C
Application number: CNB2005800131030A
Authority: CN
Inventors: 田端淳; 多贺丰
Original assignee: Toyota Motor Corp
Current assignee: Toyota Motor Corp
Priority date: 2004-02-25
Filing date: 2005-02-23
Publication date: 2009-12-02
Anticipated expiration: 2025-02-23
Also published as: CN1946582A

Abstract

The operation of switching of gearshift that the invention discloses a kind of automobile-used speed-changing mechanism that can switch and be used to control this speed-changing mechanism between stepless change gearshift and step change gearshift is to reduce the control convenience that it switches vibrations and improves the durability degree of Coupling device.By optionally unclamping and engagement action of switch clutch (C0) under the control of switching control (50) and drg (B0), speed-changing mechanism (10) can switch between the stepless change gearshift of automatically controlled foundation and step change gearshift.Unclamp action when switching to the stepless change gearshift by switch clutch (C0) or drg (B0) under the control of switching control (50), first motor (M1) is controlled by motor control assembly (82), make and produce reactive torque by first motor, the reactive torque of switch clutch (C0) or drg (B0) is suitably replaced by the reactive torque of first motor (M1) thus, switching vibrations when switching to reduce speed-changing mechanism, and reduce poor between the input and output speed of Coupling device, the result reduces the load under its partial tooth engagement state on the Coupling device, and improves the durability degree of Coupling device thus.

Description

The control convenience of Vehicular drive system

Technical field

The present invention relates to the control convenience of Vehicular drive system, more specifically, relate to the control technology that drive system is switched between the stepless change gearshift of automatically controlled foundation and step change gearshift.

Background technology

Known have a kind of vehicle, be provided with the control convenience that is used for control-driven system, drive system comprises and is arranged as the power splitting mechanism that the output of driving engine is assigned to first motor and output shaft, and is arranged in second motor between the drive wheel of the output shaft of power splitting mechanism and vehicle.The example of this control convenience comprises as the patent documentation 1 disclosed control convenience that is used for motor vehicle driven by mixed power.In the disclosed drive system of hybrid power vehicle of this patent documentation, power splitting mechanism is made up of three rotating elements, first element is connected to driving engine, second element is connected to first motor, and three element is connected to second motor, make the main portion of the propulsive effort that produces by driving engine mechanically be directly delivered to drive wheel, the remainder of propulsive effort electrically is delivered to second motor from first motor by the circuit that is formed on it simultaneously, and drive system is controlled as and makes driving engine keep the optimized operation state, allows vehicle to travel with the fuel economy that improves.

Patent documentation 1:JP-2003-130202A

Patent documentation 2:JP-2003-130203A

Patent documentation 3:JP-2003-127681A

Patent documentation 4:JP-11-19868A

Patent documentation 5:JP-11-198670A

Patent documentation 6:JP-11-217025A

Patent documentation 7:WO 03/016749A1

Summary of the invention

The problem that the present invention solves

Usually, toric transmission is known to be the equipment that is used to improve the fuel economy of vehicle, and on the other hand, the planetary gear type power transmission device such as step change transmission is known to be the equipment with high power transmission efficiency.But, known without any being applicable to the Poewr transmission mechanism that improves fuel economy and power transmission efficiency.For example, having electric energy as disclosed conventional hybrid power car drive system in above-mentioned document can be delivered to the circuit of second motor from first motor by it, that is, the part of vehicle drive force is as the power transfer path of electric energy by its transmission.These drive systems require the first motor large scaleization under the situation that the demand output to driving engine increases, utilize second motor that moves from the electric energy of first motor generation also to be required large scaleization thus, this causes drive system to trend towards large scaleization unfriendly.Alternatively, the part of its driving engine output traditional Vehicular drive system of once being converted to electric energy and then being delivered to drive wheel has the risk in (for example, vehicle is with during running at high speed relatively) fuel economy deterioration under some travel conditions of vehicle.

Result as the expansion research of making great efforts to address the above problem, the inventor finds that first and second motors do not need to have large scale under the situation that driving engine moves with normality or low relatively output area, but under the situation that driving engine travels with the height output that peak output for example is provided is used for vehicle with the operation of high output area, the demand size of motor depends on demand capacity or output and increases.Based on this fact, the inventor also finds, make that by control-driven system the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path when driving engine moves with high output area, the demand size that can reduce first and second motors is so that compact driving system.The contriver also finds during the running at high speed of vehicle, mainly by the mechanical power bang path driving engine output being delivered to that drive wheel makes can be by reducing further to improve fuel economy by the loss from the part of driving engine output to the transformation of energy of electric energy that first motor carries out, and described electric energy is fed to second motor and is converted to mechanical energy to be delivered to drive wheel by second motor by circuit.So drive system can small-sized, and can be, drive system be switched between stepless change gearshift and step change gearshift suitably improve fuel economy by depending on the concrete situation of vehicle.Drive system comprises can operate connecting first the Coupling device of any two elements to the three element of power splitting mechanism, and/or can operate second element is fixed to the Coupling device of static component.Power splitting mechanism can be used as the electric steplessly variable transmission operation in by the stepless change gearshift of unclamping one or more Coupling devices foundation, and can be used as the step change transmission operation in the step change gearshift of setting up by one of engagement Coupling device or a plurality of Coupling devices.

Drive system is by unclamping or meshing Coupling device and switch between stepless change and step change gearshift.For example, drive system switches to the stepless change gearshift by unclamping Coupling device from the step change gearshift.In the case, the reactive torque of Coupling device in question reduces in it unclamps the process of action gradually, and the reactive torque of motor increases gradually simultaneously.Drive system suffers to switch the risk that vibrations take place, the opportunity that the reactive torque of Coupling device and motor changed when this depended on change action, the perhaps size of reactive torque when the change action of power splitting mechanism.That is, if the size of the reactive torque of opportunity that reactive torque changes during change action or motor is not controlled suitably, then drive system has and switches the risk that vibrations take place.In other words, the reactive torque of Coupling device is the torque of unclamping the driving engine that transmits by Coupling device in the process of action at it, if therefore the motor torque by the Coupling device transmission is not promptly replaced by the reactive torque of motor, then drive system may suffer to shake owing to the switching that the temporary transient change that is delivered to the motor torque of drive wheel causes.In addition, (that is, during the part slippage action of Coupling device bigger poor between) the input and output speed may cause the overload on the Coupling device to Coupling device, and this has brought the risk of Coupling device durability degree deterioration in it unclamps the process of action.

When drive system by the engagement Coupling device when the stepless change gearshift switches to the step change gearshift, Coupling device may suffer because the engagement that the big velocity contrast between interconnected two rotating elements causes by the engagement action of Coupling device shakes, and this velocity contrast is finished in engagement action becomes zero when establishing grade speed-change and gearshift state.In addition, (that is, during the part slippage of Coupling device action bigger difference may cause overload on the Coupling device to Coupling device between) the input and output speed, and this has also brought the risk of this Coupling device durability degree deterioration in the process of its engagement action.

Consider that above-mentioned background carried out the present invention.Therefore the purpose of this invention is to provide a kind of control convenience that is used for Vehicular drive system, the switching vibrations of drive system when it is set to reduce to switch between stepless change gearshift and step change gearshift, a kind of control convenience that is used for this drive system perhaps is provided, it is set to improve the durability degree of the Coupling device that is used for drive system switched and is provided with between two kinds of gearshift, drive system can be used as the electric steplessly variable transmission operation in stepless change gear shift shape, and drive system can be used as the step change transmission operation in the step change gearshift.

The means of dealing with problems

The present invention according to the 1st aspect, a kind of control convenience that is used for Vehicular drive system is provided, described Vehicular drive system is set to the output of driving engine is delivered to the drive wheel of vehicle, described control convenience comprises that (a) comprises the switchable type speed-changing mechanism of power splitting mechanism and Coupling device, described power splitting mechanism has first element that is fixed to described driving engine, be fixed to second element of first electrical motor and the three element that is fixed to second motor and power transfer member, described Coupling device can operate with described first to the three element any two be connected to each other also/or described second element is fixed to static component, described switchable type speed-changing mechanism can switch between stepless change gearshift and step change gearshift, can be used as electric steplessly variable transmission work at switchable type speed-changing mechanism described in the described stepless change gearshift, can be used as step change transmission work at switchable type speed-changing mechanism described in the described step change gearshift; (b) switching control, described switching control is used for based on the predetermined state of described vehicle described Coupling device being switched between releasing orientation and engagement, so that described switchable type speed-changing mechanism is optionally placed one of described stepless change gearshift and described step change gearshift; (c) motor control assembly, described motor control assembly is used to control described first motor producing reactive torque when the unclamping of described Coupling device, and/or reduce velocity contrast between described first element, described second element and the described three element or the velocity contrast between described second element and the described static component when the engagement of described Coupling device.

In this control convenience, motor control assembly is set to control first motor of the switchable type speed-changing mechanism that comprises power splitting mechanism and Coupling device, described power splitting mechanism has first element that is fixed to driving engine, is fixed to second element of first electrical motor and the three element that is fixed to second motor and power transfer member, described Coupling device can operate with first to the three element any two be connected to each other also/or second element is fixed to static component.The switchable type speed-changing mechanism can switch between stepless change gearshift and step change gearshift, the switchable type speed-changing mechanism can be used as electric steplessly variable transmission work in the stepless change gearshift, and the switchable type speed-changing mechanism can be used as step change transmission work in the step change gearshift.Motor control assembly is controlled first motor producing reactive torque when the unclamping of Coupling device, and/or reduce velocity contrast between first, second and the three element or the velocity contrast between second element and the static component when the engagement of Coupling device.Therefore, the reactive torque of Coupling device is replaced suitably by the reactive torque of first motor, has reduced the switching vibrations when the switchable type speed-changing mechanism switches thus.In addition, by reducing of the reactive torque of the reactive torque of first motor compensation Coupling device, still remain on engagement as Coupling device, reduced poor between the input and output speed of Coupling device thus, thereby reduced the load under its partial tooth engagement state on the Coupling device, the result has improved the durability degree of Coupling device.Alternatively, the rapid change of rotating element is to the value that will set up after switching to the step change gearshift, reduce thus because the switching vibrations that the velocity contrast the during engagement of Coupling device causes, and reduce Coupling device poor between the input and output speed under its partial tooth engagement state, thereby reduce the load on the Coupling device, the result has improved Coupling device.It shall yet further be noted that power splitting mechanism is made of simply three elements and Coupling device, and under the control of switching control the switchable type speed-changing mechanism is easily being switched between stepless change gearshift and step change gearshift by Coupling device.

In according to the preferred form of the present invention aspect the 2nd, described switching control can be worked to unclamp described Coupling device, with the described switchable type speed-changing mechanism stepless change gearshift that described first, second and three element relative to each other rotate that is placed in one, and can work meshing described Coupling device, described switchable type speed-changing mechanism is placed in one in described first, second and the three element, and any two elements are connected to each other or described second element keeps static described step change gearshift.This of switching control is provided with and allows the switchable type speed-changing mechanism easily to switch between stepless change gearshift and step change gearshift.

In according to the preferred form of the present invention aspect the 3rd, described switching control can be worked when described step change gearshift switches to described stepless change gearshift at described switchable type speed-changing mechanism, to begin the action of unclamping of described Coupling device after having produced reactive torque under by the control of described first motor at described motor control assembly.Be provided with according to this, the reactive torque of Coupling device is replaced suitably by the reactive torque of first motor, has reduced the switching vibrations when the switching of switchable type speed-changing mechanism thus.In addition, the reactive torque that is produced by first motor allows to control second component speeds suitably regardless of the reducing of reactive torque of Coupling device, has improved the durability degree of Coupling device thus.

In according to the preferred form of the present invention aspect the 4th, described switching control can be worked when described step change gearshift switches to described stepless change gearshift at described switchable type speed-changing mechanism, and described motor control assembly is controlled described first motor in the process of unclamping action under the control of described Coupling device at described switching control, makes the reactive torque of described first motor unclamp along with Coupling device and increases.Be provided with according to this, the reactive torque of Coupling device is suitably replaced by the reactive torque of first motor, has reduced the switching vibrations when the switchable type speed-changing mechanism switches thus.In addition, the reactive torque that is produced by first motor allows suitably to control second component speeds regardless of the reducing of reactive torque of Coupling device, improves the durability degree of Coupling device thus.

In according to the preferred form of the present invention aspect the 5th, the speed of described first motor of described motor control assembly controlled reset is to reduce velocity contrast between described first, second and the three element or the velocity contrast between described second element and the described static component.According to this setting, in the process of unclamping action of Coupling device, reduce velocity contrast between first, second and the three element or the velocity contrast between second element and the static component, the reactive torque of Coupling device is promptly replaced by the reactive torque of first motor thus.

In according to the preferred form of the present invention aspect the 6th, described motor control assembly is controlled the speed of described first motor, make velocity contrast between described first, second and the three element or the velocity contrast between described second element and the described static component maintain the value before the action beginning of unclamping of described Coupling device, finish up to unclamping action by described switching control control described.Be provided with according to this, the difference between the input and output speed of Coupling device in its partial tooth engagement state reduces, and up to finishing by unclamping action, has reduced the load that causes owing to skidding on the Coupling device thus, and the result has improved the durability degree of Coupling device.

In according to the preferred form of the present invention aspect the 7th, described switching control can be worked when described stepless change gearshift switches to described step change gearshift at described switchable type speed-changing mechanism, reduce to have been controlled to begin the engagement action of described Coupling device after the velocity contrast or the velocity contrast between described second element and the described static component between described first, second and the three element by described motor control assembly in the speed of described first motor.According to this setting, the speed of each rotating element is controlled to change to the value of setting up after switching to the step change gearshift, the switching vibrations that velocity contrast when having reduced the engagement of Coupling device thus causes, and reduced poor between the input and output speed of Coupling device, thereby reduced the load on the Coupling device, the result has improved the durability degree of Coupling device.

In according to the preferred form of the present invention aspect the 8th, described switching control can be worked when described stepless change gearshift switches to described step change gearshift at described switchable type speed-changing mechanism, with in by described motor control assembly the speed of described first motor being controlled, can carry out the engagement action of described Coupling device with the process that reduces velocity contrast between described first, second and the three element or the velocity contrast between described second element and the described static component.According to this setting, the speed of each rotating element is controlled to change to the value of setting up after switching to the step change gearshift, when having reduced the engagement of Coupling device thus because the switching that velocity contrast causes vibrations, and reduced Coupling device poor between the input and output speed under its partial tooth engagement state, thereby reduced the load on the Coupling device, the result has improved the durability degree of Coupling device.

In according to the preferred form of the present invention aspect the 9th, control convenience also comprises the engine output controller of the torque or the output that are used to control described driving engine, and described engine output controller limits the torque or the output of described driving engine, surpass the upper limit of determining by the rated value of described first motor with torque or the output that prevents described driving engine, finish up to the engagement action of the described Coupling device of controlling by described switching control.According to this setting, for example, the demand of travelling in response to the high output of vehicle at the switchable type speed-changing mechanism is when the stepless change gearshift switches to the step change gearshift, even first motor does not have high output area capacity corresponding or output with driving engine, the switchable type speed-changing mechanism was also suitably remained on its stepless change gearshift before switching to the step change gearshift.

In according to the preferred form of the present invention aspect the 10th, judge the described predetermined state of described vehicle based on the predetermined upper limit value of the moving velocity of described vehicle, and described switching control when being higher than described predetermined upper limit value, the actual value of the moving velocity of described vehicle places described step change gearshift with described switchable type speed-changing mechanism.Therefore, wherein actual vehicle speed at vehicle is higher than under the high speed form state of higher limit, the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path, compare with the situation under the stepless change gearshift thus, under the step change gearshift owing to mechanical energy and electric energy between the minimizing of conversion loss improved fuel economy.

Preferably, judge the predetermined state of vehicle based on the predetermined upper limit value of the moving velocity of vehicle, and switching control when being higher than predetermined upper limit value, the actual value of Vehicle Speed forbids that the switchable type speed-changing mechanism places the stepless change gearshift.Therefore, wherein actual vehicle speed at vehicle is higher than under the high-speed travel state of higher limit, prevent that the switchable type speed-changing mechanism from placing the stepless change gearshift, the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path thus, and compare with the situation under the stepless change gearshift, under the step change gearshift owing to mechanical energy and electric energy between the minimizing of conversion loss improved fuel economy.

In according to the of the present invention predetermined form aspect the 11st, judge the described predetermined state of described vehicle based on the predetermined upper limit value of the drive-force-related value of described vehicle, and described switching control when being higher than described predetermined upper limit value, the described drive-force-related value of described vehicle places described step change gearshift with described switchable type speed-changing mechanism.Be provided with according to this, when being higher than predetermined going up in limited time such as vehicle driver desired vehicle drive force or the drive-force-related value the actual vehicle propulsive effort, the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path.Therefore, can reduce the maximum of the electric energy that produce by first motor, can reduce the demand size of first motor thus, thereby can reduce to comprise the demand size of the Vehicular drive system of first motor.Drive-force-related value is and the direct or indirect relevant parameter of the propulsive effort of vehicle, for example the driving torque of the output torque of the output torque of driving engine, switchable type speed-changing mechanism, drive wheel, any other torque in the power transfer path or rotary driving force and the open angle of throttle gate of representing the driving engine of these torque values.Determine that the above-mentioned predetermined upper limit value of vehicle output judges whether vehicle is in high output motoring condition.

Preferably, judge the predetermined state of vehicle based on the predetermined upper limit value of the drive-force-related value of vehicle, and switching control when being higher than predetermined upper limit value, the actual value of the drive-force-related value of vehicle forbids that the switchable type speed-changing mechanism places the step change gearshift.According to this setting, be higher than when the drive-force-related value of the vehicle vehicle drive force desired or the actual propulsive effort under the height output motoring condition of predetermined upper limit value such as the vehicle driver, prevent that the switchable type speed-changing mechanism from placing the stepless change gearshift, can reduce a maximum demand of the electric energy that produce by first motor, and the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path, the demand size of first motor can be reduced thus, thereby the demand size of the Vehicular drive system of first motor can be reduced to comprise.

In according to the preferred form of the present invention aspect the 12nd, actual value based on the drive-force-related value of the actual value of the moving velocity of described vehicle and described vehicle, and according to run at high speed boundary line and high output that the handoff boundary line chart of being stored judges that the described predetermined state of described vehicle, described handoff boundary line chart comprise that parameter by the described moving velocity of described vehicle and described drive-force-related value form the defines boundary line of travelling.Be provided with according to this, can help whether vehicle is in the judgement of high-speed travel state or high output motoring condition.

In according to the preferred form of the present invention aspect the 13rd, the predetermined state of described vehicle is a function deterioration Rule of judgment, when being used for that described switchable type speed-changing mechanism placed any function deterioration of function unit of stepless change gearshift of automatically controlled foundation, described function deterioration Rule of judgment is just satisfied, and described switching control places described step change gearshift with described switchable type speed-changing mechanism when described function deterioration Rule of judgment satisfies.According to this layout, in the incident of judging the function deterioration when (it will forbid the switchable type speed-changing mechanism is placed the stepless change gearshift), speed-changing mechanism is placed in the step change gearshift, even make to exist under the situation of function deterioration that vehicle also can travel under the step change gearshift.

Preferably, the predetermined state of vehicle is a function deterioration Rule of judgment, this condition is satisfied when being used for that the switchable type speed-changing mechanism placed any function deterioration of function unit of stepless change gearshift of automatically controlled foundation, and switching control forbids that when function deterioration Rule of judgment satisfies the switchable type speed-changing mechanism places the step change gearshift.According to this setting, judging when being used for that the switchable type speed-changing mechanism placed the incident of function deterioration of any function unit of stepless change gearshift of automatically controlled foundation, prevent that the switchable type speed-changing mechanism is placed in the stepless change gearshift, even under the situation that has the function deterioration (it makes the switchable type speed-changing mechanism can not be placed in the stepless change gearshift), speed-changing mechanism is placed in the step change gearshift so that vehicle travels under the step change gearshift thus.

In according to the preferred form of the present invention aspect the 14th, described power splitting mechanism is a compound planet gear, and described first element is the planetary wheel carrier of described compound planet gear, described second element is the sun wheel of described compound planet gear, and the gear ring that described three element is described compound planet gear, and wherein said Coupling device comprises power-transfer clutch and/or drg, described power-transfer clutch can be worked with described planetary wheel carrier, any two elements in described sun wheel and the described gear ring are connected to each other, and described drg can be worked so that described sun wheel is fixed to described static component.Be provided with according to this, can reduce the axial dimension of power splitting mechanism, and can constitute power splitting mechanism simply by a compound planet gear.

In according to the preferred form of the present invention aspect the 15th, described compound planet gear is the single-stage planetary gear type.Be provided with according to this, can reduce the axial dimension of power splitting mechanism, and can constitute power splitting mechanism simply by a compound planet gear.

In according to the preferred form of the present invention aspect the 16th, described power splitting mechanism is a differential gear equipment, and described Coupling device comprises power-transfer clutch and/or drg, described power-transfer clutch can be worked so that any two elements in described first, second and the three element are connected to each other, and described drg can be worked so that described second element is fixed to described static component.Be provided with according to this, can reduce the axial dimension of power splitting mechanism, and can constitute power splitting mechanism simply by a compound planet gear.

In according to the preferred form of the present invention aspect the 17th, described differential gear equipment is the finishing bevel gear cuter formula.Be provided with according to this, can reduce the axial dimension of power splitting mechanism, and can constitute power splitting mechanism simply by a compound planet gear.

In according to the preferred form of the present invention aspect the 18th, described switching control meshes described power-transfer clutch so that described power splitting mechanism can be 1 change-speed box work as speed ratio, perhaps meshes described drg so that described power splitting mechanism can be as having the speedup change-speed box work that is lower than 1 speed ratio.According to this setting, easily control power splitting mechanism by switching control, optionally to come work as change-speed box with single fixed speed ratio or change-speed box with a plurality of fixed speed ratios.

In according to the preferred form of the present invention aspect the 19th, described switchable type speed-changing mechanism comprises automatic transmission with hydraulic torque converter and has the speed ratio of being determined by the speed ratio of described automatic transmission with hydraulic torque converter, and described automatic transmission with hydraulic torque converter is arranged in that parallel series is connected to described power splitting mechanism between described power transfer member and the described drive wheel.Be provided with according to this,, can obtain the vehicle drive force on the speed ratio of relative broad range by utilizing the speed ratio of automatic transmission with hydraulic torque converter.

In according to the preferred form of the present invention aspect the 20th, described switchable type speed-changing mechanism has the overall ratio that the speed ratio by the speed ratio of described power splitting mechanism and described automatic transmission with hydraulic torque converter defines.Be provided with according to this,, can obtain the vehicle drive force on the speed ratio of relative broad range, can improve the efficient of the stepless change gear shift control of power splitting mechanism thus by utilizing the speed ratio of automatic transmission with hydraulic torque converter.Preferably, automatic transmission with hydraulic torque converter is that a grade automatic transmission with hydraulic torque converter is arranged.In the case, power splitting mechanism and the cooperation of grade automatic transmission with hydraulic torque converter is arranged to set up stepless change gearshift and step change transmission gearshift, the switchable type speed-changing mechanism can be used as toric transmission work in the stepless change gearshift, and speed-changing mechanism is as a grade automatic transmission with hydraulic torque converter job is arranged in the step change gearshift.

In according to the preferred form of the present invention aspect the 21st, described automatic transmission with hydraulic torque converter is the step change automatic transmission with hydraulic torque converter according to the gear shift border line chart gear shift of being stored.Be provided with according to this, easily carry out the gear shift that grade automatic transmission with hydraulic torque converter is arranged.

Switching control preferably is set to based on the predetermined state of vehicle the switchable type speed-changing mechanism optionally be placed one of stepless change gearshift and step change gearshift.Promptly, switching control is controlled Coupling device to be used for the optionally switching between stepless change gearshift and step change gearshift of switchable type speed-changing mechanism based on vehicle condition, this Coupling device is incorporated in the power splitting mechanism of switchable type speed-changing mechanism and is set to connect first to the three element any two of power splitting mechanism, or second element is fixed to static component.Therefore, drive system not only has because the advantage that the fuel economy that the function of electric steplessly variable transmission is brought improves, and also has because the advantage of the high power transmission efficiency that step change transmission function that can the mechanical transfer vehicle drive force is brought.For example, when vehicle is in low speed or drive at moderate speed state, or be in when hanging down output or middle output motoring condition, the switchable type speed-changing mechanism is placed in the stepless change gearshift, improves the fuel economy of vehicle thus.On the other hand, when vehicle is in high-speed travel state, the switchable type speed-changing mechanism is placed in the step change gearshift that speed-changing mechanism wherein can be used as step change transmission work, and the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path, minimizing owing to energy conversion loss between mechanical energy and electric energy improves fuel economy thus, when transformation of energy between mechanical energy and the electric energy will take place during as electric steplessly variable transmission speed-changing mechanism.When vehicle was in height output motoring condition, the switchable type speed-changing mechanism was placed in the step change gearshift.So, speed-changing mechanism only vehicle be in low speed or drive at moderate speed state or when being in low output or middle output motoring condition just as electric steplessly variable transmission work, can reduce the demand that produces electric energy by motor thus, promptly, the maximum of the electric energy that must transmit from motor, make it can minimize the demand size of motor, and minimize the demand size of the drive system that comprises motor.

Preferably, the switchable type speed-changing mechanism is arranged so that second motor is directly connected to the motivation transmission member.Be provided with according to this, the demand output torque of power splitting mechanism can reduce with respect to the torque of the output shaft of above-mentioned automatic transmission with hydraulic torque converter, can reduce the demand size of second motor thus.

The present invention according to the 22nd aspect, a kind of control convenience that is used for Vehicular drive system is provided, described Vehicular drive system comprises that the differential partial sum is arranged in second motor in the power transfer path between the drive wheel of power transfer member and vehicle, described differential partly can be used as automatically controlled differential equipment work, and comprising to work is assigned to first motor and power transfer member and has the box of tricks of a plurality of rotating elements with the output with driving engine, described control convenience is characterised in that and comprises: (a) Coupling device, described Coupling device is arranged in the described box of tricks and can works so that described differential part is switched between differential state and lockup state, partly can be used as automatically controlled differential equipment work and can carry out differential function at differential described in the described differential state, can not carry out described differential function in the part of differential described in the described lockup state, (b) switching control, described switching control is used for based on the predetermined state of described vehicle described Coupling device being switched between releasing orientation and engagement, so that described differential part is optionally placed one of described stepless change gearshift and described step change gearshift, (c) motor control assembly, described motor control assembly is used to control described first motor producing reactive torque when described Coupling device unclamps, and/or reduce when described Coupling device engagement that described first motor is fixed to the upper among velocity contrast between described a plurality of rotating element or the described a plurality of rotating element rotating element and the velocity contrast between the static component.

According to this control convenience, switching control is set to based on the predetermined state of vehicle Coupling device be switched between releasing orientation and engagement, to be used for that the differential part is optionally placed one of described stepless change gearshift and described step change gearshift, differential partly can be used as automatically controlled differential equipment work and can carry out differential function in the differential state, and the differential part can not be carried out differential function in lockup state.

Because the predetermined state based on vehicle under the control of switching control optionally places one of differential state and lockup state with the differential part, the advantage that the fuel economy that the transmission function that electrically changes of its speed ratio brings so drive system not only has improves also has because the advantage of the high power transmission efficiency that the function of gear type power transmission device that can the mechanical transfer vehicle drive force is brought.For example, under the situation of the output area that is in the normal state at driving engine, when vehicle is in low speed or drives at moderate speed state, or be in when hanging down output or middle output motoring condition, differential partly is placed in the differential state, improves the fuel economy of vehicle thus.On the other hand, when vehicle is in high-speed travel state, differential partly is placed in the wherein output of driving engine mainly is delivered to drive wheel by the mechanical power bang path lockup state, minimizing owing to energy conversion loss between mechanical energy and electric energy improves fuel economy thus, when transformation of energy between mechanical energy and the electric energy will take place during as electric steplessly variable transmission speed-changing mechanism.When vehicle was in height output motoring condition, differential partly was placed in lockup state.So, the change-speed box work that differential part only is in low speed or drives at moderate speed state or just can electrically change as its speed ratio when being in low output or middle output motoring condition at vehicle, can reduce the demand of the electric energy that produces by motor thus, promptly, the maximum of the electric energy that must transmit from motor, make it can minimize the demand size of motor, and minimize the demand size of the drive system that comprises motor.

At this control convenience that is used for controlling the drive system that comprises the differential part that between differential state and lockup state, to switch, motor control assembly is set to control first motor, producing reactive torque when the unclamping of Coupling device, and/or to reduce velocity contrast between first, second and the three element or the velocity contrast between second element and the static component when the engagement of Coupling device.Therefore, when Coupling device unclamped, the reactive torque of Coupling device was suitably replaced by the reactive torque of first motor, the switching vibrations when having reduced the switching of differential part under switching control control thus.In addition, by reducing of the reactive torque of the reactive torque of first motor compensation Coupling device, still remain on engagement as Coupling device, reduce poor between the input and output speed of Coupling device thus, thereby reduce the load of Coupling device under its partial tooth engagement state, the result improves the durability degree of Coupling device.When Coupling device meshes, the speed of a plurality of rotating elements be changed to after the engagement action of Coupling device is finished (promptly, after differential partly switches to lockup state) value set up, reduced thus when the engagement of Coupling device because the switching that velocity contrast causes vibrations, and reduced Coupling device poor between the input and output speed under its partial tooth engagement state, thereby reduced the load on the Coupling device, the result has improved Coupling device.

In according to the preferred form of the present invention aspect the 23rd, described a plurality of rotating elements of described box of tricks comprise first element that is fixed to described driving engine, be fixed to second element of described first motor and be fixed to the three element of described power transfer member, and described Coupling device can work with connect described first to the three element any two elements, and/or described second element is fixed to described static component.Be provided with according to this, constitute the box of tricks that the differential part can be switched by three elements and Coupling device simply between differential state and lockup state.

In according to the preferred form of the present invention aspect the 24th, described switching control can be operated to unclamp described Coupling device described differential is partly placed described differential state, and can operate to mesh described Coupling device described differential is partly placed described lockup state, can relative to each other rotate in first, second and three element described in the described differential state, described first, second and three element keep static as one unit rotation or described second element under described lockup state.Be provided with according to this, by the Coupling device by switching control control, the differential part can easily be switched between differential state and lockup state.

Preferably, switching control can operate with based on the predetermined state of vehicle with Coupling device unclamp and engagement between switch, so that box of tricks is optionally placed differential state and lockup state, thus when differential mechanism places the differential state, differential partly places the differential state, and when differential mechanism placed lockup state, differential partly placed lockup state.In the case, the differential part is easily switched between differential state and lockup state.

In according to the preferred form of the present invention aspect the 25th, described switching control can be worked when described lockup state switches to described differential state in described differential part, to begin the action of unclamping of described Coupling device after producing reactive torque under by the control of described first motor at described motor control assembly.Be provided with according to this, the reactive torque of Coupling device is replaced suitably by the reactive torque of first motor, has reduced the switching vibrations when the switching of differential part thus.In addition, the reactive torque that is produced by first motor allows to control second component speeds suitably regardless of the reducing of reactive torque of Coupling device, has improved the durability degree of Coupling device thus.

In according to the preferred form of the present invention aspect the 26th, described switching control can be worked when described lockup state switches to described differential state in described differential part, and described motor control assembly is controlled described first motor in the process of unclamping action under the control of described Coupling device at described switching control, makes the reactive torque of described first motor unclamp along with Coupling device and increases.Be provided with according to this, the reactive torque of Coupling device is suitably replaced by the reactive torque of first motor, has reduced the switching vibrations when differential partly switches thus.In addition, the reactive torque that is produced by first motor allows suitably to control second component speeds regardless of the reducing of reactive torque of Coupling device, improves the durability degree of Coupling device thus.

In according to the preferred form of the present invention aspect the 27th, the speed of described first motor of described motor control assembly controlled reset is to reduce velocity contrast between described first, second and the three element or the velocity contrast between described second element and the described static component.According to this setting, in the process of unclamping action of Coupling device, reduce velocity contrast between first, second and the three element or the velocity contrast between second element and the static component, the reactive torque of Coupling device is promptly replaced by the reactive torque of first motor thus.

In according to the preferred form of the present invention aspect the 28th, described switching control is controlled the speed of described first motor, make velocity contrast between described first, second and the three element or the velocity contrast between described second element and the described static component maintain the value before the action beginning of unclamping of described Coupling device, finish up to unclamping action by described switching control control described.Be provided with according to this, the difference between the input and output speed of Coupling device in its partial tooth engagement state reduces, and up to finishing by unclamping action, has reduced the load that causes owing to skidding on the Coupling device thus, and the result has improved the durability degree of Coupling device.

In according to the preferred form of the present invention aspect the 29th, described switching control can be worked when described differential state switches to described lockup state in described differential part, reduce to have been controlled to begin the engagement action of described Coupling device after the velocity contrast or the velocity contrast between described second element and the described static component between described first, second and the three element by described motor control assembly in the speed of described first motor.According to this setting, the speed of each rotating element is controlled to change to the value of setting up after switching to the step change gearshift, the switching vibrations that velocity contrast when having reduced the engagement of Coupling device thus causes, and reduced Coupling device poor between the input and output speed under its partial tooth engagement state, thereby reduced the load on the Coupling device, the result has improved the durability degree of Coupling device.

In according to the preferred form of the present invention aspect the 30th, described switching control can be worked when described differential state switches to described lockup state in described differential part, with in by described motor control assembly the speed of described first motor being controlled, can carry out the engagement action of described Coupling device with the process that reduces velocity contrast between described first, second and the three element or the velocity contrast between described second element and the described static component.According to this setting, the speed of each rotating element is controlled to change to the value of setting up after switching to the step change gearshift, when having reduced the engagement of Coupling device thus because the switching that velocity contrast causes vibrations, and reduced Coupling device poor between the input and output speed under its partial tooth engagement state, thereby reduced the load on the Coupling device, the result has improved the durability degree of Coupling device.

In according to the preferred form of the present invention aspect the 31st, control convenience also comprises the engine output controller of the torque or the output that are used to control described driving engine, and wherein said engine output controller limits the torque or the output of described driving engine, surpass the upper limit of determining by the rated value of described first motor with torque or the output that prevents described driving engine, finish up to the engagement action of the described Coupling device of controlling by described switching control.According to this setting, for example, the demand of travelling in the high output of vehicle in the differential partial response is when the differential state switches to lockup state, even first motor does not have high output area capacity corresponding or output with driving engine, the differential part was also suitably remained on its differential state before switching to the step change gearshift.

In according to the preferred form of the present invention aspect the 32nd, judge the described predetermined state of described vehicle based on the predetermined upper limit value of the moving velocity of described vehicle, and described switching control when being higher than described predetermined upper limit value, the actual value of the moving velocity of described vehicle partly places described lockup state with described differential.Therefore, wherein actual vehicle speed at vehicle is higher than under the high speed form state of higher limit, the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path, compare with the situation under the stepless change gearshift thus, under the step change gearshift owing to mechanical energy and electric energy between the minimizing of conversion loss improved fuel economy.

Preferably, judge the predetermined state of vehicle based on the predetermined upper limit value of the moving velocity of vehicle, and switching control when being higher than predetermined upper limit value, the actual value of Vehicle Speed forbids that differential partly places the differential state.Therefore, wherein actual vehicle speed at vehicle is higher than under the high-speed travel state of higher limit, prevent that differential from partly placing the differential state, the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path thus, and compare with the situation under the differential state, the minimizing owing to conversion loss between mechanical energy and the electric energy under lockup state has improved fuel economy.

In according to the preferred form of the present invention aspect the 33rd, judge the described predetermined state of described vehicle based on the predetermined upper limit value of the drive-force-related value of described vehicle, and described switching control when being higher than described predetermined upper limit value, the described drive-force-related value of described vehicle partly places described lockup state with described differential.Be provided with according to this, when being higher than predetermined going up in limited time such as vehicle driver desired vehicle drive force or the drive-force-related value the actual vehicle propulsive effort, the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path.Therefore, can reduce the maximum of the electric energy that produce by first motor, can reduce the demand size of first motor thus, thereby can reduce to comprise the demand size of the Vehicular drive system of first motor.Drive-force-related value is and the direct or indirect relevant parameter of the propulsive effort of vehicle, for example the driving torque of the output torque of the output torque of driving engine, switchable type speed-changing mechanism, drive wheel, any other torque in the power transfer path or rotary driving force and the open angle of throttle gate of representing the driving engine of these torque values.Determine that the above-mentioned predetermined upper limit value of vehicle output judges whether vehicle is in high output motoring condition.

Preferably, judge the predetermined state of vehicle based on the predetermined upper limit value of the drive-force-related value of vehicle, and switching control when being higher than predetermined upper limit value, the actual value of the drive-force-related value of vehicle forbids that differential partly places lockup state.According to this setting, be higher than when the drive-force-related value of the vehicle vehicle drive force desired or the actual propulsive effort under the height output motoring condition of predetermined upper limit value such as the vehicle driver, prevent that the switchable type speed-changing mechanism from placing the differential state, can reduce a maximum demand of the electric energy that produce by first motor, and the output of driving engine mainly is delivered to drive wheel by the mechanical power bang path, the demand size of first motor can be reduced thus, thereby the demand size of the Vehicular drive system of first motor can be reduced to comprise.

In according to the preferred form of the present invention aspect the 34th, actual value based on the drive-force-related value of the actual value of the moving velocity of described vehicle and described vehicle, and according to run at high speed boundary line and high output that the handoff boundary line chart of being stored judges that the described predetermined state of described vehicle, described handoff boundary line chart comprise that parameter by the described moving velocity of described vehicle and described drive-force-related value form the defines boundary line of travelling.Be provided with according to this, can help whether vehicle is in the judgement of high-speed travel state or high output motoring condition.

In according to the preferred form of the present invention aspect the 35th, the predetermined state of described vehicle is a function deterioration Rule of judgment, when being used for making described differential part can be as any function deterioration of the function unit of automatically controlled differential equipment work the time, described function deterioration Rule of judgment is just satisfied, and described switching control partly places described lockup state with described differential when described function deterioration Rule of judgment satisfies.According to this layout, in the incident of judging the function deterioration when (it will forbid the switchable type speed-changing mechanism is placed the stepless change gearshift), speed-changing mechanism is placed in lockup state, even feasible the existence under the situation of function deterioration, vehicle also can travel under lockup state.

Preferably, the predetermined state of vehicle is a function deterioration Rule of judgment, this condition satisfies when being used for that the switchable type speed-changing mechanism placed any function deterioration of function unit of stepless change gearshift of automatically controlled foundation, and switching control will forbid that when function deterioration Rule of judgment satisfies differential partly places the step change gearshift.According to this setting, judging when being used for that differential partly placed the incident of function deterioration of any function unit of differential state, prevent that the switchable type speed-changing mechanism is placed in the differential state, even under the situation that has the function deterioration (it makes the differential part can not be placed in the differential state), differential partly is placed in lockup state so that vehicle travels under lockup state thus.

In according to the preferred form of the present invention aspect the 36th, described box of tricks is a compound planet gear, and described first element is the planetary wheel carrier of described compound planet gear, described second element is the sun wheel of described compound planet gear, and the gear ring that described three element is described compound planet gear, and described Coupling device comprises power-transfer clutch and/or drg, described power-transfer clutch can be worked so that any two elements in described planetary wheel carrier, described sun wheel and the described gear ring are connected to each other, and described drg can be worked so that described sun wheel is fixed to described static component.Be provided with according to this, can reduce the axial dimension of box of tricks, and can constitute box of tricks simply by a compound planet gear.

In according to the preferred form of the present invention aspect the 37th, described compound planet gear is the single-stage planetary gear type.Be provided with according to this, can reduce the axial dimension of box of tricks, and can constitute box of tricks simply by a compound planet gear.

In according to the preferred form of the present invention aspect the 38th, described box of tricks is a differential gear equipment, and described Coupling device comprises power-transfer clutch and/or drg, described power-transfer clutch can be worked so that any two elements in described first, second and the three element are connected to each other, and described drg can be worked so that described second element is fixed to described static component.According to this setting, can reduce power splitting mechanism, and can constitute power splitting mechanism simply by a differential gear equipment.

In according to the preferred form of the present invention aspect the 39th, described differential gear equipment is the finishing bevel gear cuter formula.Be provided with according to this, can reduce the axial dimension of box of tricks, and can constitute box of tricks simply by a finishing bevel gear cuter formula differential gear equipment.

In according to the preferred form of the present invention aspect the 40th, described switching control meshes described power-transfer clutch so that described box of tricks can be 1 change-speed box work as speed ratio, perhaps meshes described drg so that described box of tricks can be as having the speedup change-speed box work that is lower than 1 speed ratio.According to this setting, easily control box of tricks by switching control, optionally to come work as change-speed box with single fixed speed ratio or change-speed box with a plurality of fixed speed ratios.

In according to the preferred form of the present invention aspect the 41st, described power transfer path comprises the automatic transmission with hydraulic torque converter part, and described Vehicular drive system has the overall ratio that the speed ratio by the speed ratio of described automatic transmission with hydraulic torque converter part and described differential part defines.Be provided with according to this,, can obtain the vehicle drive force on the speed ratio of relative broad range by utilizing the speed ratio of automatic transmission with hydraulic torque converter.

In according to the preferred form of the present invention aspect the 42nd, described automatic transmission with hydraulic torque converter partly is the step change automatic transmission with hydraulic torque converter according to the gear shift border line chart gear shift of being stored.Be provided with according to this, easily carry out the gear shift that grade automatic transmission with hydraulic torque converter is arranged.

Preferably, but second motor directly is connected to power transfer member in the place of working.Be provided with according to this, the demand output torque of differential part can reduce with respect to the torque of automatic transmission with hydraulic torque converter output shaft partly, can reduce the demand size of second motor thus.

Description of drawings

Fig. 1 is the scheme drawing that is used to explain the layout of drive system of hybrid power vehicle according to an embodiment of the invention.

Fig. 2 is the table of gear shift action of drive system of hybrid power vehicle of the embodiment of presentation graphs 1, this drive system of hybrid power vehicle can with the various combination of the serviceability of the hydraulic operation friction Coupling device of realizing each gear shift action relatively, with stepless change gearshift and the operation of step change gearshift.

Fig. 3 is an alignment chart, is illustrated in the relative rotation speed of rotating element under different gears of the drive system of hybrid power vehicle of Fig. 1 embodiment that operates under the step change gearshift.

Fig. 4 is the figure of the input and output signal of expression control electronics, and the drive system of this control electronics with the embodiment of control chart 1 is set.

Fig. 5 is a functional block diagram of explaining the major control function of being carried out by the control electronics of Fig. 4.

Fig. 6 is a view of explaining the blocked operation of being carried out by the switching control of the control electronics among the embodiment of Fig. 5.

Fig. 7 is the view of expression institute storage map, and the boundary line in stepless change gear shift zone and step change gear shift zone has been defined in this expression, and it is used to illustrate the boundary line of being represented and defined stepless change gear shift zone and step change gear shift zone by the dotted line of Fig. 6.

Fig. 8 is the view as the example of the result's of the shift-up action of step change transmission engine speed variation.

Fig. 9 is the result who unclamps action who explains when as acceleration pedal, when speed-changing mechanism switches to the stepless change gearshift from the step change gearshift, and the diagram of circuit of the major control operation of carrying out by the control electronics of Fig. 4.

Figure 10 is the sequential chart that is used to explain the control operation of the Fig. 9 that carries out when the step change gearshift switches to the stepless change gearshift by the unclamping action of switch clutch under the situation of unclamping of speed-changing mechanism at acceleration pedal.

Figure 11 is the sequential chart that is used to explain the control operation of the Fig. 9 that carries out when the step change gearshift switches to the stepless change gearshift by switching the unclamping action of drg under the situation of unclamping of speed-changing mechanism at acceleration pedal.

Figure 12 is the result who unclamps action who explains when as acceleration pedal, switchable type change-speed box part when lockup state switches to non-lockup state, the diagram of circuit of the major control operation of carrying out by the control electronics of Fig. 4.

Figure 13 is the sequential chart that is used to explain the control operation of the Figure 12 that carries out when lockup state switches to non-lockup state by the unclamping action of switch clutch under the situation of unclamping of speed-changing mechanism at acceleration pedal.

Figure 14 be used to explain when under the situation of unclamping of speed-changing mechanism at acceleration pedal by switch clutch unclamp action when the step change gearshift switches to the stepless change gearshift, at the sequential chart that as embodiment is the control operation of Fig. 9 of carrying out among the embodiment of possibility to Figure 10.

Figure 15 is used to explain when unclamping action when the step change gearshift switches to the stepless change gearshift by what switch drg under the situation of unclamping of speed-changing mechanism at acceleration pedal, at the sequential chart that as the embodiment to Figure 10 is the control operation of Fig. 9 of carrying out among the embodiment of possibility.

Figure 16 be used to explain when under the situation of unclamping of speed-changing mechanism at acceleration pedal by switch clutch unclamp action when lockup state switches to non-lockup state, at the sequential chart that as embodiment is the control operation of Figure 12 of carrying out among the embodiment of possibility to Figure 13.

Figure 17 is the result who explains when as the push action of acceleration pedal, switchable type change-speed box part when the stepless change gearshift switches to the step change gearshift, the diagram of circuit of the major control operation of carrying out by the control electronics of Fig. 4.

Figure 18 is used to explain replace blocked operation shown in Figure 6, the view of the blocked operation of being carried out by the switching control of the control electronics of the embodiment of Fig. 5.

Figure 19 is the sequential chart that is used to explain the control operation of the Figure 17 that carries out when the stepless change gearshift switches to the step change gearshift by the engagement action of switch clutch under the situation of pushing of speed-changing mechanism at acceleration pedal.

Figure 20 is the sequential chart that is used to explain the control operation of the Figure 17 that carries out when the stepless change gearshift switches to the step change gearshift by the engagement action of switching drg under the situation of pushing of speed-changing mechanism at acceleration pedal.

Figure 21 is the result who explains when as the push action of acceleration pedal, switchable type change-speed box part when non-lockup state switches to lockup state, the diagram of circuit of the major control operation of carrying out by the control electronics of Fig. 4.

Figure 22 is the sequential chart that is used to explain the control operation of the Figure 21 that carries out when non-lockup state switches to lockup state by the engagement action of switch clutch under the situation of pushing of speed-changing mechanism at acceleration pedal.

Figure 23 be used to explain when under the situation of pushing of speed-changing mechanism at acceleration pedal by switch clutch unclamp action when the step change gearshift switches to the stepless change gearshift, at the sequential chart that as embodiment is the control operation of Figure 17 of carrying out among the embodiment of possibility to Figure 19.

Figure 24 be used to explain when the engagement action by switching drg under the situation of pushing of speed-changing mechanism at acceleration pedal when the stepless change gearshift switches to the step change gearshift, at the sequential chart that as embodiment is the control operation of Figure 17 of carrying out among the embodiment of possibility to Figure 20.

Figure 25 be used to explain when the engagement action by switch clutch under the situation of pushing of speed-changing mechanism at acceleration pedal when non-lockup state switches to lockup state, at the sequential chart that as embodiment is the control operation of Figure 21 of carrying out among the embodiment of possibility to Figure 22.

Figure 26 is and the cooresponding scheme drawing of Fig. 1, shows the layout of drive system of hybrid power vehicle in accordance with another embodiment of the present invention.

Figure 27 is and the cooresponding table of Fig. 2, the gear shift action of the drive system of hybrid power vehicle of the embodiment of expression Figure 26, this drive system of hybrid power vehicle can with the various combination of the serviceability of the hydraulic operation friction Coupling device of realizing each gear shift action relatively, with stepless change gearshift and the operation of step change gearshift.

Figure 28 is and the cooresponding alignment chart of Fig. 3 to be illustrated in the relative rotation speed of rotating element under different gears of the drive system of hybrid power vehicle of Figure 26 embodiment that operates under the step change gearshift.

Figure 29 is the scheme drawing that is used for explaining the power splitting mechanism that is arranged on switchable type change-speed box part according to still another embodiment of the invention, the power splitting mechanism of the switchable type change-speed box part among the embodiment of this power splitting mechanism replacement Fig. 1.

Figure 30 illustrates the view that the manually operated gearshift that adopts mutual change type switch 44 forms is selected equipment, and this gearshift selection equipment is provided as the switching device that is used for the selective speed gear shift state.

The specific embodiment

Describe the preferred embodiments of the present invention with reference to the accompanying drawings in detail.

First embodiment

Fig. 1 is the switchable type speed-changing mechanism 10 that is set to be used for the speed-changing mechanism of hybrid vehicle (below be called speed-changing mechanism 10), and this speed-changing mechanism is by control convenience control according to an embodiment of the invention.As shown in Figure 1, speed-changing mechanism 10 comprises: adopt the input rotating member of input shaft 14 forms, it is arranged on the common axis in the mission case 12, and casing 12 is as the static component that is installed on the vehicle body; Adopt the differential part of switchable type change-speed box part 11 forms, it directly or via unshowned pulsation absorption damper (vibration damping equipment) is connected to input shaft 14 indirectly; As the automatic transmission with hydraulic torque converter part 20 that grade automatic transmission with hydraulic torque converter is arranged, it is arranged between the switchable type change-speed box part 11 and drive wheel 38 (as shown in Figure 5) of vehicle, and is connected in series to switchable type change-speed box part 11 and drive wheel 38 by Poewr transmission mechanism 18; And the output rotating member that adopts output shaft 22 forms, it is connected to automatic transmission with hydraulic torque converter part 20.Input shaft 12, switchable type change-speed box part 11, automatic transmission with hydraulic torque converter part 20 are one another in series with output shaft 22 and are connected.As shown in Figure 5, this speed-changing mechanism 10 is suitable for horizontal FR vehicle (engine behind front wheel rear-guard vehicle), and be arranged in the driving propulsion source of driving engine 8 forms and this is between the drive wheel 38, by differential gear equipment 36 (final reduction gear) and a pair of axle drive shaft vehicle drive force is delivered to this to drive wheel 38 from driving engine 8.Note, in Fig. 1, omitted the latter half with respect to the speed-changing mechanism 10 of its axis symmetric construction.Like this too among other embodiment of Shuo Ming each below.

Switchable type change-speed box part 11 comprises: first motor M 1; As the power splitting mechanism 16 of box of tricks, it can be operated and will mechanically be assigned to first motor M 1 and power transfer member 18 by the output of the driving engine 8 of input shaft 14 receptions; With and the axle shaft can be with second motor M 2 of power transfer member 18 rotation.Second motor M 2 can be arranged in any position of the power transfer path between power transfer member 18 and the drive wheel 38.Being used for first motor M 1 of present embodiment and each of second motor M 2 all is the so-called dynamoelectric machine with motor function and generator function.But first motor M 1 should be used as the electrical generator that can operate with generation electric energy and antagonistic force at least, and second motor M 2 should be at least as operating the driving propulsion source that produces vehicle drive force.

Power splitting mechanism 16 comprise as major part with lower member, have first compound planet gear 24, the switch clutch C0 of the single-stage planetary gear type of for example about 0.418 transmitting ratio ρ 1 and switch drg B0.First compound planet gear 24 has rotating element, comprising: the first sun wheel S1; The first planetary wheel P1; The first planetary wheel carrier CA1, it supports the first planetary wheel P1 can and can rotate the planetary wheel P1 that wins around its axis rotation around the axis of the first sun wheel S1; With by the first planetary wheel P1 and the first sun wheel S1 ingear, the first gear ring R1.Under the situation that the number of teeth of the first sun wheel S1 and the first gear ring R1 is represented by ZS1 and ZR1 respectively, above-mentioned transmitting ratio ρ 1 is represented by ZS1/ZR1.

In power splitting mechanism 16, the first planetary wheel carrier CA1 is connected to input shaft 14, promptly is connected to driving engine 8, and the first sun wheel S1 is connected to first motor M 1, and the first gear ring R1 is connected to power transfer member 18.Switch drg B0 and be arranged between the first sun wheel S1 and the mission case 12, and switch clutch C0 is arranged between the first sun wheel S1 and the first planetary wheel carrier CA1.When switch clutch C0 and drg B0 unclamp, power splitting mechanism 16 is placed in the differential state, in this differential state, the first sun wheel S1, the first planetary wheel carrier CA1 and the first gear ring R1 as three rotating elements (three elements) of first compound planet gear 24 are relative to each other rotatable, to carry out differential function, make the output of driving engine 8 be assigned to first motor M 1 and power transfer member 18, the output of the part of driving engine 8 is used to drive first motor M 1 and produces electric energy thus, and this electric energy is stored or is used for driving second motor M 2.So, switchable type change-speed box part 11 is placed in stepless change gearshift (the CVT state of automatically controlled foundation), in this stepless change gearshift, change-speed box part 11 plays automatically controlled differential equipment, and the rotating speed of power transfer member 18 can change and continuously regardless of the rotating speed of driving engine 8.Promptly, when power splitting mechanism 16 is placed in the differential state, switchable type change-speed box part 11 also is placed in the differential state, to be placed in the stepless change gearshift in other words, change-speed box part 11 can vary continuously to the electric steplessly variable transmission of maxim γ 0max from minimum value γ 0min as its speed ratio γ 0 (rotating speed of the rotating speed/power transfer member 18 of input shaft 14) in this stepless change gearshift.

During vehicle travels along with the output of driving engine, when when switchable type change-speed box part 11 is placed in the stepless change gearshift, making switch clutch C0 or drg B0 engagement, power splitting mechanism 16 enters non-differential state or lockup state, and differential function is unavailable in this state.More specifically, when switch clutch C0 meshes, the first sun wheel S1 connects together with the first planetary wheel carrier CA1, make power splitting mechanism 16 be placed in lockup state or non-differential state, wherein three rotating elements that comprise the first sun wheel S1, the first planetary wheel carrier CA1 and the first gear ring R1 of first compound planet gear 24 can be used as the one unit rotation, make switchable type change-speed box part 11 also be placed in non-differential state.Under this non-differential state, the rotating speed of the rotating speed of driving engine 8 and power transfer member 18 is equal to each other, therefore switchable type change-speed box part 11 is placed in fixed speed ratio gearshift or step change gearshift, and wherein change-speed box part 11 is as having the change-speed box that equals 1 fixed speed ratio γ 0.When switching drg B0 replaces switch clutch C0 to be engaged, the first sun wheel S1 is fixed to mission case 12, make power splitting mechanism 16 be placed in wherein non-rotatable locking of the first sun wheel S1 or non-differential state, and switchable type change-speed box part 11 also is placed in non-differential state.Because make the rotating speed of the gear ring R1 that wins be higher than the rotating speed of the first planetary wheel carrier CA1, so power splitting mechanism 16 is as speed increasing mechanism, and switchable type change-speed box part 11 is placed in fixed speed ratio gearshift or step change gearshift, and wherein change-speed box part 11 is as the speedup change-speed box that has than 1 little fixed speed ratio γ 0 (for example about 0.7).

So switch clutch C0 and switching drg B0 are as the Coupling device that serves as the differential state switching device, it can be operated and optionally power splitting mechanism 16 be placed differential state (non-lockup state) and lockup state (non-differential state).Promptly, switch clutch C0 and switching drg B0 serve as Coupling device, this Coupling device can be operated so that switchable type change-speed box part 11 is optionally switched between differential state (non-lockup state) and lockup state (non-differential state), change-speed box part 11 can be used as the automatically controlled differential gear with differential function and comes work under the differential state, and this differential function is unavailable under lockup state.For example, the Coupling device of switch clutch C0 and drg B0 form is arranged as switchable type change-speed box part 11 is optionally switched between differential state and lockup state, but change-speed box part 11 can be used as its speed ratio continually varying toric transmission work under this differential state, and change-speed box part 11 can not be as electric steplessly variable transmission work and the constant fixed value that remains on of speed ratio under this lockup state.In other words, switch clutch C0 and drg B0 are arranged as change-speed box part 11 are optionally switched between stepless change gearshift and fixed speed ratio gearshift, speed ratio can change on automatically controlled ground continuously under the stepless change gearshift, and change-speed box 11 can be used as and comprises the single gear with a speed ratio or have separately that the change-speed box of a plurality of gears of speed ratio comes work under the fixed speed ratio gearshift.

Automatic transmission with hydraulic torque converter part 20 comprises single-stage planetary gear type second compound planet gear 26, single-stage planetary gear type the third line star gear cluster 28 and single-stage planetary gear type fourth line star gear cluster 30.Second compound planet gear 26 has: the second sun wheel S2; The second planetary wheel P2; The second planetary wheel carrier CA2, it supports the second planetary wheel P2 makes the second planetary wheel P2 and can rotate around the axis of the second sun wheel S2 around its axis rotation; With by the second planetary wheel P2 and the second sun wheel S2 ingear, the second gear ring R2.For example, second compound planet gear 26 has about 0.562 transmitting ratio ρ 2.The third line star gear cluster 28 has: the 3rd sun wheel S3; The third line star gear P3; The third line star wheel frame CA3, it supports the third line star gear P3 makes the third line star gear P3 and can rotate around the axis of the 3rd sun wheel S3 around its axis rotation; With by the third line star gear P3 and the 3rd sun wheel S3 ingear the 3rd gear ring R3.For example, the third line star gear cluster 28 has about 0.425 transmitting ratio ρ 3.Fourth line star gear cluster 30 has: the 4th sun wheel S4; Fourth line star gear P4; Fourth line star wheel frame CA4, it supports fourth line star gear P4 makes fourth line star gear P4 and can rotate around the axis of the 4th sun wheel S4 around its axis rotation; With by fourth line star gear P4 and the 4th sun wheel S4 ingear the 4th gear ring R4.For example, fourth line star gear cluster 30 has about 0.421 transmitting ratio ρ 4.Under the situation that the number of teeth of the second sun wheel S2, the second gear ring R2, the 3rd sun wheel S3, the 3rd gear ring R3, the 4th sun wheel S4 and the 4th gear ring R4 is represented by ZS2, ZR2, ZS3, ZR3, ZS4 and ZR4 respectively, above-mentioned transmitting ratio ρ 2, ρ 3 and ρ 4 are represented by ZS2/ZR2, ZS 3/ZR3 and ZS4/ZR4 respectively.

In automatic transmission with hydraulic torque converter part 20, the second sun wheel S2 and the 3rd sun wheel S3 are fixed to one another integratedly as one unit, optionally be connected to power transfer member 18 by second clutch C2, and optionally be fixed to casing 12 by the first drg B1.The second planetary wheel carrier CA2 optionally is fixed to mission case 12 by the second drg B2, and the 4th gear ring R4 optionally is fixed to mission case 12 by the 3rd drg B3.The second gear ring R2, the third line star wheel frame CA3 and fourth line star wheel frame CA4 are fixed to one another integratedly and be fixed to output shaft 22.The 3rd gear ring R3 and the 4th sun wheel S4 are fixed to one another integratedly, and optionally are connected to power transfer member 18 by first clutch C1.

Above-mentioned switch clutch C0, first clutch C1, second clutch C2, switching drg B0, the first drg B1, the second drg B2 and the 3rd drg B3 are the hydraulic operation friction Coupling devices that uses in traditional automatic transmission for vehicles.In these friction Coupling devices each all is made of the multi-disc wet clutch that comprises a plurality of friction discs, described a plurality of friction disc is pressed against each other by hydraulic actuator, perhaps be made of the external contracting drum brake that comprises a rotary drum and a band or two bands, described band is wrapped on the outer surface of rotary drum and at one end by the hydraulic actuator tensioning.Among power-transfer clutch C0-C2 and the drg B0-B3 each is optionally meshed, and to connect each power-transfer clutch or drg is placed therebetween two members.

As shown in the table of Fig. 2, in the speed-changing mechanism 10 of constructing as mentioned above, by from above-mentioned switch clutch C0, first clutch C1, second clutch C2, switch the engagement action of the respective combination of the friction Coupling device of selecting drg B0, the first drg B1, the second drg B2 and the 3rd drg B3, optionally set up first gear (the first fast position) to the 5th gear (the 5th fast position), backing car gear (activation point backward) and Neutral Position one of them.These gears have into different speed ratio γ (the drive shaft speed N that geometric series changes _IN/ output shaft speed N _OUT).Especially, notice that power splitting mechanism 16 is provided with switch clutch C0 and drg B0, therefore as mentioned above, switchable type change-speed box part 11 can be selectively placed on fixed speed ratio gearshift and stepless change gearshift by the engagement of switch clutch C0 and switching drg B0, mechanism 16 can be used as its speed ratio and keeps constant change-speed box to come work under the fixed speed ratio gearshift, and mechanism 16 can be used as toric transmission and comes work under the stepless change gearshift.Therefore, in this speed-changing mechanism 10, by automatic transmission with hydraulic torque converter part 20 and by engagement switch clutch C0 or switch the toric transmission part 11 that drg B0 is placed in the fixed speed ratio gearshift and constitute step change transmission.In addition, by automatic transmission with hydraulic torque converter part 20 and when switch clutch C0 and drg B0 all are not engaged and the toric transmission part 11 that is placed in the stepless change gearshift constitutes toric transmission.In other words, speed-changing mechanism 10 is switched to the step change gearshift by engagement switch clutch C0 and of switching among the drg B0, and by unclamping switch clutch C0 and drg B0 is switched to the stepless change gearshift.Switchable type change-speed box part 11 also is regarded as the change-speed box that can switch between step change gearshift and stepless change gearshift.

Be used as under the situation of step change transmission at speed-changing mechanism 10, for example, as shown in Figure 2, engagement action by switch clutch C0, first clutch C1 and the 3rd drg B3 set up have for example about 3.357 the most at a high speed than first gear of γ 1, and set up second gear by the engagement action of switch clutch C0, first clutch C1 and the second drg B2 with speed ratio γ 2 (being lower than speed ratio γ 1) of for example about 2.180.In addition, set up third gear by the engagement action of switch clutch C0, first clutch C1 and the first drg B1, and set up fourth speed position with speed ratio γ 4 (being lower than speed ratio γ 3) of for example about 1.000 by the engagement action of switch clutch C0, first clutch C1 and second clutch C2 with speed ratio γ 3 (being lower than speed ratio γ 2) of for example about 1.424.Set up the 5th gear with speed ratio γ 5 (being lower than speed ratio γ 4) of for example about 0.705 by first clutch C1, second clutch C2 and the engagement action of switching drg B0.In addition, the engagement action by second clutch C2 and the 3rd drg B3 is set up the backing car gear with speed ratio γ R (it is between speed ratio γ 1 and γ 2) of for example about 3.209.Set up Neutral Position N by only meshing switch clutch C0.

On the other hand, be used as under the situation of toric transmission at speed-changing mechanism 10, as shown in Figure 2, switch clutch C0 and switching drg B0 both are released, make toric transmission part 11 as toric transmission, the automatic transmission with hydraulic torque converter part 20 that is connected in series to switchable type change-speed box part 11 simultaneously is as step change transmission, be delivered to first the speed that rotatablely moves (being the rotating speed of power transfer member 18) that is placed in thus and changed continuously, make that the speed ratio of drive system can change continuously when automatic transmission with hydraulic torque converter part 20 is placed in one of these gears on preset range to the automatic transmission with hydraulic torque converter part 20 of one of fourth speed position.So the speed ratio of automatic transmission with hydraulic torque converter part 20 can change on whole adjacent gear continuously, the overall ratio γ T of speed-changing mechanism 10 can change continuously thus.

The alignment chart of Fig. 3 is illustrated in the relation between the rotating speed of rotating element in each gear of speed-changing mechanism 10 with straight line, speed-changing mechanism 10 is by constituting as the switchable type change-speed box part 11 of stepless change gear shift part or first gear shift part and as the automatic transmission with hydraulic torque converter part 20 of step change gear shift part or second gear shift part.The alignment chart of Fig. 3 is the rectangle two-dimensional coordinate system, and wherein the transmitting ratio ρ of compound planet gear 24,26,28,30 is taken as along transverse axis, and the relative rotation speed of rotating element is taken as along the longitudinal axis.Article three, lower one among horizon X1, X2, the XG, promptly horizon X1 represents 0 rotating speed, and in three horizons by last one, promptly horizon X2 represents 1.0 rotating speed, promptly is connected to the running velocity NE of the driving engine 8 of input shaft 14.Horizon XG represents the rotating speed of power transfer member 18.The relative rotation speed of the 3rd rotating element (three element) RE3 of second rotating element (second element) RE2 that represents the first sun wheel S1 form respectively corresponding to three perpendicular line Y1, Y2 and the Y3 of the power splitting mechanism 16 of switchable type change-speed box part 11, first rotating element (first element) RE1 of the first planetary wheel carrier CA1 form and the first gear ring R1 form.Distance between adjacent perpendicular line Y1, Y2 and the Y3 is determined by the transmitting ratio ρ 1 of first compound planet gear 24.That is, the distance between vertical curve Y1 and the Y2 is corresponding to " 1 ", and the distance between vertical curve Y2 and the Y3 is corresponding to transmitting ratio ρ 1 simultaneously.In addition, corresponding to five perpendicular line Y4 of automatic transmission with hydraulic torque converter part 20, Y5, Y6, Y7 and Y8 represent to adopt the second and the 3rd sun wheel S2 fixed to one another integratedly respectively, the 4th rotating element (quaternary part) RE4 of S3 form, the 5th rotating element of the second planetary wheel carrier CA2 form (the 5th element) RE5, the 6th rotating element (the hexa-atomic) RE6 of the 4th gear ring R4 form, adopt the second gear ring R2 fixed to one another integratedly and the third and fourth planetary wheel carrier CA3, the 7th rotating element of CA4 form (the 7th element) RE7, and the relative rotation speed that adopts the 8th rotating element (the 8th element) RE8 of the 3rd gear ring R3 fixed to one another integratedly and the 4th sun wheel S4 form.Distance between the adjacent perpendicular line Y4-Y8 is determined by transmitting ratio ρ 2, ρ 3 and the ρ 4 of second, third and fourth line star gear cluster 26,28,30.Promptly, sun wheel of each and the distance between the planetary wheel carrier be corresponding to " 1 " in second, third and the fourth line star gear cluster 26,28,30, and in these compound planet gears 26,28,30 planetary wheel carrier of each and the distance between the gear ring corresponding to transmitting ratio ρ.

Alignment chart with reference to Fig. 3, the power splitting mechanism 16 of speed-changing mechanism 10 is arranged to: the first planetary wheel carrier CA1 as one of three rotating elements of first compound planet gear 24 is fixed to input shaft 14 integratedly, and optionally be connected to another rotating element of the first sun wheel S1 form by switch clutch C0, and the rotating element of this first sun wheel S1 form is connected to first motor M 1, and optionally be fixed to mission case drive wheel 12 by switching drg B0, and the 3rd rotating element of the first gear ring R1 form is fixed to the power transfer member 18 and second motor M 2, makes rotatablely moving of input shaft 14 be delivered to automatic transmission with hydraulic torque converter 20 (step change transmission part) by power transfer member 18.Relation between the rotating speed of the first sun wheel S1 and the first gear ring R1 is represented by the angled straight lines L0 through the intersection point between line Y2 and the X2.For example, when power splitting mechanism 16 is unclamped action when entering the stepless change gearshift by switch clutch C0 and drg B0, the antagonistic force that produces by the running of the generation electric energy of first motor M 1 by control, improve or reduce the rotating speed by the first represented sun wheel S1 of the intersection point between line L0 and the vertical curve Y1, feasible rotating speed by the first represented gear ring R1 of the intersection point between line L0 and the vertical curve Y3 reduces or raises.When switch clutch C0 meshes, the first sun wheel S1 and the first planetary wheel carrier CA1 are connected to each other, and power splitting mechanism 16 is placed in the non-differential state of wherein above-mentioned three rotating elements as the one unit rotation, line L0 aims at horizon X2 thus, makes Poewr transmission mechanism 18 rotate with the speed that equates with engine speed NE.On the other hand, when switching drg B0 engagement, the rotation of the first sun wheel S1 stops, and power splitting mechanism 16 is placed in non-differential state and is used as speed increasing mechanism, make line L0 tilt with as shown in Figure 3 state, thus, feasible rotating speed (being the rotating speed of power transfer member 18) by the first represented ring gear R1 of the intersection point between line L0 and the Y3 is higher than engine speed NE and is delivered to automatic transmission with hydraulic torque converter part 20.

When first clutch C1 and the 3rd drg B3 engagement, automatic transmission with hydraulic torque converter part 20 is placed in first gear.As shown in Figure 3, the rotating speed of output shaft 22 is fixed to the perpendicular line Y7 of rotating speed of the 7th rotating element RE7 of output shaft 22 and the intersection point between the angled straight lines L1 is represented in first gear by expression, and angled straight lines L1 is through the perpendicular line Y8 and the intersection point between the horizon X2 of expression the 8th rotating element RE8 rotating speed and represent the perpendicular line Y6 of the 6th rotating element RE6 rotating speed and the intersection point between the horizon X1.Similarly, the rotating speed of the output shaft 22 in second gear that the engagement action by the first clutch C1 and the second drg B2 is set up is represented by the intersection point between the perpendicular line Y7 of the rotating speed of the 7th rotating element RE7 that is fixed to output shaft 22 by determined angled straight lines L2 of these engagement action and expression.The rotating speed of the output shaft 22 in the third gear that the engagement action by the first clutch C1 and the first drg B1 is set up is represented by the intersection point between the perpendicular line Y7 of the rotating speed of the 7th rotating element RE7 that is fixed to output shaft 22 by determined angled straight lines L3 of these engagement action and expression.The rotating speed of the output shaft 22 in the fourth speed position that the engagement action by first clutch C1 and second clutch C2 is set up is represented by the intersection point between the perpendicular line Y7 of the rotating speed of the 7th rotating element RE7 that is fixed to output shaft 22 by determined horizontal line L 4 of these engagement action and expression.First gear that is placed in engagement at switch clutch C0 is to the fourth speed position, and under the situation of the propulsive effort that receives from power splitting mechanism 16, the 8th rotating element RE8 is with the speed rotation identical with engine speed NE.When switching drg B0 replacement switch clutch C0 engagement, under the situation of the propulsive effort that receives from power splitting mechanism 16, the 8th rotating element RE8 is to be higher than the speed rotation of engine speed NE.By first clutch C1, second clutch C2 with switch the rotating speed of the output shaft 22 in the 5th gear that the engagement action of drg B0 sets up, represent by the intersection point between the perpendicular line Y7 of the rotating speed of the 7th rotating element RE7 that is fixed to output shaft 22 by determined horizontal line L 5 of these engagement action and expression.

Fig. 4 illustrates signal that is received by the control electronics 40 that is provided for controlling speed-changing mechanism 10 and the signal that is produced by control electronics 40.This control electronics 40 comprise have CPU, the so-called microcomputer of ROM, RAM and input/output interface, and handle these signals according to the program that is stored among the ROM when being provided in the ephemeral data memory function of utilizing RAM, realizing the hybrid power drive controlling of driving engine 8 and motor M 1 and M2, and the drive controlling of the gear shift control and so on of automatic transmission with hydraulic torque converter part 20 for example.

Control electronics 40 is configured to receive various signals from various sensors shown in Figure 4 and switch, for example: the signal of the cooling water temperature of expression driving engine; The output signal of the current selected operating position of expression gear shifting handle; The running velocity N of expression driving engine 8 _ESignal; The signal of selected group value of the forerunner position of speed-changing mechanism 10 is represented in expression; The signal of expression M pattern (motor drive mode); The signal of expression air-conditioning serviceability; The signal of the corresponding speed of a motor vehicle of rotating speed of expression and output shaft 22; The signal of the temperature of the power fluid of expression automatic transmission with hydraulic torque converter part 20; The signal of the serviceability of expression Parking Brake; The signal of the serviceability of expression foot-operated brake; The signal of expression catalyst temperature; The signal of the work angle of expression acceleration pedal; The signal of expression cam angle degree; Expression is to the signal of the selection of snowfield drive pattern; The signal of the longitudinal acceleration value of expression vehicle; Expression is to the signal of the selection of automatic cruising drive pattern; The signal of expression vehicle weight; The signal of the drive wheel speed of expression vehicle; The signal of the serviceability of expression step change Gear-shift switch, this step change Gear-shift switch are provided to the speed-changing mechanism 10 fixed speed ratio gearshift of speed-changing mechanism 10 as step change transmission that be placed in one; The signal of the serviceability of expression stepless change Gear-shift switch, this stepless change Gear-shift switch are provided to the speed-changing mechanism 10 stepless change gearshift of speed-changing mechanism 10 as toric transmission that be placed in one; The signal of representing the rotational speed N M1 of first motor M 1; The signal of representing the rotational speed N M2 of second motor M 2.Control electronics 40 also is configured to produce various signals, for example: drive the signal of throttle actuator with the control throttle opening; Regulate the signal of the pressure of blwr; The signal of electrical power for operation air-conditioning; The signal of the ignition device of the timing of ignition of control driving engine 8; The signal of operating electrical machines M1 and M2; Operation is used to represent the signal of shift range indicating device of the selected operating position of gear shifting handle; Operation is used to represent the signal of the transmitting ratio indicating device of transmitting ratio; Operation is used to represent the signal to the snowfield mode indicator of the selection of snowfield drive pattern; Operate the signal of the ABS actuator of the ABS (Anti-lock Braking System) that is used for wheel; Operation is used to represent the signal to the M mode indicator of the selection of M pattern; The signal of the electromagnetic control valve that operation comprises in the hydraulic control unit 42, hydraulic control unit 42 are provided to control the hydraulic actuator of the hydraulic operation friction Coupling device of power splitting mechanism 16 and automatic transmission with hydraulic torque converter part 20; Operate the signal of the electric oil pump of the hydraulic power source that is used as hydraulic control unit 42; Drive the signal of electric heater; And the signal that is applied to the cruising control computing machine.

Fig. 5 is the functional block diagram that is used to explain the major control function of being carried out by control electronics 40.As shown in Figure 5, switching control 50 comprises the judgment means 62 of running at high speed, high output travel judgment means 64 and circuit function diagnostic device 66, and is set to based on the situation of vehicle switchable type change-speed box part 11 (being power splitting mechanism 16) be switched between differential state and lockup state.That is, switching control 50 is set to based on the situation of vehicle speed-changing mechanism 10 be switched between stepless change gearshift and organic speed-change and gearshift state.Hybrid power control setup 52 is set to control driving engine 8 with high-efficiency operation, and control first motor M 1 and/or second motor M 2 to optimize the ratio of the propulsive effort that is produced by the driving engine 8 and second motor M 2, thereby when speed-changing mechanism 10 is placed in the stepless change gearshift (promptly when switchable type change-speed box part 11 is placed in the differential state), control is as the speed ratio γ 0 of the switchable type change-speed box part 11 of electric steplessly variable transmission work.Step change shift controller 54 is provided to based on the output T by vehicle velocity V and automatic transmission with hydraulic torque converter part 20 _OutRepresented vehicle condition, and, judge whether the gear shift action of automatic transmission with hydraulic torque converter part 20 should take place according to being stored in the figure memory storage 56 and as shown in Figure 6 gear shift border line chart.Step change shift controller 54 comes order automatic transmission with hydraulic torque converter part 20 with autoshift according to above-mentioned judgement.

The above-mentioned judgment means 62 of running at high speed is set to judge whether actual vehicle speed V has reached the preset speed values V1 as higher limit, judges that when surpassing this higher limit vehicle is in high-speed travel state.Above-mentioned high output travel judgment means 64 be set to judge propulsive effort with motor vehicle driven by mixed power relevant, such as the output torque T of automatic transmission with hydraulic torque converter 20 _OutAnd so on drive-force-related value whether reached predetermined output torque value T1 as higher limit, judge that when surpassing this higher limit vehicle is in high output motoring condition.Foregoing circuit functional diagnosis device 66 is set to judge whether the parts that can operate with the speed-changing mechanism 10 of setting up the stepless change gearshift have the function deterioration.This judgement of being undertaken by diagnostic device 66 is that the electric energy that is produced by first motor M 1 is converted into mechanical energy by this circuit according to the functions of components deterioration relevant with circuit.For example, based on the inefficacy of any parts in first motor M 1, second motor M 2, inverter 58, electrical energy storage device 60 and the electrical lead that is connected these parts or owing to the function deterioration or the defective that lost efficacy or low temperature causes, judge.

Above-mentioned drive-force-related value is the parameter corresponding to the propulsive effort of vehicle, and it can be the output torque T of automatic transmission with hydraulic torque converter part 20 _Out, driving engine 8 output torque T _EOr the accekeration of vehicle, and the driving torque of drive wheel 38 or propulsive effort.Motor torque T _ECan be based on actual value that the operational ton of acceleration pedal or the open angle of throttle gate (or suction quantity, air/fuel ratio or fuel injection amount) and engine speed NE calculated, maybe can be based on by the vehicle driver carry out to the operational ton of acceleration pedal or the motor torque T that open angle calculated of throttle gate _EOr the estimated valve of required vehicle drive force.The vehicular drive torque can not only wait based on output torque Tout and calculate, and can also calculate based on the speed ratio of differential gear mechanism 36 and the radius of drive wheel 38, also can be by directly detections such as torque masters.That is, height is exported the judgment means 64 of travelling detects vehicle based on the propulsive effort correlation parameter of representing vehicle drive force directly or indirectly high output state.

High gear judgment means 68 be configured to judge based on vehicle condition and according to be stored in the figure memory device 56 and the speed-changing mechanism 10 of as shown in Figure 6 gear shift border line chart should gear shift to gear whether be high gear, for example, the 5th gear.Carry out this and judge, to judge one that to be engaged among switch clutch C0 and the drg B0, so that speed-changing mechanism 10 is placed the step change gearshift.When speed-changing mechanism 10 integral body were placed in the step change gearshift, switch clutch C0 engagement to be placing speed-changing mechanism 10 first gear to any of fourth speed position, and switched drg B0 engagement so that speed-changing mechanism 10 is placed the 5th gear.

Switching control 50 is in step change gear shift zone at following predetermined condition or the situation vehicle condition that judges, and described conditioned disjunction situation is: the judgment means of running at high speed 62 has judged that vehicle is in high-speed travel state; The high judgment means 64 of travelling of exporting has judged that vehicle is in high output motoring condition; With circuit function diagnostic device 66 decision circuitry function deterioration.In the case, switching control 50 can not be worked hybrid power control setup 52, forbid that promptly hybrid power control setup 52 carries out hybrid power control or stepless change gear shift control, and the step change gear shift control operation of ordering step change shift controller 54 to be scheduled to, for example, order automatic transmission with hydraulic torque converter 20 automatically switches to according to being stored in the gearshift map memory storage 56 and the operation of as shown in Figure 6 the selected gear of gear shift border line chart.The form of Fig. 2 is represented hydraulic operation friction Coupling device, promptly C0, C1, C2, B0, B1, B2 and B3 and the combination cooresponding serviceability of each gear.Therefore, in the case, the speed-changing mechanism of being made up of switchable type change-speed box part 11 and automatic transmission with hydraulic torque converter 20 10 is used as so-called step change automatic transmission with hydraulic torque converter on the whole, and realizes the automatic switchover action shown in the form of Fig. 2.

Judge that in high gear judgment means 68 selected speed is under the situation of the 5th gear, to judge that vehicles are in high when exporting motoring condition for judgment means 64 when the judgment means 62 of running at high speed judges that vehicles are in high-speed travel state or when high output is travelled, switching control 50 order hydraulic control units 42 unclamp switch clutch C0 and drg B0 is switched in engagement, so that switchable type change-speed box part 11 can be the auxiliary gear box of 0.7 fixed speed ratio γ 0 as for example having, speed-changing mechanism 10 is placed in high gear on the whole thus, and this high gear is to have the what is called " hypervelocity gear " that is lower than 1.0 speed ratios.Export the judgment means 64 of travelling at height and judge that vehicles are under the situation of high output motoring condition, and judge that in high gear judgment means 68 selected gear is not under the situation of the 5th gear, switching control part 50 order hydraulic control units, 42 engagement switch clutch C0 also unclamp switching drg B0, make that switchable type change-speed box part 11 is the auxiliary gear box of 1 fixed speed ratio γ 0 as for example having, speed-changing mechanism 10 is placed in its speed ratio on the whole and is not less than 1.0 low-grade location thus.So, under any one condition of above-mentioned predetermined condition, switching control 50 places the step change gearshift with speed-changing mechanism 10, and optionally will place high tap position and low-grade location as the switchable type change-speed box part 11 of auxiliary gear box, make the automatic transmission with hydraulic torque converter part 20 that is connected in series to switchable type change-speed box part 11 can be used as step change transmission simultaneously, speed-changing mechanism 10 is used as the so-called grade automatic transmission with hydraulic torque converter that has on the whole thus.

For example, the speed of a motor vehicle upper limit V1 of the speed of a motor vehicle is confirmed as making that speed-changing mechanism 10 is placed in the step change gearshift when vehicle velocity V is higher than limit value V1.If speed-changing mechanism 10 is placed in the stepless change gearshift under higher relatively Vehicle Speed, then be defined as very effective to the possibility that minimizes the Vehicle Economy deterioration like this.Character of operation according to first motor M 1 is determined output torque upper limit T1, first motor M 1 is small-sized and makes that its maximum power output is less relatively, so that the reactive torque of first motor M 1 can be very not big when driving engine output is higher relatively in the height output motoring condition at vehicle.Alternatively, when vehicle is in height output motoring condition, speed-changing mechanism 10 is placed in step change gearshift (fixed speed ratio gearshift) rather than stepless change gearshift, make engine speed NE change along with the shift-up action of automatic transmission with hydraulic torque converter part 20, rhythmicity with the engine speed NE that guarantees comfortable when automatic transmission with hydraulic torque converter 20 upgrades changes, as shown in Figure 8.In this regard, note, when driving engine is in high output state, the more important thing is the demand of the raising vehicle steerability that satisfies the vehicle driver than satisfying the demand that improves fuel economy.

But, when speed-changing mechanism 10 normality when operation under its stepless change gearshift on the whole, promptly, when the judgment means 62 of running at high speed judges that vehicle is not in high-speed travel state, when height output is travelled judgment means 64 when judging that vehicles are not in high output motoring condition, and when circuit function diagnostic device 66 decision circuitry functions not during deterioration, switching control part 50 order hydraulic control units 42 unclamp switch clutch C0 and switch drg B0 so that switchable type change-speed box part 11 is placed the stepless change gearshift.In the case, switching control part 50 makes hybrid power control setup 52 can realize hybrid power control, and order step change shift controller 54 remains on automatic transmission with hydraulic torque converter part 20 for the stepless change gear shift controls selected predetermined gear, perhaps allows automatic transmission with hydraulic torque converter part 20 gear shift automatically to according to being stored in the gearshift map memory device 56 and as shown in Figure 6 the selected gear of gear shift border line chart.In the case, suitable one (except combinations of the engagement of switch clutch C0 and drg B0) in the combination of the engagement of represented friction Coupling device in the form of automatic transmission with hydraulic torque converter 20 according to Fig. 2, gear shift automatically under the control of step change shift controller 50.So, under the predetermined state of vehicle, switching control 50 makes switchable type change-speed box part 11 operate with the stepless change gearshift, to be used as toric transmission, and the automatic transmission with hydraulic torque converter part 20 that is connected in series to switchable type change-speed box part 11 is used as step change transmission, therefore drive system provides enough vehicle drive forces, make to be delivered to and place first gear, second gear, the speed that rotatablely moves of the automatic transmission with hydraulic torque converter part 20 of one of third gear and fourth speed position (being the rotating speed of power transfer member 18) is changed continuously, therefore when automatic transmission with hydraulic torque converter part 20 was placed in one of above-mentioned gear, the speed ratio of drive system can change on preset range continuously.So the speed ratio of automatic transmission with hydraulic torque converter part 20 can change on whole adjacent gear continuously, the overall ratio γ T of speed-changing mechanism 10 changes serially thus.

Hybrid power control setup 52 control driving engines 8 are with high-efficiency operation, and control first motor M 1 and/or second motor M 2, the ratio of the propulsive effort that is produced by driving engine 8 and first motor M 1 and/or second motor M 2 with optimization.For example, hybrid power control setup 52 calculates the desired output of vehicle driver under the current driving speed of vehicle based on the operational ton of acceleration pedal and Vehicle Speed, and requires output and requirement to calculate desired vehicle drive force by the electric energy generation of first motor generation based on the institute that calculates.Based on the vehicle drive force that requires that calculates, hybrid power control setup 52 calculates the speed N of desired driving engine 8 _EWith total output, and according to the speed N of the desired driving engine 8 that calculates _EWith total output, control the real output of driving engine 8 and the electric energy generation of motor.When being provided in the current selected gear of considering automatic transmission with hydraulic torque converter part 20, realizes hybrid power control setup 52 above-mentioned hybrid power control, with the steerability that improves vehicle and the fuel economy of driving engine 8.In hybrid power control, switchable type change-speed box part 11 is controlled to as electric steplessly variable transmission, so that be the engine speed N of driving engine 8 efficient operation _EThe rotating speed of the power transfer member of determining with vehicle velocity V and by the selected gear of automatic transmission with hydraulic torque converter part 20 18 has the optimization cooperation.That is to say that hybrid power control setup 52 is determined the expected value of the overall ratio γ T of speed-changing mechanism 10, makes driving engine 8 move according to the highest fuel-economy linearity curve of being stored.The highest fuel-economy linearity curve of being stored satisfies the expectation work efficiency and the highest fuel economy of driving engine 8.The speed ratio γ 0 of hybrid power control setup 52 control switchable type change-speed box parts 11 can be controlled at overall ratio γ T in the preset range to obtain the expected value of overall ratio γ T, to make, for example between 13 and 0.5.

In hybrid power control, hybrid power control setup 52 control inverters 58, make the electric energy that produces by first motor M 1 be fed to the electrical energy storage device 60 and second motor M 2 by inverter 58, thereby make the main portion of the propulsive effort that produces by driving engine 8 be mechanically transmitted to power transfer member 18, and the remainder of propulsive effort is consumed this part is converted to electric energy by first motor M 1, this electric energy is fed to the electric energy operation that second motor M 2 or first motor M 1 make that second motor M 2 or first motor M, 1 usefulness are supplied by inverter 58, is delivered to the mechanical energy of power transfer member 18 with generation.So drive system is provided with circuit, the electric energy that is produced by the part conversion of the propulsive effort of driving engine 8 is converted into mechanical energy by this circuit.This circuit comprises with the generation of electric energy with by the relevant parts of consumption of 2 pairs of electric energy that produce of second motor M.

Note, hybrid power control setup 52 can be set up what is called " electric motor starting and driving " pattern, wherein by utilizing the automatically controlled CVT function (differential function) of switchable type change-speed box part 11, and no matter driving engine 8 is in non-operating state or idling mode, vehicle is only by starting as the motor (for example, second motor M 2) that drives propulsion source and driving.As output torque T _OUTWhen being in low relatively scope (wherein engine efficiency is low relatively), or when driving engine is in low load range (wherein vehicle velocity V is low relatively), select electric motor starting and drive pattern usually.

Fig. 6 shows and is stored in the gearshift map memory storage 56 and is used to judge the gear shift border line chart that automatic transmission with hydraulic torque converter part 20 whether should gear shift.This gear shift border line chart is defined in the rectangle two-dimensional coordinate system, and this rectangle two-dimensional coordinate system has corresponding to each parameter, i.e. the output torque T of vehicle velocity V and employing automatic transmission with hydraulic torque converter part 20 _OUTTwo axles of drive-force-related value of form.In Fig. 6, solid line is a shift-up boundary line, and long and short dash line is a shift-down boundary line.Dotted line among Fig. 6 is to define the boundary line that is switched control part 50 employed step change gear shift zones and stepless change gear shift zone.Speed of a motor vehicle upper limit V1 and output torque upper limit T1 are represented in these boundary lines, and serve as respectively and be used to judge height output that the boundary line and being used to of running at high speed that whether vehicle condition is in high-speed travel state judges whether vehicle condition the is in high output motoring condition boundary line of travelling.Fig. 6 also shows long and two-short dash line, and they are the boundary lines of departing from suitable control hysteresis amount with respect to dotted line, makes optionally to make with dashed lines and long and two-short dash line as the boundary line.So Fig. 6 also shows the handoff boundary line chart of being stored (relation), it is switched control setup 50 and uses with according to vehicle velocity V and output torque T _OUTWhether be higher than predetermined upper limit value V1, T1, judge whether vehicle is in step change gearshift or stepless change gearshift.Therefore, can be according to this handoff boundary line chart and based on vehicle velocity V and output torque T _OUTActual value judge vehicle condition.This handoff boundary line chart and gear shift border line chart can be stored in the gearshift map memory device 56.The handoff boundary line chart can comprise at least one in the boundary line of representing speed of a motor vehicle upper limit V1 and output torque upper limit T1, and can only use two V parameter and T _OUTIn one.Gear shift border line chart and handoff boundary line chart can be used to actual vehicle speed V and limit value V1 compares and with real output torque T _OUTThe storage equation that compares with limit value T1 substitutes.

Be superimposed upon the handoff boundary line that is illustrated by the broken lines on the gear shift border line chart that is used for automatic transmission with hydraulic torque converter part 20 among Fig. 6 and be based on the gear shift of being stored zone switching figure (relation) shown in Figure 7, Fig. 7 has represented to have defined the boundary line in the regional and stepless change gear shift zone of step change gear shift in the two-dimensional coordinate system that has corresponding to two axles of the parameter of engine speed NE and motor torque Te form.In other words, switch the handoff boundary line chart that figure obtains Fig. 6 based on the gear shift zone of Fig. 7.Switching control 50 can use the gear shift zone switching figure of Fig. 7 to replace the handoff boundary line chart of Fig. 6, whether is in stepless change or step change zone to judge the vehicle condition that is detected.

The step change gear shift zone of being defined by the handoff boundary line chart of Fig. 6 is defined as wherein output torque T _OUTBe not less than predetermined upper limit T ₁The high torque (HT) zone, or wherein vehicle velocity V is not less than predetermined upper limit V ₁High-speed region.Therefore, as the torque T of driving engine 8 _EWhen high relatively or when vehicle velocity V is high relatively, make step change gear shift control effectively, and work as the torque T of driving engine 8 _EWhen low relatively or when vehicle velocity V is low relatively, promptly when driving engine 8 is in the normal state output state, make stepless change gear shift control effectively.Similarly, the step change gear shift zone of being defined by the gear shift of Fig. 7 zone switching figure is defined as wherein that motor torque Te is not less than predetermined upper limit T _E1The high torque (HT) zone, or wherein engine speed NE is not less than predetermined upper limit N _E1High-speed region, perhaps be defined as alternatively wherein based on motor torque Te and speed N _EThe output of the driving engine 8 that calculates is not less than the high output area of predetermined limits.Therefore, as the torque T of driving engine 8 _E, speed N _EOr output makes step change gear shift control effectively when high relatively, and as the torque T of driving engine 8 _E, speed N _EOr export when hanging down relatively, promptly when driving engine 8 is in the normal state output state, make stepless change gear shift control effectively.The boundary line of the gear shift zone switching figure of Fig. 7 can be considered to high speed threshold line or high-engine output threshold line, and it has defined the upper limit of vehicle velocity V or driving engine output.

Switching control 50 also comprises vehicle condition judgment means 88.This vehicle condition judgment means 88 is configured to judge vehicle velocity V and the output torque T by reality _OUTWhether the vehicle condition of expression or whether need switching control 50 to switch the gearshift of speed-changing mechanism 10 by the vehicle condition that engine speed NE and motor torque Te represent perhaps needs a grade speed-change and gearshift control setup 54 and makes 20 gear shift of automatic transmission with hydraulic torque converter part.For example, carry out this judgement based on the change of vehicle condition and according to handoff boundary line chart and the gear shift border line chart of Fig. 6.In other words, vehicle condition judgment means 88 can be considered to serve as and be used for judging whether speed-changing mechanism 10 should optionally switch to the device of another gearshift from a gearshift of stepless change and step change gearshift.In the present embodiment, switching control 50 and step change shift controller 54 can be carried out overlapping switching and gear shift control, wherein the switching controls of being undertaken by switching control 50 and overlapped each other substantially by the gear shift control that step change shift controller 54 carries out.Overlapping switching and gear shift control can initialization substantially simultaneously, or overlaps each other at least in part, makes the part of processing of the part of processing of switching controls and gear shift control take place substantially simultaneously.

Downward arrow line among Fig. 6 is represented the example of simultaneous substantially shift-up action and change action, and the upwards arrow line among Figure 18 is represented simultaneous substantially shift-down action and change action.In these examples, output torque T _OUTBe based on the demand output torque T to the operational ton calculating of acceleration pedal by the vehicle driver _OUTMore specifically, when speed-changing mechanism 10 places the step change gearshift, carry out unclamp operation as the represented acceleration pedal of the downward arrow line among Fig. 6.In the case, speed-changing mechanism 10 is switched to the blocked operation of stepless change gearshift and the shift-up action from first gear to second gear of automatic transmission with hydraulic torque converter part 20 takes place substantially simultaneously from the step change gearshift.Promptly, under the situation of affirmative determination that travelled by the judgment means 62 of running at high speed, high output without any one judgment means 64 and circuit function diagnostic device 66 are obtaining or decision, determine that speed-changing mechanism 10 should switch to the stepless change gearshift from the step change gearshift, simultaneously cross first to second shift-up boundary line, judge that substantially simultaneously automatic transmission with hydraulic torque converter part 20 should be by speed-change and gearshift control setup 54 from first gear, second gear that upgrades because vehicle condition has changed to move.On the other hand, when speed-changing mechanism 10 places the stepless change gearshift, carry out pressing operation as the represented acceleration pedal of the upwards arrow line among Figure 18.In the case, speed-changing mechanism 10 is switched to the blocked operation of step change gearshift and the shift-down action from second gear to first gear of automatic transmission with hydraulic torque converter part 20 takes place substantially simultaneously from the stepless change gearshift.Promptly, under the situation of the sure decision that the judgment means 64 of being travelled by height output obtains, determine that speed-changing mechanism 10 should switch to the step change gearshift from the stepless change gearshift, simultaneously because vehicle condition has changed to move crosses second to first shift-down boundary line and judge that substantially side by side automatic transmission with hydraulic torque converter part 20 should be by speed-change and gearshift control setup 54 from second gear, first gear that lowers category.In the present embodiment, substantially simultaneous switching controls of being undertaken by switching control 50 and be collectively referred to as works " gear shift that lowers category/switch overlapping control ", and simultaneous substantially switching controls of being undertaken by switching control 50 and control by upgrading of carrying out of step change shift controller 54 and to be collectively referred to as work " gear shift that upgrades/switch overlapping control " by the control that lowers category that step change shift controller 54 carries out.

Be appreciated that the change of the operational ton of acceleration pedal from Fig. 6 and Figure 18, i.e. the demand output torque T that calculates based on the operational ton of acceleration pedal _OUTChange initiation is used to switch the switching controls of the gearshift of speed-changing mechanism 10.Vehicle condition judgment means 80 is judged vehicle condition based on unclamping with pressing operation of acceleration pedal.In this regard, note, can judge vehicle condition based on any drive-force-related value except that the operational ton of acceleration pedal (for example open angle of throttle gate).

Speed-changing mechanism 10 can switch between stepless change gearshift and step change gearshift.For example, establishing under grade situation of speed-change and gearshift state by engagement switch clutch C0, the first sun wheel S1 of first compound planet gear 24 and the first gear ring R1 are as the speed rotation of one unit to equate with engine speed NE.Under this state, be fixed to the first sun wheel S1 first motor M 1 speed and to be fixed to the speed and the engine speed NE of second motor M 2 of the first gear ring R1 synchronous, but first motor M 1 not necessarily provides output torque.When speed-changing mechanism 10 switched to the stepless change gearshift by unclamping switch clutch C0, switch clutch C0 little by little reduced at the reactive torque that it unclamps in the process of action, and the reactive torque of first motor M 1 little by little increases simultaneously.If the reactive torque of the switch clutch C0 and first motor M 1 reduces and opportunity of increasing is not controlled suitably, then speed-changing mechanism 11 will be switched the risk that vibrations take place.In other words, the reactive torque of Coupling device is the torque of unclamping the driving engine that transmits by Coupling device in the process of action at it, if therefore the motor torque by the Coupling device transmission is not promptly reduced, then drive system may suffer to shake owing to the switching that the temporary transient change that is delivered to the motor torque of drive wheel causes.

For reducing the risk that above-mentioned switching vibrations take place, motor control assembly 82 is set to control first motor M 1, make first and second motor M 1, at least the first motor M 1 among the M2 produces reactive torque, with when switch clutch C0 or drg B0 unclamp, promptly be under the control of switching control 50 when the step change gearshift switches to the stepless change gearshift at speed-changing mechanism 10, speed-changing mechanism 10 is maintained and the essentially identical state of setting up by the engagement action of switch clutch C0 or drg B0 of step change gearshift, be about to the first element RE1, the second element RE2 maintains identical rotating speed with three element RE3.This control of first motor M 1 the switching vibrations of speed-changing mechanism 10 when the step change gearshift switches to the stepless change gearshift have been reduced.When judging that speed-changing mechanism 10 should be when the step change gearshift switches to the stepless change gearshift, produced under the control of motor control assembly 82 after the reactive torque of first motor M 1, switching control 50 begins the action of unclamping of switch clutch C0 or drg B0.

More specifically, motor control assembly 82 orders hybrid power control setup 52 controls first motor M 1 to produce and the reactive torque that will be equated by the reactive torque that engagement action was produced of switch clutch C0 when switch clutch C0 unclamps.Under this state of a control to first motor M 1, the first sun wheel S1 temporarily receives two kinds of different torques.For example, the generation of the electric energy that hybrid power control setup 52 control is produced by first motor M 1 makes the reactive torque that produced by first motor M 1 that the speed NM1 of first motor is maintained identical value with engine speed NE.In other words, by switch clutch C0 unclamp action when the step change gearshift switches to the stepless change gearshift, by the speed NM1 of motor control assembly 82 controls first motor, the speed NM1 of making is maintained with engine speed NE and equates substantially.That is, by control first motor M 1 under the control of motor control assembly 82, the rotating speed of controlling the first sun wheel S1 makes the rotating speed of the sun wheel S1 that wins keep equating substantially with engine speed NE.

Under the step change gearshift of being set up by the engagement action of switching drg B0, it is static that the first sun wheel S1 keeps, that is, the rotating speed of the first sun wheel S1 remains zero.Under this state, the speed that is fixed to first motor M 1 of the first sun wheel S1 also remains zero, but first motor M 1 not necessarily produces torque.When switching drg B0 by engagement, when speed-changing mechanism 10 switched to the stepless change gearshift, the reactive torque that is in the switching drg B0 under the engagement little by little reduced, and the reactive torque of first motor M 1 little by little increases simultaneously.The reactive torque of the drg B0 and first motor M 1 increases and opportunity of reducing is not controlled suitably if switch, and then change-speed box 11 can suffer the risk that takes place in the switching vibrations when the step change gearshift switches to the stepless change gearshift.

For reducing the risk of above-mentioned switching vibrations generation, the reactive torque of order hybrid power control setup 52 controls first motor M 1 to produce and will equate when motor control assembly 82 unclamps at switching drg B0 by the reactive torque that engagement action was produced of switching drg B0.Under this state of a control to first motor M 1, the first sun wheel S1 temporarily receives two kinds of different torques.For example, hybrid power control setup 52 control first motor M 1 makes that the generation of the electric energy that produced by first motor M 1 is zero substantially, thereby makes the reactive torque that is produced by first motor M 1 keep the first sun wheel S1 static.In other words, by switch clutch C0 unclamp action when the step change gearshift switches to the stepless change gearshift, by the speed NM1 of motor control assembly 82 controls first motor, it is zero substantially that the speed NM1 of making is maintained.That is, by control first motor M 1 under the control of motor control assembly 82, it is zero substantially that the rotating speed of controlling the first sun wheel S 1 keeps the rotating speed of the sun wheel S1 that wins.

Synchro control is set to be finished judgment means 84 and judges when determining that speed-changing mechanism 10 should switch to the stepless change gearshift from the step change gearshift whether produced the predetermined reactive torque that equates with the reactive torque that will be produced by the engagement action of switch clutch C0 or drg B0 by first motor M 1 under the control of motor control assembly 82.For example, by whether judging the amount of electric energy that produces and be fed to electrical energy storage device 60 by first motor M 1 corresponding to above-mentioned predetermined reactive torque, the cause synchro control is finished judgment means 84 and is carried out this judgement.

When synchro control was finished judgment means 84 and judged that the predetermined reactive torque of first motor M 1 has produced, above-mentioned switching control 50 beginning switch clutch C0 or drg B0 unclamped action.Based on the beginning of unclamping action, switch clutch C0 or drg B0 do not need to produce reactive torque, and this is because produce predetermined reactive torque by first motor M 1.Therefore, the hydraulic pressure of switch clutch C0 or drg B0 does not need to reduce gradually, and can reduce rapidly to be used for relatively promptly switching to the stepless change gearshift.

Before unclamping of switch clutch C0 moved beginning, the speed NM1 that motor control assembly 82 continues control first motor is to keep the velocity contrast of first, second and three element RE1, RE2 and RE3, be about to the first sun wheel S1 and maintain identical speed, finish up to the action of unclamping of the switch clutch C0 under the control of switching control 50 with engine speed NE.Unclamping after action finishes of switch clutch C0, make the reactive torque that is produced corresponding to actual engine torque Te by the reactive torque that first motor M 1 produces by hybrid power control setup 52 control.

Alternatively, before unclamping of switching drg B0 moved beginning, motor control assembly 82 continues the speed NM1 of control first motor to keep the velocity contrast of above-mentioned second element and above-mentioned mission case 12, promptly, the first sun wheel S1 is maintained its speed remain zero quiescence, finish up to the action of unclamping of the switching drg B0 under the control of switching control 50.

Fig. 9 is a diagram of circuit of explaining the major control operation of being carried out by control electronics 40, that is, and and the control routine of when the step change gearshift switches to the stepless change gearshift, carrying out at speed-changing mechanism 10.This control routine extremely repeats with for example approximate number millisecond tens of milliseconds very short period.Figure 10 and Figure 11 are the sequential charts that is used for the example of the control operation shown in the diagram of circuit of key drawing 9.The sequential chart of Figure 10 show when the step change gearshift of setting up by the engagement action of switch clutch C0 be switched to by switch clutch C0 unclamp the stepless change gearshift that action sets up the time control operation carried out, and the sequential chart of Figure 11 show when the step change gearshift of setting up by the engagement of switching drg B0 be switched to by switch drg B0 unclamp the stepless change gearshift of action foundation the time control operation carried out.

The switching controls routine judges with step SA1 (after this will omit " step " this speech) beginning corresponding to vehicle condition judgment means 80 whether acceleration pedal unclamps.Operational ton based on acceleration pedal carries out this judgement.When obtaining definite results in SA1, control flow proceeds to also corresponding to the SA2 of vehicle condition judgment means 80, judges by actual vehicle speed V and the demand output torque T that calculates based on the operational ton of acceleration pedal _OUTWhether represented vehicle condition changes, to such an extent as to require speed-changing mechanism 10 to switch to the stepless change gearshift from the step change gearshift.For example, the figure according to Fig. 6 carries out changing this relevant judgement with vehicle condition.If obtain negative result at SA1 or SA2, then control flow proceeds to SA8 to keep the current driving state of vehicle.These steps SA1 and SA2 can be revised as single step and judge whether speed-changing mechanism 10 should switch to the stepless change gearshift from the step change gearshift.This judgement can be by carrying out as judging, promptly, by judge whether not judge high output vehicle ', hot-short travels and the circuit function deterioration in any, perhaps require the judgement of function deterioration of the circuit of step change gearshift to change to the function deterioration (that is, whether circuit is restored from the function deterioration) of not judging circuit by judgement.

When all obtaining definite results among SA1 and the SA2 (at the time point t shown in Figure 10 and 11 ₁The place), control flow proceeds to the SA3 corresponding to motor control assembly 82, controls first motor M 1 and makes at the time point t shown in Figure 10 and 11 ₂The place produces the predetermined reactive torque that equates with the reactive torque of switch clutch C0 or drg B0 by first motor M 1, and the first sun wheel S1 temporarily receives two kinds of different torques thus.Then, control flow proceeds to synchro control and finishes judgment means 84 cooresponding SA4, judges whether to produce the pre-determined torque that equates with the reactive torque of switch clutch C0 or drg B0 by first motor M 1.For example, whether carry out this judgement by judgement by the amount that first motor M 1 produced and be fed to the electric energy of electrical energy storage device 60 corresponding to above-mentioned predetermined reactive torque.Repeat SA3 up in this step, obtaining definite results.When obtaining definite results in SA4, control flow proceeds to and switching control 50 cooresponding SA5, and what begin switch clutch C0 or drg B0 unclamps action (at the time point t shown in Figure 10 and 11 ₂The place).Owing under this state, produced predetermined reactive torque by first motor M 1, then do not need switch clutch C0 or drg B0 to produce reactive torque, therefore the hydraulic pressure of switch clutch C0 or drg B0 does not need to reduce gradually, and therefore can be at time point t as shown in figure 10 ₂To time point t ₃Time period reduce rapidly, therefore can finish switching to the stepless change gearshift in the short period of time.

Then, control flow proceeds to also the SA6 corresponding to motor control assembly 82, wherein establish under grade situation of speed-change and gearshift state, continue to make the speed of the sun wheel S1 that wins keep equating with engine speed NE to the control of first motor M 1 in engagement action by switch clutch C0.Establishing under grade situation of speed-change and gearshift state by the engagement action of switching drg B0, continuing control to first motor M 1 and make the sun wheel S1 that wins keep static with its speed state of zero of remaining.Then, control flow proceeds to the SA7 corresponding to hybrid power control setup 52, come with the speed-changing mechanism 10 beginning vehicle controls that place the stepless change gearshift, wherein in the ratiometric while of optimization by the vehicle drive force of driving engine 8 and first motor M 1 and/or 2 generations of second motor M, driving engine 8 efficiently moves.Vehicle under this stepless change gearshift is controlled at the time point t shown in Figure 10 and 11 ₃Beginning.As a result, the reactive torque that switch clutch C0 or drg B0 produce under its engagement is replaced rapidly by the reactive torque that first motor M 1 produces, and makes to reduce to switch vibrations.In addition, can reduce switch clutch C0 or drg B0 unclamps in the action or the process of its partial tooth engagement state (from the time point t shown in Figure 10 and 11 at it ₂To time point t ₃Time period during) input and output speed between poor, thereby can reduce that switch clutch C0 or drg B0 go up because the load that its skidding produces, the raising that brings its durability degree.

As mentioned above, motor control assembly 82 (SA3, SA6) first motor of control speed-changing mechanism 10, control speed-changing mechanism 10 comprises power splitting mechanism 16, power splitting mechanism 16 has the first element RE1 (the first planetary wheel carrier CA1) that is fixed to driving engine 8, be fixed to the second element RE2 (the first sun wheel S1) of first motor M 1 and the three element RE3 (the first gear ring R1) that is fixed to second motor M 2 and power transfer member 18, and comprise and being used for the first and second element RE1, interconnected switch clutch C0 of RE2 and the switching drg B0 that is used for the second element RE2 is fixed to casing 12, and power splitting mechanism 16 therein power splitting mechanism 16 as the stepless change gearshift of electric steplessly variable transmission work with wherein switch between the step change gearshift of power splitting mechanism 16 as step change transmission work.Motor control assembly 82 control first motor M 1 is to produce predetermined reactive torque when switch clutch C0 or drg B0 unclamp, make the reactive torque of switch clutch C0 or drg B0 suitably be replaced, to reduce the switching vibrations when the switching of speed-changing mechanism by the reactive torque of first motor M 1.In addition, the reducing of the reactive torque of switch clutch C0 or drg B0 compensated by the predetermined reactive torque of first motor M 1, still remain on engagement as switch clutch C0 or drg B0, make the difference between the input and output speed of switch clutch C0 or drg B0 reduce, thereby reduce the upward load under its partial tooth engagement state of switch clutch C0 or drg B0, the raising that brings power-transfer clutch C0 or drg B0 durability degree.In addition, power splitting mechanism 16 is made of simply three elements and switch clutch C0 and drg B0, and by switch clutch C0 or drg B0, speed-changing mechanism 10 easily switches between stepless change and step change gearshift under the control of switching control 50.

Also be arranged so that at speed-changing mechanism 10 switching control 50 when the step change gearshift switches to the stepless change gearshift according to control convenience of the present invention and can operate to begin the action of unclamping of switch clutch C0 or drg B0 after under the control of motor control assembly 82, having produced predetermined reactive torque by first motor M 1.Be provided with according to this, the reactive torque of switch clutch C0 or drg B0 is replaced suitably by the reactive torque of first motor M 1, makes that the switching vibrations when the switching of speed-changing mechanism 10 reduce.In addition, no matter the reactive torque that is produced by first motor M 1 allows the reducing of the reactive torque of switch clutch C0 or drg B0, rotating speed by the second element RE2 of suitable control (the first sun wheel S1) reduces, the feasible durability degree that improves switch clutch C0 or drg B0.

Also be arranged so that the speed of motor control assembly 82 first motor M 1 according to the control convenience of present embodiment, to such an extent as to velocity contrast between the first element RE1, the second element RE2 and the three element RE3 or the velocity contrast between the second element RE2 and the casing 12 switch clutch C0 or drg B0 unclamp action before remain on a value, instruct by the switch clutch C0 of switching control 50 controls or the action of unclamping of drg B0 and finish.Therefore, switch clutch C0 or drg B0 unclamp in the process of action or the input and output speed under its partial tooth engagement state reduces up to unclamping action and finishes at it, make the load that produces owing to its skidding on switch clutch C0 or the drg B0 reduce, the result improves its durability degree.

In the present embodiment, judge the predetermined state of vehicle based on the predetermined upper limit value V1 of the moving velocity of vehicle, and when the actual travel speed V of vehicle was higher than predetermined upper limit value V1, switching control 50 placed the step change gearshift with speed-changing mechanism 10.Vehicle velocity V is higher than under the high-speed travel state of vehicle of higher limit V1 therein, the output of driving engine 8 mainly is delivered to drive wheel 38 by the mechanical power bang path, make and to compare, because of the minimizing of the conversion loss between mechanical energy and the electric energy in the step change gearshift has improved fuel economy with the stepless change gearshift.

In the present embodiment, judge the predetermined state of vehicle based on the predetermined upper limit value T1 of the output of vehicle, and as real output value T _OUTWhen being higher than predetermined upper limit value T1, switching control 50 places the step change gearshift with speed-changing mechanism 10, and therefore, the output of driving engine 8 mainly is delivered to drive wheel 38 by the mechanical power bang path.But when vehicle was in middle output or low output motoring condition, speed-changing mechanism 10 was operated as electric steplessly variable transmission.Therefore, can reduce should be by the required maximum power of first motor M, 1 generation, promptly, can reduce the demand output capacity of first motor M 1, therefore the demand size of first motor M 1 and second motor M 2 can be reduced, thereby the demand size of the Vehicular drive system that comprises first and second motor M 1, M2 can be reduced.

Control convenience according to present embodiment is arranged so that also switching control 50 can be based on actual vehicle speed and output torque T _OUTAnd according to upper limit V1 and output torque T by vehicle velocity V _OUTThe handoff boundary line chart of being stored that defines of upper limit T1 judge easily whether vehicle is at a high speed or high output motoring condition.

Be arranged so that also that according to the control convenience of present embodiment switching control 50 determines that when function deterioration Rule of judgment satisfies speed-changing mechanism 10 should switch to the step change gearshift, when being used for that speed-changing mechanism 10 placed any function deterioration of function unit of stepless change gearshift, satisfy function deterioration Rule of judgment.Therefore, under the arbitration functions deterioration makes the invalid situation of the speed-changing mechanism 10 will be placed in the stepless change gearshift, therefore speed-changing mechanism 10 is placed in the step change gearshift, even under the situation that the function deterioration exists, vehicle also can travel with the step change gearshift.

In addition, constitute by first compound planet gear 24 (it has three elements that comprise the first planetary wheel carrier CA1, the first sun wheel S1 and the first gear ring R1) of single-stage planetary gear type simply by the power splitting mechanism of controlling according to the control convenience of present embodiment 16, make that the axial dimension of power splitting mechanism 16 is less.In addition, by switching control 50, power splitting mechanism 16 can be switched between stepless change gearshift and step change gearshift, switching control 50 is set to control switch clutch C0 and switches the hydraulic operation friction Coupling device of drg B0 form, switch clutch C0 is used for the first sun wheel S1 and the first planetary wheel carrier CA1 are connected to each other, and switches drg B0 and is used for the first sun wheel S1 is fixed to mission case 12.

In addition, be connected in series and be inserted between power splitting mechanism 16 and the drive wheel 38 by automatic transmission with hydraulic torque converter part 20 according to the speed-changing mechanism 10 of the control convenience of present embodiment control, and, promptly determine the overall ratio of speed-changing mechanism 10 by the speed ratio of the speed ratio of switchable type change-speed box part 11 and automatic transmission with hydraulic torque converter part 20 by the speed ratio of power splitting mechanism 16.Therefore,, can on wide relatively ratio coverage, obtain vehicle drive force, the feasible stepless change control efficiency that can improve switchable type change-speed box part 11, i.e. hybrid power control efficiency by utilizing the speed ratio of automatic transmission with hydraulic torque converter part 20.

In addition, switchable type change-speed box part 11 by this control convenience control can be operated under the state of a part that as it is automatic transmission with hydraulic torque converter part 20, and has the hypervelocity gear of speed ratio less than 1 employing the 5th gear form when speed-changing mechanism 10 places the step change gearshift.

The switching control 50 of this control convenience is set to according to vehicle condition speed-changing mechanism 10 automatically be switched between stepless change and step change gearshift, therefore Vehicular drive system not only has the advantage of the fuel economy that improves electric steplessly variable transmission, also has the advantage of the higher mechanical power transmission efficiency of step change transmission.Therefore, when driving engine was in the normal state output state, for example, being in wherein, vehicle V was not higher than upper limit V1 and output torque T _OUTWhen being not less than the stepless change gear shift zone as shown in Figure 7 of upper limit T1 or the zone of stepless change gear shift as shown in Figure 6, speed-changing mechanism 10 is placed in the stepless change gearshift, make and travel and improve fuel economy in (that is, in the middling speed of vehicle and low speed driving and middle output and low output are travelled) in the normality urban district of motor vehicle driven by mixed power.When driving engine is in high-speed travel state, for example, when being in the stepless change gear shift zone as shown in Figure 6 that vehicle velocity V wherein is higher than upper limit V1, speed-changing mechanism 10 is placed in the wherein output of driving engine 8 mainly is delivered to drive wheel 38 by the mechanical power bang path step change gearshift, make and compare that the minimizing owing to the conversion loss between mechanical energy and the electric energy in the step change gearshift improves fuel economy with the stepless change gearshift.When driving engine 8 is in height output motoring condition, for example be in wherein output torque T _OUTWhen being not less than in the stepless change gear shift zone as shown in Figure 6 of upper limit T1, speed-changing mechanism 10 is placed in the wherein output of driving engine 8 mainly is delivered to drive wheel 38 by the mechanical power bang path step change gearshift.So, only when vehicle is in middling speed or low speed driving state or be in middle output or low output state, speed-changing mechanism 10 just is placed in the stepless change gearshift, to such an extent as to can reduce the power demand that produces by first motor M 1 (i.e. the maximum power that must transmit from first motor M 1), the feasible demand size that can reduce the demand size of first and second motor M 1, M2 and comprise the Vehicular drive system of these motors.

In the present embodiment, second motor M 2 is fixed to the power transfer member 18 as the input rotating element of automatic transmission with hydraulic torque converter part 20, therefore with respect to the torque of the output shaft 22 of change-speed box part 20, the output torque of second motor M 2 can be reduced, thereby the demand size of second motor M 2 can be reduced.

Other embodiment of the present invention will be described.In the following description, used in the present embodiment same numeral will be used to identify corresponding elements, will be no longer to its explanation.

Second embodiment

Figure 12 is a diagram of circuit of explaining the major control operation of control electronics 40, that is, and and the routine of when lockup state switches to differential state (non-lockup state), carrying out in switchable type change-speed box part 11 (that is, power splitting mechanism 16).This control routine extremely repeats with for example approximate number millisecond tens of milliseconds very short period.Figure 13 is the sequential chart that is used to explain the example of the control operation shown in the diagram of circuit of Figure 12, this control operation the lockup state of setting up by the engagement action of switch clutch C0 switch to by switch clutch C0 unclamp the non-lockup state that action sets up the time carry out.

The difference of the control routine of the diagram of circuit of Figure 12 and the diagram of circuit of Fig. 9 is, in the diagram of circuit of Figure 12, the control routine of Figure 12 is applied to switchable type change-speed box part 11 by unclamping the switching from lockup state to non-lockup state that switchable type power-transfer clutch C0 or drg B0 carry out, and switches vibrations to reduce.In this regard, notice that the switching of speed-changing mechanism 10 from the step change gearshift to the stepless change gearshift can be thought and be equal to the switching of switchable type change-speed box part 11 from lockup state to non-lockup state.

Control routine judges with the SA1 ' beginning corresponding to vehicle condition judgment means 80 whether acceleration pedal unclamps.Operational ton based on acceleration pedal carries out this judgement.When in the middle acquisition definite results of SA1 ', control flow proceeds to also the SA2 ' corresponding to vehicle condition judgment means 80, judge whether vehicle condition changes, to such an extent as to require switchable type change-speed box part 11 to switch to non-lockup state from lockup state.For example, the figure according to Fig. 6 carries out changing this relevant judgement with vehicle condition.If in SA1 ' or the negative result of SA2 ' acquisition, then control flow proceeds to SA8 ' to keep the current driving state of vehicle.These steps SA1 ' and SA2 ' can be revised as single step and judge whether switchable type change-speed box part 11 should switch to non-lockup state from lockup state.This judgement can be by carrying out as judging, promptly, by judge whether not judge high output vehicle ', hot-short travels and the circuit function deterioration in any, perhaps require the judgement of function deterioration of the circuit of lockup state to change to the function deterioration (that is, whether circuit is restored from the function deterioration) of not judging circuit by judgement.

When SA1 ' and SA2 ' obtain definite results among both (at time point t as shown in figure 13 ₁The place), control flow proceeds to the SA3 ' corresponding to motor control assembly 82, controls first motor M 1 and makes at as shown in figure 13 time point t ₂The place produces the predetermined reactive torque that equates with the reactive torque of switch clutch C0 or drg B0 by first motor M 1, and the first sun wheel S1 temporarily receives two kinds of different torques thus.Then, control flow proceeds to synchro control and finishes judgment means 84 cooresponding SA4 ', judges whether to produce the pre-determined torque that equates with switch clutch C0 or drg B0 by first motor M 1.For example, whether carry out this judgement by judgement by the amount that first motor M 1 produced and be fed to the electric energy of electrical energy storage device 60 corresponding to above-mentioned predetermined reactive torque.Repeat SA3 ' up in this step, obtaining definite results.When obtaining definite results among the SA4 ', control flow proceeds to and switching control 50 cooresponding SA5 ', and that starts switch clutch C0 or drg B0 unclamps action (at time point t as shown in figure 13 ₂The place).Owing under this state, produced predetermined reactive torque by first motor M 1, so do not need switch clutch C0 or drg B0 to produce reactive torque, therefore the hydraulic pressure of switch clutch C0 or drg B0 does not need to reduce gradually, and therefore can be at time point t as shown in figure 13 ₂To time point t ₃Time period reduce rapidly, thereby can in shorter time, be accomplished to the switching of non-lockup state.

Then, control flow proceeds to also the SA6 ' corresponding to motor control assembly 82, wherein setting up by the engagement action of switch clutch C0 under the situation of lockup state, continuing to make the speed of the sun wheel S1 that wins keep equating with engine speed NE to the control of first motor M 1.Setting up under the situation of lockup state by the engagement action of switching drg B0, continuing control to first motor M 1 and make the sun wheel S1 that wins keep static with its speed state of zero of remaining.Then, control flow proceeds to the SA7 ' corresponding to hybrid power control setup 52, come beginning vehicle control under the differential state of switchable type change-speed box part 11, wherein in the ratiometric while of optimization by the vehicle drive force of driving engine 8 and first motor M 1 and/or 2 generations of second motor M, driving engine 8 efficiently moves.As a result, the reactive torque that switch clutch C0 or drg B0 produce under its engagement is replaced rapidly by the reactive torque that first motor M 1 produces, and makes to reduce to switch vibrations.In addition, can reduce switch clutch C0 or drg B0 unclamps in the action or the process of its partial tooth engagement state (from as shown in figure 13 time point t at it ₂To time point t ₃Time period during) input speed and output speed between poor, thereby can reduce that switch clutch C0 or drg B0 go up because the load that its skidding produces, the raising that brings its durability degree.

About the switching controls when the switching of speed-changing mechanism 10 by the gearshift of unclamping switch clutch C0 or drg B0 and carrying out, have and the identical advantage of control convenience according to previous embodiment according to the control convenience of present embodiment, this is because the switching of speed-changing mechanism 10 from the step change gearshift to the stepless change gearshift is equal to the switching of switchable type change-speed box part 11 from lockup state to non-lockup state.

The 3rd embodiment

Formerly among the embodiment, only under the control of motor control assembly 82, produced after the predetermined reactive torque of first motor M 1, just unclamped switch clutch C0 or drg B0 by switching control 50. present embodiments are that with the difference of previous embodiment the motor control assembly 82 in the present embodiment is set to order hybrid power control device 52 to control first motor M 1; So that under the control of switching control 50, produce the predetermined anti-torque of first motor M 1 in the process of unclamping action of switch clutch C0 or brake B0, unclamp that gear 10 is switched to the infinitely variable speeds gearshift or with the switching vibrations of switchable type speed changer part 11 (power splitting mechanism 16) when switching to non-lockup state from lockup state from the step speed change gearshift so that reduce switch clutch C0 or brake B0.

Particularly, the switching control 50 switch clutch C0 that comes up, motor control assembly 82 makes speed (i.e. the speed NM1 of the first motor) maintenance of the sun wheel S1 that wins equate with engine speed NE at the speed NM1 that unclamps control first motor in the action of switch clutch C0 simultaneously.Promptly, present embodiment is set to carry out what is called " overlapping switching and electric machine control ", wherein by switching control 50 carry out to the control of unclamping action of switch clutch C0 with undertaken by motor control assembly 82 to the control of the speed of first motor M 1 (promptly, by controlling of the control of its speed to the torque of first motor M 1, or rather, to the control of the torque of first motor M 1 so that motor speed NM1 keep equating with engine speed NE) carry out simultaneously.

The result, along with switch clutch C0 reduces gradually at the reactive torque that it unclamps in the process of action, the reactive torque that is produced by first motor M 1 under the control of motor control assembly 82 increases gradually, makes the reactive torque of switch clutch C0 under its engagement be replaced by the reactive torque of first motor M 1 gradually.For example, the speed NM1 of motor control assembly 82 controlled resets first motor makes that the difference between speed NM1 and the engine speed NE is zero substantially, to reduce the velocity contrast between the above-mentioned first element RE1, the second element RE2 and three element RE3.

Alternatively, switching control 50 unclamps at leisure and switches drg B0, motor control assembly 82 is controlled the speed NM1 of first motor in the process of unclamping action of switch clutch C0 simultaneously, makes the speed NM1 of the motor of winning keep equating with engine speed NE.Promptly, present embodiment is set to carry out what is called " overlapping switching and electric machine control ", wherein by switching control 50 carries out the control of unclamping action of switch clutch C0 and the control of being undertaken by motor control assembly 82 (this control makes motor speed NM1 equal engine speed NE) to the torque of first motor M 1 are taken place simultaneously.

The result, reduce gradually at the reactive torque that it unclamps in the process of action along with switching drg B0, the reactive torque that is produced by first motor M 1 under the control of motor control assembly 82 increases gradually, makes that switching the reactive torque of drg B0 under its engagement is replaced by the reactive torque of first motor M 1 gradually.For example, the speed NM1 of motor control assembly 82 controlled resets first motor is to reduce the velocity contrast between the speed of above-mentioned second element RE2 and casing 12.

Figure 14 be used to explain speed-changing mechanism 10 from the step change gearshift of setting up by the engagement action of switch clutch C0 switch to by switch clutch C0 unclamp the stepless change gearshift that action sets up the time the sequential chart of control operation.Example shown in the sequential chart of Figure 14 is the possibility for the example shown in the sequential chart of Figure 10.Figure 15 be used to explain speed-changing mechanism 10 from the step change gearshift of setting up by the engagement action of switching drg B0 switch to by switch drg B0 unclamp the stepless change gearshift that action sets up the time the sequential chart of control operation.Example shown in the sequential chart of Figure 15 is the possibility for the example shown in the sequential chart of Figure 11.Figure 16 be used to explain speed-changing mechanism 11 from the lockup state of setting up by the engagement action of switch clutch C0 switch to by switch clutch C0 unclamp the non-lockup state that action sets up the time the sequential chart of control operation.Example shown in the sequential chart of Figure 16 is the possibility for the example shown in the sequential chart of Figure 13.

In Figure 10,11 and 13 example, only after the predetermined reactive torque that produces first motor M 1, the hydraulic pressure of switch clutch C0 or drg B0 just promptly reduces.The difference of the example of Figure 14-16 and Figure 10,11 and 13 corresponding example mainly is, in the example of Figure 14-16, can carry out so-called overlapping switching and electric machine control, make and to take place simultaneously each other to the control of unclamping action of switch clutch C0 or drg B0 and to the speed control of first motor M 1 (that is, carrying out torque control) to first motor by its speed control.Therefore, Figure 14 and 15 example and the example difference of Figure 10 and 11 are, in the example of Figure 14 and 15, step SA3 and SA4 and step SA5 carry out simultaneously, and the example difference of the example of Figure 16 and Figure 13 is, the step SA5 ' in the example of step SA3 ' and SA4 ' and Figure 16 carries out simultaneously.

Explain, in the process of unclamping action of switch clutch C0, when the speed of the first sun wheel S1, promptly the speed NM1 of first motor is fed control when keeping equating with engine speed NE, and switch clutch C0 is from time point t in the example of Figure 14 ₂To time point t ₃' time period during with than unclamping with lower speed in the example of Figure 10, switch clutch C0 is from time point t in the example of Figure 10 ₂To time point t ₃Time period during promptly unclamp.That is, the torque of control first motor M 1 in the process of unclamping action of switch clutch C0 makes the speed NM1 of the motor of winning keep equating with engine speed NE.At time point t shown in Figure 14 ₃' afterwards, carry out the vehicle control under the stepless change gearshift of speed-changing mechanism 10.

Similarly, in the process of unclamping action of switching drg B0, when the speed of the first sun wheel S1, promptly the speed NM1 of first motor is fed control when remaining zero, switches drg B0 in the example of Figure 15 from time point t ₂To time point t ₃' time period during unclamp with the speed lower than the example of Figure 11, in the example of Figure 11, switch drg B0 from time point t ₂To time point t ₃Time period during promptly unclamp.That is, the torque of control first motor M 1 in the process of unclamping action of switching drg B0 makes the speed NM1 of the motor of winning remain zero.At time point t shown in Figure 15 ₃' afterwards, carry out the vehicle control under the stepless change gearshift of speed-changing mechanism 10.

Similarly, in the process of unclamping action of switch clutch C0, when the speed of the first sun wheel S1, promptly the speed NM1 of first motor is fed control when keeping equating with engine speed NE, and switch clutch C0 is from time point t in the example of Figure 16 ₂To time point t ₃' time period during with than unclamping with lower speed in the example of Figure 13, switch clutch C0 is from time point t in the example of Figure 13 ₂To time point t ₃Time period during promptly unclamp.That is, the torque of control first motor M 1 in the process of unclamping action of switch clutch C0 makes the speed NM1 of the motor of winning keep equating with engine speed NE.At time point t shown in Figure 16 ₃' afterwards, carry out the vehicle control under the differential state of switchable type change-speed box part 11.

The result, along with the reactive torque of switch clutch C0 or drg B0 reduces in it unclamps the process of action gradually, the reactive torque that is produced by first motor M 1 increases gradually, make switch clutch C0 or the reactive torque of drg B0 under its engagement be replaced by the reactive torque of first motor M 1 gradually, switch vibrations thereby reduced.In addition, reduced switch clutch C0 or drg B0 and unclamped poor the input and output speed of (during) under when action or its partial tooth engagement state from the time point t2 shown in Figure 14-16 to the time period of time point t3 ' at it, the result has reduced on switch clutch or the drg because the load that skidding produces, and has therefore improved the durability degree of switch clutch or drg.

In Figure 14,15 and 16 example, can depend on that vehicle velocity V or motor torque Tc control the reduction rate of the hydraulic pressure of the Magnification of torque of first motor M 1 or switch clutch C0 or drg B0, can carry out so-called overlapping switching and electric machine control, make to increase motor torque at switch clutch C0 or when drg B0 unclamps.

As mentioned above, according to the control convenience of present embodiment be arranged so that speed-changing mechanism 10 when the step change gearshift switches to the stepless change gearshift (, in switchable type change-speed box part 11 (power splitting mechanism 16) when lockup state switches to non-lockup state) motor control assembly 82 can operate, and under the control of switching control 50 in the process of unclamping action of switch clutch C0 or drg B0, motor control assembly 82 control first motor M 1 makes the reactive torque of the motor M 1 of winning unclamp along with switch clutch C0 or drg B0 and increases.Be provided with according to this, the reactive torque of switch clutch C0 or drg B0 is suitably replaced by the reactive torque of first motor M 1, makes the switching that reduces when speed-changing mechanism switches shake.In addition, no matter the reactive torque that is produced by first motor M 1 allows the reducing of the reactive torque of switch clutch C0 or drg B0, the rotating speed of the second element RE2 (the first sun wheel S1) is all controlled suitably, has improved the durability degree of switch clutch C0 or drg B0 thus.

Control convenience according to present embodiment also is arranged so that in the process of unclamping action of switch clutch C0 or drg B0, and the speed of motor control assembly 82 controlled resets first motor M 1 is to reduce velocity contrast between the first element RE1, the second element RE2 and the three element RE3 or the velocity contrast between the second element RE2 and the casing 12.Therefore, the reactive torque of switch clutch C0 or drg B0 was replaced by the reactive torque of first motor M 1 in the shorter time period.

Different with the previous embodiment that unclamps action that wherein begins switch clutch C0 or drg B0 after the predetermined reactive torque of first motor M 1 produces, present embodiment is set to unclamp and produce the reactive torque of first motor M 1 along with switch clutch C0 or drg B0.Except the difference of above-mentioned control, present embodiment has and the previous identical advantage of embodiment.

The 4th embodiment

As mentioned above, speed-changing mechanism 10 can switch between stepless change gearshift and step change gearshift.For example, under the stepless change gearshift, speed-changing mechanism 10 is in the speed of the first sun wheel S1 and the first gear ring R1 wherein and is not fixed to first motor M 1 of the first sun wheel S1 and is fixed to the influence of second motor M 2 of the first gear ring R1 or the free state of domination.That is, place the speed ratio of the speed-changing mechanism 11 of stepless change gearshift not to be maintained fixed with respect to engine speed NE.On the other hand, for example under the step change gearshift of setting up by the engagement action of switch clutch C0, the rotating element of first compound planet gear 24 rotates as one unit, and the speed of the speed of the first sun wheel S1 and the first gear ring R1 keeps equating that with engine speed NE promptly the speed with the first planetary wheel carrier CA1 equates.Under the first planetary wheel carrier CA1 and the mutual not synchronous situation of the first sun wheel S1, switch clutch has because the velocity contrast between the first planetary wheel carrier CA1 and the first sun wheel S1 causes the risk of engagement vibrations when speed-changing mechanism 10 switches to the step change gearshift by engagement switch clutch C0.In other words, speed-changing mechanism 10 has the risk that switches and shake at speed-changing mechanism 10 when the stepless change gearshift switches to the step change gearshift.

Switch vibrations for reducing this, motor control assembly 82 in the present embodiment be set to when the engagement of switch clutch C0 or drg B0 (, when speed-changing mechanism 10 switches to the step change gearshift from the stepless change gearshift) control first motor M 1 speed, to reduce the first element RE1, velocity contrast between the second element RE2 and the three element RE3 or the velocity contrast between the second element RE2 and the casing 12 make and win, second and three element RE1, RE2, RE3 has and switches to the speed that the speed set up after the step change gearshift equates substantially.In other words, motor control assembly 82 control first motor M 1 makes predetermined reactive torque control first motor M 1 and makes and produced and received a predetermined reactive torque that the reactive torque of doing to produce equates by the engagement enlightening of switch clutch C0 or drg B0 by at least the first motor M 1 among first and second motor M 1, the M2, shakes in the switching of speed-changing mechanism 10 when the stepless change gearshift switches to the step change gearshift so that reduce.On the other hand, the engagement action of switching control 50 beginning switch clutch C0 or drg B0, only under the control of motor control assembly 82, the speed of first motor M 1 is controlled to reduce speed-changing mechanism 10 being switched to the step change gearshift from the stepless change gearshift after the velocity contrast or the velocity contrast between the second element RE2 and the casing 12 between first, second and three element RE1, RE2 and the RE3.

Explain, motor control assembly 82 is ordered hybrid power control setup 52 controls first motor M 1 when the engagement of switch clutch C0, make the speed of the sun wheel S1 that wins, promptly the speed NM1 of first motor changes towards engine speed NE, in other words, the torque of controlling first motor M 1 makes the speed NM1 of the motor of winning equal engine speed NE.Be controlled at switching in the process of unclamping action of switch clutch C0 and make the speed of the sun wheel S1 that wins, promptly the speed NM1 of first motor keeps equating with engine speed NE.Hybrid power control setup 52 is controlled first motor M 1 to produce the pre-determined torque that equates with the reactive torque of switch clutch C0 by control by the electric energy generation of first motor M 1.

When the stepless change gearshift switched to the step change gearshift, synchro control was finished the speed that judgment means 84 can operate to judge the first sun wheel S1 and whether has been equaled engine speed NE in the engagement action of speed-changing mechanism 10 by switch clutch C0.For example, by judging whether the speed NM1 of first motor has equaled engine speed NE under the control of motor control assembly 82, carries out this judgement.When the stepless change gearshift switched to the step change gearshift, synchro control finished whether the speed that judgment means 84 can operate to judge the first sun wheel S1 has served as zero in the engagement action of speed-changing mechanism 10 by switching drg B0.For example, under the control of motor control assembly 82, whether be zero this judgement of carrying out by the speed NM1 that judges first motor.

Whether the speed of finishing the first sun wheel S1 that judgment means 84 carries out in synchro control has equaled engine speed NE or the engagement action of exercisable switching control 50 beginning switch clutch C0 or drg B0 when whether being zero judgement.When engagement action begins,, do not need switch clutch C0 or drg B0 to produce reactive torque owing to produce predetermined reactive torque by first motor M 1.Therefore, the hydraulic pressure of switch clutch C0 or drg B0 does not need to reduce gradually, and can reduce rapidly, to be used for relatively promptly switching to the step change gearshift.

When speed-changing mechanism 10 under the control of switching control 50 when the stepless change gearshift switches to the step change gearshift, motor control assembly 82 continues the control of first motor M 1, up to the moment that the engagement action of switch clutch C0 or drg B0 is finished, to be used to keep predetermined reactive torque,, thereby or make the speed of the sun wheel S1 that wins remain the zero engagement vibrations that reduce to switch drg B0 so that thereby the speed of the first sun wheel S1 keeps equating to reduce the engagement vibrations of switch clutch C0 with engine speed NE.When the engagement action of switch clutch C0 or drg B0 was finished, switch clutch or drg temporarily received two kinds of different torques.For example, by the reactive torque that first motor M 1 produces, make the torque that is produced equal actual engine torque Te by 52 controls of hybrid power control setup.

The essential judgment means 86 of driving engine output control is set judges the Magnification that in speed-changing mechanism switches to the process of step change gearshift, whether must temporarily reduce motor torque Te or driving engine output, perhaps the Magnification with motor torque Te or driving engine output is restricted to the value that is not higher than predetermined limits, to prevent surpassing the predetermined upper limit of being determined by the rated value of first motor M 1 by the electric energy of 1 generation of first motor M and supply.

Engine output controller 88 is set with when obtaining sure judgement by the essential judgment means 86 of driving engine output control, temporarily reduce the Magnification of motor torque Te or driving engine output, perhaps the Magnification of limiting engine torque Te or driving engine output.

Figure 17 is a diagram of circuit of explaining the major control operation of being carried out by control electronics 40, that is, and and the control routine of when the stepless change gearshift switches to the step change gearshift, carrying out at speed-changing mechanism 10.This control routine extremely repeats with for example approximate number millisecond tens of milliseconds very short period.Figure 19 and 20 is the sequential charts that are used to explain the example of control operation as shown in figure 17.The sequential chart of Figure 19 show when switch clutch C0 engagement being used for the control operation when the stepless change gearshift switches to the step change gearshift, and the sequential chart of Figure 20 shows when switching drg and meshes to be used for the control operation when the stepless change gearshift switches to the step change gearshift.

The switching controls routine judges with step SB1 (after this will omit " step " this speech) beginning corresponding to vehicle condition judgment means 80 whether acceleration pedal unclamps.Operational ton based on acceleration pedal carries out this judgement.When obtaining definite results in SB1, control flow proceeds to also corresponding to the SB2 of vehicle condition judgment means 80, judges by actual vehicle speed V and the demand output torque T that calculates based on the operational ton of acceleration pedal _OUTWhether represented vehicle condition changes, and switches to the step change gearshift to require speed-changing mechanism 10 from the stepless change gearshift.For example, the figure according to Figure 18 carries out changing this relevant judgement with vehicle condition.If obtain negative result at SB1 or SB2, then control flow proceeds to SB8 to keep the current driving state of vehicle.These steps SB1 and SB2 can be revised as single step and judge whether speed-changing mechanism 10 should switch to the step change gearshift from the stepless change gearshift.This judgement can by as judge and carry out, that is, and by judge whether to judge high output vehicle ', hot-short travels and the circuit function deterioration in any.

When all obtaining definite results among SB1 and the SB2 (at the time point t shown in Figure 19 and 20 ₁The place), control flow proceeds to the SB3 corresponding to motor control assembly 82, control first motor M 1 with for example establishing under grade situation of speed-change and gearshift state by engagement switch clutch C0, the speed (i.e. the speed NM1 of first motor M 1) of the sun wheel S1 that wins is equated with engine speed NE.That is, first motor M 1 is controlled to be produced as and makes speed NM1 maintenance equate required predetermined reactive torque with engine speed NE.Establishing under grade situation of speed-change and gearshift state by engagement switching drg B0, the speed (i.e. the speed NM1 of first motor) of controlling the first sun wheel S1 is to become zero.That is, controlling first motor M 1 makes the first sun wheel S1 keep static required predetermined reactive torque to be produced as.This control to reactive torque takes place during from the time point t1 shown in Figure 19 and 20 to the time period of time point t3.Then, control flow proceeds to synchro control and finishes judgment means 84 cooresponding SB4, judges in the engagement by switch clutch C0 to establish under grade situation of speed-change and gearshift state whether the speed of the first sun wheel S1 has equaled engine speed NE.For example, by judging whether speed NM1 by first motor M 1 has equaled engine speed NE and carried out this judgement.For example establishing under grade situation of speed-change and gearshift state switching drg B0 by engagement, whether the speed NM1 by judging first motor has been whether zero to come the speed of the first sun wheel S1 be zero to judge.

Repeat SB3 up in SB4, obtaining definite results.When in SB4, to negate as a result the time, control flow proceeds to the SB6 corresponding to the essential judgment means 86 of driving engine output control, judge whether temporarily to reduce the Magnification of motor torque Te or driving engine output, perhaps the Magnification with motor torque Te or driving engine output is restricted to the value that is not higher than predetermined limits, finishes up to the engagement action of switch clutch C0 or drg B0.If obtain definite results at SB6, then control flow proceeds to the SB7 corresponding to engine output controller 88, by open angle that for example reduces throttle gate or the amount of fuel that is fed to driving engine 8, perhaps postpone the engine ignition timing, reduce motor torque (from the time point t shown in Figure 19 and 20 ₃To time point t ₄Time period during).If obtain the result that negates at SB6, or after carrying out SB7, control flow is got back to SB3.

If obtain definite results at SB4, then control flow proceeds to the SB5 corresponding to switching control 50, and the engagement action that begins switch clutch C0 or drg B0 is (at the time point t shown in Figure 19 and 20 ₃The place).Because when when SB4 obtains definite results, having produced predetermined reactive torque by first motor M 1, so in the process of engagement action, do not need switch clutch C0 or drg B0 to produce reactive torque, the hydraulic pressure of switch clutch C0 or drg B0 does not need to increase gradually thus, therefore can increase rapidly.Shown in Figure 19 and 20 from time point t ₃To time point t ₄Time period during the rapid increase of this hydraulic pressure takes place.Therefore after the engagement action of switch clutch C0 or drg B0 was finished, first motor M 1 did not need to produce reactive torque, and the control to first motor that produces reactive torque stops.Though not shown this of the diagram of circuit of Figure 17 stops, Figure 19 and 20 shows at time point t ₄The place stops to produce reactive torque by first motor M 1, after this places control vehicle under the situation under the step change gearshift at speed-changing mechanism.

As the execution result of this control routine, engagement switch clutch C0 when the speed of the first sun wheel S1 equals engine speed NE reduces the engagement vibrations of switch clutch C0 thus.Alternatively, the first sun wheel S1 its speed be under zero the situation static in engagement switch drg B0, reduce to switch the engagement vibrations of drg B0 thus.In addition, switch clutch C0 or drg B0 in the process of its engagement action or under its partial tooth engagement state (shown in Figure 19 and 20 from time point t ₃To time point t ₄Time period during) input and output speed between velocity contrast reduce, reduced thus that switch clutch C0 or drg B0 go up because the load that skidding produces, thereby improved the durability degree of switch clutch or drg.

As mentioned above, first motor M 1 of motor control assembly 82 (SB3) control speed-changing mechanism 10, speed-changing mechanism 10 comprises power splitting mechanism 16, power splitting mechanism 16 has the first element RE1 (the first planetary wheel carrier CA1) that is fixed to driving engine 8, be fixed to the second element RE2 (the first sun wheel S1) of first motor M 1 and the three element RE3 (the first gear ring R1) that is fixed to second motor M 2 and power transfer member 18, and comprise and being used for the first and second element RE1, interconnected switch clutch C0 of RE2 and the switching drg B0 that is used for the second element RE2 is fixed to casing 12, and power splitting mechanism 16 therein power splitting mechanism 16 as the stepless change gearshift of electric steplessly variable transmission work with wherein switch between the step change gearshift of power splitting mechanism 16 as step change transmission work.When the engagement of switch clutch C0 or drg, motor control assembly 82 control first motor M 1 is to reduce velocity contrast between the second element RE2 and the first element RE1 or the velocity contrast between the second element RE2 and the casing 12, make and reduced because the engagement vibrations that above-mentioned velocity contrast causes, the result has reduced to switch vibrations, and reduce the velocity contrast between the input and output speed of switch clutch C0 or drg B0, the result has reduced the load when its partial tooth engagement state on switch clutch or the drg, and has improved the durability degree of switch clutch C0 or drg B0 thus.Should also be noted that, power splitting mechanism 16 is made of simply three elements and switch clutch C0 and drg B0, and easily speed-changing mechanism 10 is being switched between stepless change and step change gearshift by switch clutch C0 or drg B0 under the control of switching control 50.

Also be arranged so that at speed-changing mechanism 10 switching control when the stepless change gearshift switches to the step change gearshift according to control convenience of the present invention and can operate to begin the engagement action of switch clutch C0 or drg B0 reduce velocity contrast between first, second and three element RE1, RE2, the RE3 or the velocity contrast between the second element RE2 and the casing 12 in speed after by motor control assembly 82 controls first motor M 1.Therefore, the speed of each rotating element is controlled to change to the value of setting up after switching to the step change gearshift, the switching vibrations that make switch clutch C0 or drg B0 cause owing to velocity contrast when engagement reduce, and switch clutch C0 or the drg B0 difference between the input and output speed under its partial tooth engagement state reduces, thereby reduce the load on switch clutch or the drg, this has brought the raising of the durability degree of switch clutch C0 or drg B0.

Control convenience according to present embodiment also comprises engine output controller 88 (SB7), it is used to control the torque Te or the output of driving engine 8, make motor torque Te or output be limited to prevent that it from surpassing the predetermined upper limit of being determined by the rated value of first motor M 1, finishes up to the engagement action of the switch clutch C0 that is controlled by switching control 50.For example, the demand of travelling in response to the high output of vehicle at speed-changing mechanism 10 is when the stepless change gearshift switches to the step change gearshift, even do not have high output area capacity corresponding or output with driving engine 8 in first motor M 1, speed-changing mechanism 10 was also suitably remained on its stepless change gearshift before switching to the step change gearshift.

The 5th embodiment

Figure 21 is a diagram of circuit of explaining the major control operation of control electronics 40, that is, and and the routine of carrying out when switching to lockup state from differential state (non-lockup state) in switchable type change-speed box part 11 (that is, power splitting mechanism 16).This control routine extremely repeats with for example approximate number millisecond tens of milliseconds very short period.Figure 22 is the sequential chart that is used to explain the example of the control operation shown in the diagram of circuit of Figure 21, carries out when the non-lockup state of this control operation switches to the lockup state of being set up by the engagement action of switch clutch C0.

The difference of the control routine of the diagram of circuit of Figure 21 and the diagram of circuit of Figure 17 is, the control routine of Figure 21 is applied to the switching from non-lockup state to non-lockup state that switchable type change-speed box part 11 is undertaken by engagement switchable type power-transfer clutch C0 or drg B0, switches vibrations to reduce.In this regard, notice that the switching of speed-changing mechanism 10 from the stepless change gearshift to the step change gearshift can be thought and be equal to switchable type change-speed box part 11 switching from non-lockup state to lockup state.

Control routine judges with the SB1 ' beginning corresponding to vehicle condition judgment means 80 whether acceleration pedal is pressed.Operational ton based on acceleration pedal carries out this judgement.When in the middle acquisition definite results of SB1 ', control flow proceeds to also corresponding to the SB2 ' of vehicle condition judgment means 80, judges by actual vehicle speed V with based on the demand output torque T of the operational computations of acceleration pedal _OUTWhether the vehicle condition of expression changes, to such an extent as to require switchable type change-speed box part 11 to switch to lockup state from non-lockup state.For example, the figure according to Figure 18 carries out changing this relevant judgement with vehicle condition.If in SB1 ' or the negative result of SB2 ' acquisition, then control flow proceeds to SB8 ' to keep the current driving state of vehicle.These steps SB1 ' and SB2 ' can be revised as single step and judge whether switchable type change-speed box part 11 should switch to lockup state from non-lockup state.This judgement can by as judge and carry out, that is, and by judge whether to judge high output vehicle ', hot-short travels and the circuit function deterioration in any.

When SB1 ' and SB2 ' obtain definite results among both (at time point t as shown in figure 22 ₁The place), for example setting up under the situation of lockup state by engagement switch clutch C0, control flow proceeds to the SB3 ' corresponding to motor control assembly 82, controls the speed (i.e. the speed NM1 of first motor M 1) that first motor M 1 makes the sun wheel S1 that wins and equals engine speed NE.That is, first motor M 1 is controlled to be produced as and makes speed NM1 maintenance equate required predetermined reactive torque with engine speed NE.Set up under the situation of lockup state by engagement switching drg B0, the speed of the first sun wheel S1 (i.e. the speed NM1 of first motor) is controlled as zero.That is, first motor M 1 is controlled to be produced as and makes the static required predetermined reactive torque of the first sun wheel S1.As shown in figure 22 from time point t ₁To time point t ₃Time period during this control to reactive torque takes place.Then, control flow proceeds to synchro control and finishes judgment means 84 cooresponding SB4 ', judges whether the speed of the first sun wheel S1 under the situation of setting up lockup state by engagement switch clutch C0 has equaled engine speed NE.For example, whether equal engine speed NE by the speed NM1 that judges first motor M 1 and carried out this judgement.Whether for example setting up under the situation of lockup state by engagement switching drg B0, be whether zero speed of carrying out the first sun wheel S1 has been zero judgement by judging the first rotating speed of motor NM1.

Repeat SB3 ' up in SB4 ', obtaining definite results.When obtain among the SB4 ' negating as a result the time, control flow proceeds to and the essential judgment means 86 cooresponding SB6 ' of driving engine output control, judge whether temporarily to reduce the Magnification of motor torque Te or driving engine output, perhaps the Magnification with motor torque Te or driving engine output is restricted to the value that is not higher than predetermined limits, finishes up to the engagement action of switch clutch C0 or drg B0.If obtain definite results at SB6 ', then control flow proceeds to the SB7 ' corresponding to engine output controller 88, by open angle that for example reduces throttle gate or the amount of fuel that is fed to driving engine 8, perhaps postpone the engine ignition timing, reduce motor torque (as shown in figure 22 from time point t ₃To time point t ₄Time period during).If obtain the result that negates at SB6 ', or carrying out SB7 ' afterwards, control flow is got back to SB3 '.

If obtain definite results at SB4 ', then control flow proceeds to the SB5 ' corresponding to switching control 50, and the engagement action that begins switch clutch C0 or drg B0 is (at time point t as shown in figure 22 ₃The place).Because when when SB4 ' obtains definite results, having produced predetermined reactive torque by first motor M 1, so in the process of engagement action, do not need switch clutch C0 or drg B0 to produce reactive torque, the hydraulic pressure of switch clutch C0 or drg B0 does not need to increase gradually thus, and therefore can increase rapidly.As shown in figure 22 from time point t ₃To time point t ₄Time period during the rapid increase of this hydraulic pressure takes place.Therefore after the engagement action of switch clutch C0 or drg B0 was finished, first motor M 1 did not need to produce reactive torque, and the control to first motor that produces reactive torque stops.Though not shown this of the diagram of circuit of Figure 21 stops, Figure 22 shows at time point t ₄The place stops to produce reactive torque by first motor M 1, after this partly places control vehicle under the situation under the lockup state at the switchable type change-speed box.

As the execution result of this control routine, engagement switch clutch C0 when the speed of the first sun wheel S1 equals engine speed NE reduces the engagement vibrations of switch clutch C0 thus.Alternatively, the first sun wheel S1 its speed be under zero the situation static in engagement switch drg B0, reduce to switch the engagement vibrations of drg B0 thus.In addition, switch clutch C0 or drg B0 in the process of its engagement action or under its partial tooth engagement state (as shown in figure 22 from time point t ₃To time point t ₄Time period during) input speed and the velocity contrast between the output speed reduce, reduced thus that switch clutch C0 or drg B0 go up because the load that skidding produces, thereby improved the durability degree of switch clutch or drg.

About the switching controls when the switching of speed-changing mechanism 10 by the gearshift of unclamping switch clutch C0 or drg B0 and carrying out, have and the identical advantage of control convenience according to previous embodiment according to the control convenience of present embodiment, this is because the switching of speed-changing mechanism 10 from the stepless change gearshift to the step change gearshift is equal to switchable type change-speed box part 11 switching from non-lockup state to lockup state.

The 6th embodiment

Formerly among the embodiment, only velocity contrast between the first element RE1, the second element RE2 and the three element RE3 or the velocity contrast between the second element RE2 and the casing 12 reduce just to begin the engagement action of switch clutch C0 or drg B0 by switching control 50 after the switching vibrations when reducing switch clutch C0 or drg B0 engagement under by the situation of the speed of motor control assembly 82 control first motor M 1.The difference of present embodiment and previous embodiment is the engagement action of switching control 50 in present embodiment control switch clutch C0 or drg B0 in by the process of the speed control of 82 pairs first motor M 1 of motor control assembly, this speed control is in order to reduce first, second and three element RE1, velocity contrast between velocity contrast between RE2 and the RE3 or the second element RE2 and the casing 12, switch clutch C0 or drg B0 are meshed, so that reduce speed-changing mechanism 10 is being switched to the step change gearshift or with the switching vibrations of switchable type change-speed box part 11 (power splitting mechanism 16) when non-lockup state switches to lockup state from the stepless change gearshift under the control of switching control 50.In addition, the motor control assembly in the present embodiment 82 is set to reduce the reactive torque of first motor M 1 in switch clutch C0 or drg B0 are in the process of the engagement action under the control of switching control 50.

Particularly, slowly ingear is simultaneously to make switch clutch C0 at switching control 50 control switch clutch C0, motor control assembly 82 controls first motor makes the speed of the sun wheel S1 that wins equal engine speed NE, to reduce the engagement vibrations of switch clutch C0.Promptly, present embodiment is set to carry out what is called " overlapping switching and electric machine control ", the wherein engagement action of the switch clutch C0 under the control of switching control 50 and the control of being undertaken by motor control assembly 82 to the speed of first motor M 1 (that is, to the control of the torque of first motor M 1 so that motor speed NM1 keep equating with engine speed NE) is carried out simultaneously.

The result, at switch clutch C0 when it unclamps reactive torque in the process of action and increases gradually, the reactive torque that is produced by first motor M 1 under the control of motor control assembly 82 reduces gradually, and the reactive torque that makes the reactive torque of the motor M 1 of winning be switched power-transfer clutch C0 in the process of the engagement action of switch clutch C0 replaces.For example, switch clutch C0 slowly ingear simultaneously, the speed of the first sun wheel S1, promptly the speed NM1 of first motor is fed control and equates with engine speed NE keeping.

Alternatively, when switching control 50 controls switching drg B0 made that switching drg B0 slowly meshes, it was zero that motor control assembly 82 controls first motor M 1 makes the speed of the sun wheel S1 that wins, to reduce the engagement vibrations of switching drg B0.Promptly, present embodiment is set to execution so-called " overlapping switching and electric machine control ", wherein switches the engagement action of drg B0 under the control of switching control 50 and is controlled by the torque of 82 pairs first motor M 1 of motor control assembly so that the speed NM1 of first motor M 1 is zero generation simultaneously.

The result, increase gradually along with switching the reactive torque of drg B0 in the process of its engagement action, the reactive torque that is produced by first motor M 1 reduces gradually, makes the reactive torque of the motor M 1 of winning be switched the reactive torque replacement of drg B0 in the process of its engagement action gradually.For example, switch drg B0 slowly ingear simultaneously, the speed NM1 of first motor is fed control to remain zero.

Figure 23 is the sequential chart that is used to explain the control operation of engagement action when the stepless change gearshift switches to the step change gearshift by switch clutch C0.Example shown in the sequential chart of Figure 23 is the possibility for the example shown in the sequential chart of Figure 19.Figure 24 is the sequential chart that is used to explain the control operation of engagement action when the stepless change gearshift switches to the step change gearshift by switching drg B0.Example shown in the sequential chart of Figure 24 is the possibility for the example shown in the sequential chart of Figure 20.Figure 25 is the sequential chart that is used to explain the control operation of engagement action when non-lockup state switches to lockup state by switch clutch C0.Example shown in the sequential chart of Figure 25 is the possibility for the example shown in the sequential chart of Figure 22.

Though Figure 19,20 and 22 example are set to increase rapidly the hydraulic pressure of switch clutch C0 or drg B0 in the predetermined reactive torque that produces first motor M 1, but the example of Figure 23-25 is set to carry out overlapping switching and electric machine control, and wherein the speed control of the engagement action of switch clutch C0 or drg B0 and first motor M 1 takes place simultaneously to produce predetermined reactive torque.Thus, the difference of the example of Figure 23 and 24 example and Figure 19 and 20 is that the step SB5 in the example of the step SB3 of Figure 17 and SB4 and Figure 23 and 24 carries out simultaneously.Similarly, the difference of the example of the example of Figure 25 and Figure 22 is that the step SB5 ' in the example of the step SB3 ' of Figure 21 and SB4 ' and Figure 25 carries out simultaneously.

Explain, in the process of the engagement action of switch clutch C0, when the speed of the first sun wheel S1, promptly the speed NM1 of first motor is fed control when keeping equating with engine speed NE, and switch clutch C0 is from time point t in the example of Figure 23 ₃To time point t ₄Time period during with the speed engagement lower than the example of Figure 19, switch clutch C0 is from time point t in the example of Figure 11 ₂To time point t ₄Time period during promptly the engagement.That is, the torque of control first motor M 1 in the process of the engagement action of switch clutch C0 makes the speed NM1 of the motor of winning keep equating with engine speed NE.At time point t shown in Figure 23 ₄Afterwards, the vehicle of carrying out under the step change gearshift of speed-changing mechanism 10 is controlled.

Similarly, in the process of the engagement action of switching drg B0, when the speed of the first sun wheel S1, promptly the speed NM1 of first motor is fed control when remaining zero, switches drg B0 in the example of Figure 24 from time point t ₃To time point t ₄Time period during with the speed engagement lower than the example of Figure 20, in the example of Figure 20, switch drg B0 from time point t ₃To time point t ₄Time period during promptly the engagement.That is, the torque of control first motor M 1 in the process of the engagement action of switching drg B0 makes the speed NM1 of the motor of winning remain zero.At time point t shown in Figure 24 ₄Afterwards, the vehicle of carrying out under the step change gearshift of speed-changing mechanism 10 is controlled.

Similarly, in the process of the engagement action of switch clutch C0, when the speed of the first sun wheel S1, promptly the speed NM1 of first motor is fed control when keeping equating with engine speed NE, and switch clutch C0 is from time point t in the example of Figure 25 ₃To time point t ₄Time period during with than in the example of Figure 22 with the engagement of lower speed, switch clutch C0 is from time point t in the example of Figure 22 ₃To time point t ₄Time period during promptly the engagement.That is, the torque of first motor M 1 reduces gradually in the process of the engagement action of switch clutch C0, makes the speed NM1 of the motor of winning keep equating with engine speed NE.At time point t shown in Figure 25 ₄Afterwards, the vehicle of carrying out under the lockup state of switchable type change-speed box part 11 is controlled.

As a result, be controlled to and engagement switch clutch C0 when engine speed NE equates, make the engagement vibrations that reduce switch clutch C0 in the speed of the first sun wheel S1.Alternatively, drg B0 is switched in engagement when the speed of the first sun wheel S1 is controlled as zero, makes to reduce the engagement vibrations of switching drg B0.In addition, reduced switch clutch C0 or drg B0 when its engagement action or under its partial tooth engagement state (shown in Figure 23-35 from time point t ₃To time point t ₄Time period during) input and output speed between poor, the result has reduced on switch clutch or the drg because the load that skidding produces, and has therefore improved the durability degree of switch clutch or drg.

In Figure 23,24 and 25 example, can depend on that vehicle velocity V or motor torque Te control the Magnification of the hydraulic pressure of the Magnification gradually of torque of first motor M 1 or switch clutch C0 or drg B0, can carry out so-called overlapping switching and electric machine control, make to reduce motor torque simultaneously at switch clutch C0 or drg B0 ingear.

As mentioned above, according to the control convenience of present embodiment be arranged so that speed-changing mechanism 10 when the stepless change gearshift switches to the step change gearshift (, in switchable type change-speed box part 11 (power splitting mechanism 16) when non-lockup state switches to lockup state) switching control 50 can operate, with can by the speed control of 82 pairs first motor M 1 of motor control assembly to reduce first, second and three element RE1, RE2, carry out the engagement action of switch clutch C0 or drg B0 in the process of the velocity contrast between the velocity contrast between the RE3 or the second element RE2 and the casing 12.According to this setting, the speed of each rotating element is controlled to change to the value of setting up after switching to the step change gearshift, reduce thus because the switching vibrations that the velocity contrast the during engagement of Coupling device causes, and reduced Coupling device poor between the input and output speed under its partial tooth engagement state, thereby reduced the load on the Coupling device, the result has improved the durability degree of Coupling device.

Also be arranged so that at speed-changing mechanism 10 when the stepless change gearshift switches to the step change gearshift according to the control convenience of present embodiment, or in switchable type change-speed box part 11 (power splitting mechanism 16) when non-lockup state switches to lockup state, in the engagement action of carrying out switch clutch C0 or drg B0 by the speed control of 82 pairs first motor M 1 of motor control assembly in the process that reduces velocity contrast between the first element RE1, the second element RE2 and the three element RE3 or the velocity contrast between the second element RE2 and the casing 12.Therefore, the speed of each rotating element is controlled so as to the value of setting up after the step change gearshift for switching to when the engagement action of switch clutch C0 or drg B0 is finished, reduce thus because the switching vibrations that the velocity contrast the during engagement of switch clutch C0 or drg B0 causes.In addition, reduced poor between the input and output speed under its partial tooth engagement state of switch clutch C0 or drg B0, thereby reduced the load on switch clutch or the drg, the result has improved the durability degree of switch clutch C0 or drg B0.

With wherein first, second and three element RE1, after reducing, velocity contrast between velocity contrast between RE2 and the RE3 or the second element RE2 and the casing 12 begins the engagement action of switch clutch C0 or drg B0, the previous embodiment difference of the switching vibrations when reducing the engagement of switch clutch C0 or drg B0, present embodiment is set to first, second and three element RE1, the engagement action of beginning switch clutch C0 or drg B0 in the process that above-mentioned velocity contrast between above-mentioned velocity contrast between RE2 and the RE3 or the second element RE2 and the casing 12 reduces.Except the difference of above-mentioned control, present embodiment has and the previous identical advantage of embodiment.

The 7th embodiment

Figure 26 is can be by the scheme drawing of the layout of the speed-changing mechanism 70 of control convenience according to the present invention control, and Figure 27 is the table of various combination of the serviceability of the gear and being used for of the expression speed-changing mechanism 70 hydraulic operation friction Coupling device of setting up these gears respectively, and Figure 28 is the alignment chart that is used to explain the gear-change operation of speed-changing mechanism 70.

Speed-changing mechanism 70 comprises switchable type change-speed box part 11, and with identical among first embodiment, it has the first electrical motor M1, power splitting mechanism 16 and the second electrical motor M2.Speed-changing mechanism 70 also comprises the automatic transmission with hydraulic torque converter part 72 with three forerunner positions.Automatic transmission with hydraulic torque converter part 72 is arranged between switchable type change-speed box part 11 and the output shaft 22, and is connected in series to switchable type change-speed box part 11 and output shaft 22 by power transfer member 18.Identical with first embodiment, power splitting mechanism 16 comprises first compound planet gear 24, the switch clutch C0 of the single-stage planetary gear type with transmitting ratio ρ 1 of for example about 0.418 and switches drg B0.The third line star gear cluster 28 that automatic transmission with hydraulic torque converter part 72 comprises second compound planet gear 26 of the single-stage planetary gear type with transmitting ratio ρ 2 of for example about 0.532 and has the single-stage planetary gear type of for example about 0.418 transmitting ratio ρ 3.Second sun wheel S2 of second compound planet gear 26 and the 3rd sun wheel S3 of the third line star gear cluster 28 are fixed to one another integratedly as one unit, optionally be connected to power transfer member 18 by second clutch C2, and optionally be fixed to mission case 12 by the first drg B1.Second planetary wheel carrier CA2 of second compound planet gear 26 and the 3rd gear ring R3 of the third line star gear cluster 28 are fixed to one another integratedly and be fixed to output shaft 22.The second gear ring R2 optionally is connected to power transfer member 18 by first clutch C1, and the third line star wheel frame CA3 optionally is fixed to housing 12 by the second drg B2.

In the speed-changing mechanism 70 of as above constructing, by from above-mentioned switch clutch C0, first clutch C1, second clutch C2, switch the engagement action of the respective combination of the friction Coupling device of selecting drg B0, the first drg B1 and the second drg B2, optionally set up first gear (the first fast position) to the fourth speed position one of (the 4th fast position), backing car gear (activation point backward) and Neutral Position.These gears have into different speed ratio γ (the drive shaft speed N that geometric series changes _IN/ output shaft speed N _OUT).Especially, notice that the power splitting mechanism 16 that is provided with switch clutch C0 and drg B0 can be selectively placed on fixed speed ratio gearshift and stepless change gearshift by the engagement of switch clutch C0 or switching drg B0, mechanism 16 can be used as the change-speed box with one or more fixed speed ratios in the fixed speed ratio gearshift, and mechanism 16 can be used as toric transmission as described above in the stepless change gearshift.So in this speed-changing mechanism 70, constitute step change transmission by automatic transmission with hydraulic torque converter part 20 with by the switchable type change-speed box part 11 that the switch clutch C0 or the engagement of switching drg B0 are placed in the fixed speed ratio gearshift.In addition, by automatic transmission with hydraulic torque converter part 20 with when all not being engaged among switch clutch C0 and the drg B0 and place the switchable type change-speed box part 11 of stepless change gearshift to constitute toric transmission.In other words, speed-changing mechanism 70 is switched to the step change gearshift by engagement switch clutch C0 and of switching among the drg B0, and by unclamping switch clutch C0 and drg B0 is switched to the stepless change gearshift.

Be used as under the situation of step change transmission at speed-changing mechanism 70, for example, engagement action by switch clutch C0, first clutch C1 and the second drg B2 set up have for example about 2.804 the most at a high speed than first gear of γ 1, and set up second gear with speed ratio γ 2 (being lower than speed ratio γ 1) of for example about 1.531 by the engagement action of switch clutch C0, first clutch C1 and the first drg B1, as shown in figure 23.In addition, set up third gear by the engagement action of switch clutch C0, first clutch C1 and second clutch C2, and set up fourth speed position with speed ratio γ 4 (being lower than speed ratio γ 3) of for example about 0.705 by first clutch C1, second clutch C2 and the engagement action of switching drg B0 with speed ratio γ 3 (being lower than speed ratio γ 2) of for example about 1.000.In addition, the engagement action by the second clutch C2 and the second drg B2 is set up the backing car gear with speed ratio γ R (it is between speed ratio γ 1 and γ 2) of for example about 2.393.Set up Neutral Position N by only meshing switch clutch C0.

On the other hand, when speed-changing mechanism 70 is used as toric transmission, as shown in figure 27.Switch clutch C0 and switching drg B0 both are released, make switchable type change-speed box part 11 as toric transmission, the automatic transmission with hydraulic torque converter part 72 that is connected in series to switchable type change-speed box part 11 simultaneously is as step change transmission, be passed to first the speed that rotatablely moves that places thus to the automatic transmission with hydraulic torque converter part 72 of one of third gear, the rotating speed that is power transfer member 18 is changed continuously, makes that the speed ratio of speed-changing mechanism 10 can change on preset range continuously when automatic transmission with hydraulic torque converter part 72 is placed in one of above-mentioned gear.So the speed ratio of automatic transmission with hydraulic torque converter part 72 can change on adjacent gear continuously, the overall ratio γ T of speed-changing mechanism 70 can change continuously thus.

The alignment chart of Figure 28 is represented relation between the rotating speed of rotating element in each gear of speed-changing mechanism 70 with straight line, and speed-changing mechanism 70 is by constituting as the switchable type change-speed box part 11 of stepless change gear shift part or first gear shift part with as the automatic transmission with hydraulic torque converter part 72 of step change gear shift part or second gear shift part.The alignment chart of Figure 28 is represented the rotating speed of each element of power splitting mechanism 16 when switch clutch C0 and drg B0 both unclamp and the rotating speed of these elements as switch clutch C0 or when switching drg B0 engagement, this with previous embodiment in identical.

When first clutch C1 and second drg B2 engagement, automatic transmission with hydraulic torque converter part 72 is placed in first gear.The rotating speed of output shaft 22 is fixed to the perpendicular line Y6 of rotating speed of the 6th rotating element RE6 of output shaft 22 and the intersection point between the angled straight lines L1 is represented in first gear by expression, angled straight lines L1 is through the intersection point of expression perpendicular line Y7 of the 7th rotating element RE7 (R2) rotating speed and horizon X2 and represent the perpendicular line Y5 of the 5th rotating element RE5 (CA3) rotating speed and the intersection point between the horizon X1, as shown in figure 28.Similarly, the rotating speed of the output shaft 22 in second gear that the engagement action by the first clutch C1 and the first drg B1 is set up, by by the determined angled straight lines L2 of these engagement action and the intersection point of representing to be fixed between the perpendicular line Y6 of rotating speed of the 6th rotating element RE6 (CA2, R3) of output shaft 22 represent.The rotating speed of the output shaft 22 in the third gear that the engagement action by first clutch C1 and second clutch C2 is set up is represented by the intersection point between the perpendicular line Y6 of the rotating speed of the 6th rotating element RE6 that is fixed to output shaft 22 by determined angled straight lines L3 of these engagement action and expression.First gear that is placed in engagement at switch clutch C0 is receiving under the situation of propulsive efforts from switchable type change-speed box part 11 to third gear, the 7th rotating element RE7 with engine speed N _EIdentical speed rotation.When switching drg B0 replaces switch clutch C0 to be engaged, receiving under the situation of propulsive efforts from switchable type change-speed box part 11, the 6th rotating element RE6 is to be higher than engine speed N _ESpeed rotation.By first clutch C1, second clutch C2 with switch the rotating speed of the output shaft 22 in the fourth speed position that the engagement action of drg B0 sets up, represent by the intersection point between the perpendicular line Y6 of the rotating speed of the 6th rotating element RE6 that is fixed to output shaft 22 by determined horizontal line L 4 of these engagement action and expression.

Speed-changing mechanism 70 also constitutes by the switchable type change-speed box part 11 that is used as stepless change gear shift part or first gear shift part with as step change gear shift part or second gear shift automatic transmission with hydraulic torque converter part 72 partly, so this speed-changing mechanism 70 has and the first embodiment confers similar advantages.

The 8th embodiment

Figure 29 is the scheme drawing that is used to explain the power splitting mechanism 92 of switchable type change-speed box part 90, and power splitting mechanism 92 is the possibilities for the power splitting mechanism among the previous embodiment 16.

Power splitting mechanism 92 comprise as main portion see as lower member, known finishing bevel gear cuter formula differential gear equipment 94, switch clutch C0 and switch drg B0.This differential gear equipment 94 comprises: the first finishing bevel gear cuter BE1; Gear case 98, it supports the first finishing bevel gear cuter BE1 makes the finishing bevel gear cuter BE1 that wins can be around its axis and around the rotation of the axis of differential gear equipment 94; Middle tap gear B E2; With third hand tap gear B E3, it is by the first finishing bevel gear cuter BE1 and middle tap gear B E2 engagement.Gear case 92 is corresponding to the first element RE1, and middle tap gear B E2 is corresponding to the second element RE2, and third hand tap gear B E3 is corresponding to three element RE3.

In this power splitting mechanism 92, gear case 92 is operably connected to a pair of countershaft-gear 96, and it is corresponding to input shaft 14 and have for example 1.0 transmitting ratio.That is, gear case 92 is operably connected to driving engine 8 by a pair of countershaft-gear 96.Middle tap gear B E2 is fixed to first motor M 1, and third hand tap gear B E3 is fixed to power transfer member 18.Switch drg B0 and be arranged between middle tap gear B E2 and the gear case 92, and switch clutch C0 is arranged between middle tap gear B E2 and the gear case 92.When these switch clutchs C0 and drg B0 are in releasing orientation, gear case 92 and second and third hand tap gear B E2, BE3 can relative to each other rotate, make the output of driving engine 8 be assigned to first motor M 1 and power transfer member 18, and a part that is assigned to driving engine 8 outputs of first motor M 1 is converted into electric energy, and this electric energy is stored or is fed to second motor M 2.So power splitting mechanism 92 places so-called stepless change gearshift (automatically controlled CVT state), no matter wherein the speed of driving engine 8 how, the speed of power transfer member 18 is stepless variable all.Promptly, switchable type change-speed box part 11 places the stepless change gearshift, and wherein change-speed box part 11 is as the electric steplessly variable transmission of speed ratio (countershaft-gear is to the speed of speed/Poewr transmission mechanism spare 18 of 96) from minimum value γ 0min to maxim γ 0max stepless variable.

When during vehicle travels under the stepless change gearshift with switchable type change-speed box part 90, meshing switch clutch C0 under the output of driving engine 8, middle tap gear B E2 and gear case 92 are connected to each other, make as the gear case 92 of three elements of differential gear equipment 94 and second and third hand tap gear B E2, BE3 rotate together as one unit, make the speed of driving engine 8 and the speed of power transfer member 18 be equal to each other thus.As a result, switchable type change-speed box part 90 places the fixed speed ratio gearshift, and wherein change-speed box part 90 is as the change-speed box with fixed speed ratio of 1.0.When switching drg B0 replacement switch clutch C0 engagement, it is static that middle tap gear B E2 keeps, and makes the speed of third hand tap gear B E3 be higher than the speed of gear case 92,, is higher than engine speed N that is _E, switchable type change-speed box part 90 places the fixed speed ratio gearshift thus, and wherein change-speed box part 90 is as the speedup change-speed box with the transmitting ratio that is lower than 1.0 (for example, 0.7).So, switch clutch C0 that present embodiment is provided with and switching drg B0 are as differential state switching device, it can be operated so that switchable type change-speed box part 90 is optionally placed one of stepless change gearshift and lockup state, but change-speed box part 90 is operated as speed ratio continually varying toric transmission in the stepless change gearshift, change-speed box part 90 remains on fixed value as toric transmission operation and its speed ratio in lockup state, that is, change-speed box part 90 is as having single gear of a speed ratio or having the fixed speed ratio gearshift of transmission operating of many gears of different speed ratios.

The switchable type change-speed box part 90 of present embodiment also comprises first motor M 1, the box of tricks of power splitting mechanism 92 forms, with second motor M 2 with power transfer member 18 rotations, the output that box of tricks can be operated with the driving engine 8 that will be delivered to input shaft 14 is assigned to first motor M 1 and the Poewr transmission mechanism.Therefore, principle of the present invention can be equal to the Vehicular drive system that has been effectively applied to comprise this switchable type change-speed box part 90 that replaces the switchable type change-speed box part 11 used among the previous embodiment.

The 9th embodiment

Figure 30 shows the mutual change type switch 44 (after this being called " switch 44 ") of selecting equipment as gearshift, but its M/C is selected the differential state or the non-differential state of power splitting mechanism 16, promptly selects the stepless change gearshift or the step change gearshift of speed-changing mechanism 10.As shown in figure 30, switch 44 has the first that is designated as " step change " and is designated as the second portion of " stepless change ", and by being placed in the step change shift pattern, and by being placed in the stepless change shift pattern in its second portion PS (Push Switch) 44 in its first's PS (Push Switch) 44.

Formerly among the embodiment, based on the vehicle condition that is detected and automatically switch the gearshift of speed-changing

mechanism

10,70 according to the handoff boundary line chart of Fig. 6 or Figure 18.But the gearshift of speed-changing

mechanism

10,70 can be come manual switchover by the M/C of mutual change type switch 44.That is, switching control 50 can be set to depend on whether switch 44 places its stepless change shift pattern or step change shift pattern and optionally speed-changing

mechanism

10,70 is placed stepless change gearshift or step change gearshift.For example, when the user wishes that speed-changing

mechanism

10,70 is as toric transmission operation or when wishing to improve the fuel economy of driving engine, the user operable switch 44 of vehicle to be placing the stepless change gearshift with speed-changing

mechanism

10,70, or speed-changing

mechanism

10,70 placed the step change gearshift when changing (as the result with the gear shift action of the automatic transmission with hydraulic torque converter part 20 of step change transmission operation) alternatively when the user wishes the rhythmicity of engine speed.

Except stepless change shift pattern and step change shift pattern, switch 44 can also have midway location.When the user does not select desired gearshift etc. or wishes that speed-changing

mechanism

10,70 automatically places one of stepless change and step change gearshift, switch 44 position that can be placed in one.

Even when the gearshift of speed-changing mechanism 10 is manually selected by switch 44, also can be applicable to this speed-changing mechanism 10 according to control convenience of the present invention.

Though below described the preferred embodiments of the present invention with reference to the accompanying drawings in detail, it should be understood that the present invention can also otherwise implement.

Formerly among the embodiment, motor control assembly 82 is configured such that rotating speed and the engine speed N of the first sun wheel S1 _ESynchronously.But motor control assembly 82 does not need to be set to make speed and the engine speed N of the first sun wheel S1 _EFully synchronously, can be configured such that the speed of the sun wheel S1 that wins is towards engine speed N _EChange.Though motor control assembly 82 is configured such that also the first sun wheel S1 keeps static, motor control assembly 82 can be set to the speed of the first sun wheel S1 is reduced towards zero.These modifications make that also switching vibrations reduces, and improve the durability degree of Coupling device.

In the embodiment that is explained, when switchable type change-speed box part 11 (power distribution part 16) is selectively placed on its differential state and non-differential state, speed-changing

mechanism

10,70 is selectively placed on one of stepless change and step change gearshift, switchable type change-speed box part 11 is as the electric steplessly variable transmission operation in the differential state, and switchable type change-speed box part 11 is not operated as electric steplessly variable transmission in non-differential state.But when this change-speed box part 11 remained in the differential state, speed-changing

mechanism

10,70 can be used as step change transmission, and switchable type change-speed box part 11 is step change rather than infinite variable speed at this moment.In other words, the differential of switchable type change-speed box part 11 and non-differential state not necessarily correspond respectively to the stepless change and the step change gearshift of speed-changing

mechanism

10,70, and switchable type change-speed box part 11 is not necessarily changeable between stepless change and step change gearshift.Principle of the present invention can be applicable to any speed-changing mechanism (its switchable type change-speed box part 11 or power splitting mechanism 16) that can switch between differential state and non-differential state.

In the power splitting mechanism 16 in explanation embodiment, the first planetary wheel carrier CA1 is fixed to that driving engine 8, the first sun wheel S1 are fixed to first motor M 1 and the first gear ring R1 is fixed to power transfer member 18.But this layout is optional.Driving engine 8, first motor M 1 and power transfer member 18 can be fixed to any other element of selecting from three element CA1, S1 of first compound planet gear 24 and R1.

In the power splitting mechanism 92 in explanation embodiment, gear case 98 is fixed to driving engine 8, and middle tap gear B E2 is fixed to first motor M 1 and third hand tap gear B E3 is fixed to power transfer member 18.But this layout is optional.Driving engine 8, first motor M 1 and power transfer member 18 can be fixed to any other element that three elements (comprising gear case 92, middle tap gear B E2 and third hand tap gear B E3) from differential gear equipment 94 are selected.

Though driving engine 8 directly is fixed to input shaft 14 in explanation embodiment, driving engine 8 can be operably connected to input shaft 14 by any suitable structure such as gear or band, and not necessarily with input shaft 14 coaxial arrangement.

In the embodiment that is explained, first motor M 1 and second motor M 2 and input shaft 14 coaxial arrangement, and be respectively fixed to the first sun wheel S1 and power transfer member 18.But this layout is optional.For example, first and second motor M 1 and M2 can be operably connected to the first sun wheel S1 and power transfer member 18 respectively by gear or band.

Though above-mentioned power splitting mechanism 16 is provided with switch clutch C0 and switches drg B0, power splitting mechanism 16 not necessarily is provided with switch clutch C0 and switches drg B0.Though switch clutch C0 is set to optionally the first sun wheel S1 and the first planetary wheel carrier CA1 are connected to each other, but switch clutch C0 can be set to optionally the first sun wheel S1 and the first gear ring R1 are connected to each other, or optionally the first planetary wheel carrier CA1 and the first gear ring R1 is connected to each other.That is, switch clutch C0 can be set to connect any two elements in three elements of first compound planet gear 24.

Though above-mentioned power splitting mechanism 92 is provided with switch clutch C0 and switches drg B0, power splitting mechanism 92 not necessarily is provided with switch clutch C0 and drg B0.When switch clutch C0 is set to optionally connect middle tap gear B E2 and gear case 92, switch clutch C0 can be set to optionally just that middle tap gear B E2 and third hand tap gear B E3 are connected to each other, or optionally gear case 92 and third hand tap gear B E3 is connected to each other.That is, switch clutch C0 can be provided with any two elements in three elements that connect differential gear equipment 94.

Though engagement switch clutch C0 sets up Neutral Position N in the embodiment that is explained, switch clutch C0 not necessarily meshes to set up Neutral Position N.

The hydraulic operation friction Coupling device that is used as switch clutch C0, switching drg B0 etc. in the embodiment that is explained can be replaced by the Coupling device that magnetic motive force formula, electromagnetic type or machinery are, for example powder coupling (magnetic-powder clutch), magnetic clutch and engagement type claw clutch.

In the embodiment that is explained, second motor M 2 is fixed to power transfer member 18.But second motor M 2 can be fixed to output shaft 22 or be fixed to the rotating member of automatic transmission with hydraulic

torque converter part

20,72.

In the embodiment that is explained, automatic transmission with hydraulic

torque converter part

20,72 is arranged in drive wheel 38 and as in the power transfer path between the power transfer member 18 of the output link of switchable type change-

speed box part

11,90 or power splitting mechanism 16,92.But, automatic transmission with hydraulic

torque converter part

20,72 can be replaced by the power transmission device of any other type, for example as a kind of toric transmission (CVT) of automatic transmission with hydraulic torque converter, or similar substantially but be provided with the selection cylinder that is used for the autoshift action or the automatic transmission with hydraulic torque converter of gear shift cylinder at textural and known manual parallel twin shaft constant mesh transmission.Under the situation that toric transmission (CVT) is set, when power splitting mechanism 16 was placed in the fixed speed ratio gearshift, speed-changing mechanism was placed in the step change gearshift on the whole.The fixed speed ratio gearshift is defined as its medium power mainly by the transmission of mechanical power bang path, and does not pass through the state of the transmission of power of circuit.

In the embodiment that is explained, speed-changing

mechanism

10,70 is used for motor vehicle driven by mixed power, and wherein drive wheel 38 can not only be driven by driving engine 8 but also can be by the torque actuated of first or second motor M 1, M2.But principle of the present invention can be applicable to non-hybrid vehicle drive system, and wherein switchable type change-

speed box part

11,90 can be only as the toric transmission operation with automatically controlled CVT function.

Though automatic transmission with hydraulic

torque converter part

20,72 is connected in series to switchable type change-speed box part 11 by power transfer member 18 in the embodiment that is explained, automatic transmission with hydraulic

torque converter part

20,72 can be installed on the tween drive shaft parallel with input shaft 14 and with the tween drive shaft coaxial arrangement.In the case, switchable type change-speed box part 11 and automatic transmission with hydraulic

torque converter part

20,72 operationally are connected to each other by power transfer member 18, this power transfer member 18 adopts the form of one group of two power transfer member, for example a pair of countershaft-gear, the perhaps combination of sprocket wheel and chain.

Though be made of a compound planet gear at the embodiment medium power distributor gears of being explained 16, power splitting mechanism 16 can be constituted and is set to when placing its fixed speed ratio gearshift as the transmission operating with two or more gears by two or more compound planet gears.

Though above-mentioned switch 44 is mutual change types, switch 44 can be by single push-button switch, optionally push to two push-button switchs, lever switch, the slipping switch of a plurality of operating positions or can operate switch or switchgear replacement to select one any other type desired in stepless change gearshift (differential state) and the step change gearshift (non-differential state).Switch 44 can have or not have midway location.Do not have at switch 44 under the situation of midway location, additional switch can be set enable and forbid mutual change type switch 44.The function of this extra switch is corresponding to the midway location of mutual change type switch 44.Switch 44 can be by operating to select any other equipment of one in stepless change gearshift (differential state) and the step change gearshift (non-differential state) to replace, for example in response to the equipment of vehicle driver's sound, perhaps can be by the equipment of vehicle driver's foot control system.

Though the preferred embodiments of the present invention below only have been described for explanatory purposes, have it should be understood that the present invention can implement with various changes and modification that those skilled in the art can carry out.

Claims

1. control convenience that is used for Vehicular drive system, described Vehicular drive system is set to the output of driving engine is delivered to the drive wheel of vehicle, and described control convenience is characterised in that and comprises:

The switchable type transmission mechanism that comprises power splitting mechanism and Coupling device, described power splitting mechanism has first element that is fixed to described driving engine, be fixed to second element of first motor, and the three element that is fixed to second motor and power transfer member, described Coupling device can operate with described first to the three element any two be connected to each other also/or described second element is fixed to static component, described switchable type transmission mechanism can switch between stepless change gearshift and step change gearshift, can be used as the electric steplessly variable transmission operation at switchable type transmission mechanism described in the described stepless change gearshift, can be used as the step change transmission operation at switchable type transmission mechanism described in the described step change gearshift;

Switching control, described switching control is used for based on the predetermined state of described vehicle described Coupling device being switched between releasing orientation and engagement, so that described switchable type transmission mechanism is optionally placed one of described stepless change gearshift and described step change gearshift; With

Motor control assembly, described motor control assembly is used to control described first motor to produce reactive torque when described Coupling device unclamps, and/or when the engagement of described Coupling device, reduce described first element, described second element, and described three element between velocity contrast or the velocity contrast between described second element and the described static component

Wherein, based on by described switching control described switchable type speed-changing mechanism being switched to described stepless change gearshift from described step change gearshift, described motor control assembly is being worked in the course of action to increase the antagonistic force of described first motor when described Coupling device is released to unclamping of described Coupling device by described switching control.

2. control convenience according to claim 1, wherein said switching control can be operated to unclamp described Coupling device, with the described switchable type transmission mechanism stepless change gearshift that described first, second and three element relative to each other rotate that is placed in one, and can operate to mesh described Coupling device, described switchable type transmission mechanism is placed in one, and described first, second is connected to each other with three element or described second element keeps static described step change gearshift.

3. control convenience according to claim 1 and 2, wherein said switching control can be operated when described step change gearshift switches to described stepless change gearshift at described switchable type transmission mechanism, to begin the action of unclamping of described Coupling device after having produced described reactive torque under by the control of described first motor at described motor control assembly.

4. control convenience according to claim 1, the speed of described first motor of wherein said motor control assembly controlled reset is to reduce velocity contrast between described first, second and the three element or the velocity contrast between described second element and the described static component.

5. control convenience according to claim 1, wherein said motor control assembly is controlled the speed of described first motor, the described value of unclamping before the action beginning that makes that described velocity contrast between described first, second and the three element or the described velocity contrast between described second element and the described static component maintain described Coupling device is finished up to unclamping action by described switching control control described.

6. control convenience according to claim 1, wherein said switching control can be operated when described stepless change gearshift switches to described step change gearshift at described switchable type transmission mechanism, with the speed of described first motor by described motor control assembly control with after reducing the described velocity contrast or the described velocity contrast between described second element and the described static component between described first, second and the three element, begin the engagement action of described Coupling device.

7. control convenience according to claim 1, wherein said switching control can be operated when described stepless change gearshift switches to described step change gearshift at described switchable type transmission mechanism, with in by described motor control assembly the speed of described first motor being controlled, can carry out the engagement action of described Coupling device with the process that reduces described velocity contrast between described first, second and the three element or the described velocity contrast between described second element and the described static component.

8. control convenience according to claim 6, the engine output controller that also comprises the torque or the output that are used to control described driving engine, and wherein said engine output controller limits the described torque or the described output of described driving engine, surpass by the predetermined upper limit of the rated value of described first motor with described torque or the described output that prevents described driving engine, finish up to the described engagement action of the described Coupling device of controlling by described switching control.

9. control convenience according to claim 1, wherein judge the described predetermined state of described vehicle, and described switching control when being higher than described predetermined upper limit value, the actual value of the described moving velocity of described vehicle places described step change gearshift with described switchable type transmission mechanism based on the predetermined upper limit value of the moving velocity of described vehicle.

10. control convenience according to claim 1, wherein judge the described predetermined state of described vehicle, and described switching control when being higher than described predetermined upper limit value, the described drive-force-related value of described vehicle places described step change gearshift with described switchable type transmission mechanism based on the predetermined upper limit value of the drive-force-related value of described vehicle.

11. control convenience according to claim 1, wherein based on the actual value of the drive-force-related value of the actual value of the moving velocity of described vehicle and described vehicle, and according to run at high speed boundary line and high output that the handoff boundary line chart of being stored judges that the described predetermined state of described vehicle, described handoff boundary line chart comprise that parameter by the described moving velocity of described vehicle and described drive-force-related value form the defines boundary line of travelling.

12. control convenience according to claim 1, the described predetermined state of wherein said vehicle is a function deterioration Rule of judgment, when being used for that described switchable type transmission mechanism placed electrically any function deterioration of function unit of the described stepless change gearshift of setting up, described function deterioration Rule of judgment is just satisfied, and described switching control places described step change gearshift with described switchable type transmission mechanism when described function deterioration Rule of judgment satisfies.

13. control convenience according to claim 1, wherein said power splitting mechanism is a compound planet gear, and described first element planetary wheel carrier that is described compound planet gear, and described second element is the sun wheel of described compound planet gear, and the gear ring that described three element is described compound planet gear

And wherein said Coupling device comprises power-transfer clutch and/or drg, described power-transfer clutch can be operated so that any two elements in described planetary wheel carrier, described sun wheel and the described gear ring are connected to each other, and described drg can be operated so that described sun wheel is fixed to described static component.

14. control convenience according to claim 13, wherein said compound planet gear are the single-stage planetary gear tyves.

15. control convenience according to claim 1, wherein said power splitting mechanism is a differential gear equipment, and described Coupling device comprises power-transfer clutch and/or drg, described power-transfer clutch can be operated so that any two elements in described first, second and the three element are connected to each other, and described drg can be operated so that described second element is fixed to described static component.

16. control convenience according to claim 15, wherein said differential gear equipment is the finishing bevel gear cuter formula.

17. control convenience according to claim 13, wherein said switching control meshes described power-transfer clutch so that described power splitting mechanism can be 1 transmission operating as speed ratio, perhaps meshes described drg so that described power splitting mechanism can be as having the speedup transmission operating that is lower than 1 speed ratio.

18. control convenience according to claim 1, wherein said switchable type transmission mechanism comprises automatic transmission with hydraulic torque converter and has the speed ratio of being determined by the speed ratio of described automatic transmission with hydraulic torque converter, and described automatic transmission with hydraulic torque converter is arranged in that parallel series is connected to described power splitting mechanism between described power transfer member and the described drive wheel.

19. control convenience according to claim 18, wherein said switchable type transmission mechanism have the overall ratio that the described speed ratio by the speed ratio of described power splitting mechanism and described automatic transmission with hydraulic torque converter defines.

20. control convenience according to claim 18, wherein said automatic transmission with hydraulic torque converter are the step change automatic transmission with hydraulic torque converters according to the gear shift border line chart gear shift of being stored.

21. control convenience that is used for Vehicular drive system, described Vehicular drive system comprises the differential part, described differential partly can be used as automatically controlled differential operation of equipment, and comprise can operating being assigned to first motor and power transfer member and having the box of tricks of a plurality of rotating elements that described control convenience is characterised in that and comprises with output with driving engine:

Coupling device, described Coupling device is arranged in the described box of tricks and can operates so that described differential part is switched between differential state and lockup state, partly can be used as described automatically controlled differential operation of equipment and can carry out differential function at differential described in the described differential state, can not carry out described differential function in the part of differential described in the described lockup state;

Switching control, described switching control are used for based on the predetermined state of described vehicle described Coupling device being switched between releasing orientation and engagement, so that described differential part is optionally placed one of described differential state and described lockup state; With

Motor control assembly, described motor control assembly is used to control described first motor to produce reactive torque when described Coupling device unclamps, and/or reduce when the engagement of described Coupling device that described first motor is fixed to the upper among velocity contrast between described a plurality of rotating element or the described a plurality of rotating element rotating element and the velocity contrast between the static component

Wherein, based on by described switching control described differential part being switched to described differential state from described lockup state, described motor control assembly is being worked in the course of action to increase the antagonistic force of described first motor when described Coupling device is released to unclamping of described Coupling device by described switching control.

22. control convenience according to claim 21, described a plurality of rotating elements of wherein said box of tricks comprise first element that is fixed to described driving engine, are fixed to second element of described first motor and the three element that is fixed to described power transfer member, and described Coupling device can operate with connect described first to the three element any two elements, and/or described second element is fixed to described static component.

23. control convenience according to claim 22, wherein said switching control can be operated to unclamp described Coupling device described differential is partly placed described differential state, and can operate to mesh described Coupling device described differential is partly placed described lockup state, can relative to each other rotate in first, second and three element described in the described differential state, keep static as one unit rotation or described second element in first, second and three element described in the described lockup state.

24. according to claim 22 or 23 described control conveniences, wherein said switching control can be operated when described lockup state switches to described differential state in described differential part, to begin the action of unclamping of described Coupling device after producing described reactive torque under by the control of described first motor at described motor control assembly.

25. control convenience according to claim 21, the speed of described first motor of wherein said motor control assembly controlled reset is to reduce described velocity contrast between described first, second and the three element or the described velocity contrast between described second element and the described static component.

26. control convenience according to claim 21, wherein said switching control is controlled the speed of described first motor, the described value of unclamping before the action beginning that makes that described velocity contrast between described first, second and the three element or the described velocity contrast between described second element and the described static component maintain described Coupling device is finished up to unclamping action by described switching control control described.

27. control convenience according to claim 21, wherein said switching control can be operated when described differential state switches to described lockup state in described differential part, with the speed of described first motor by described motor control assembly control with after reducing the described velocity contrast or the described velocity contrast between described second element and the described static component between described first, second and the three element, begin the engagement action of described Coupling device.

28. control convenience according to claim 21, wherein said switching control can be operated when described differential state switches to described lockup state in described differential part, with in by described motor control assembly the speed of described first motor being controlled, can carry out the engagement action of described Coupling device with the process that reduces described velocity contrast between described first, second and the three element or the described velocity contrast between described second element and the described static component.

29. control convenience according to claim 27, the engine output controller that also comprises the torque or the output that are used to control described driving engine, and wherein said engine output controller limits the described torque or the output of described driving engine, surpass by the predetermined upper limit of the rated value of described first motor with described torque or the output that prevents described driving engine, finish up to the described engagement action of the described Coupling device of controlling by described switching control.

30. control convenience according to claim 21, wherein judge the described predetermined state of described vehicle, and described switching control when being higher than described predetermined upper limit value, the actual value of the described moving velocity of described vehicle partly places described lockup state with described differential based on the predetermined upper limit value of the moving velocity of described vehicle.

31. control convenience according to claim 21, wherein judge the described predetermined state of described vehicle, and described switching control when being higher than described predetermined upper limit value, the described drive-force-related value of described vehicle partly places described lockup state with described differential based on the predetermined upper limit value of the drive-force-related value of described vehicle.

32. control convenience according to claim 21, wherein based on the actual value of the drive-force-related value of the actual value of the moving velocity of described vehicle and described vehicle, and according to run at high speed boundary line and high output that the handoff boundary line chart of being stored judges that the described predetermined state of described vehicle, described handoff boundary line chart comprise that parameter by the described moving velocity of described vehicle and described drive-force-related value form the defines boundary line of travelling.

33. control convenience according to claim 21, the predetermined state of wherein said vehicle is a function deterioration Rule of judgment, when being used for making described differential part can be as any function deterioration of the function unit of automatically controlled differential operation of equipment the time, described function deterioration Rule of judgment is just satisfied, and described switching control partly places described lockup state with described differential when described function deterioration Rule of judgment satisfies.

34. control convenience according to claim 21, wherein said box of tricks is a compound planet gear, and described first element planetary wheel carrier that is described compound planet gear, and described second element is the sun wheel of described compound planet gear, and the gear ring that described three element is described compound planet gear

35. control convenience according to claim 34, wherein said compound planet gear are the single-stage planetary gear tyves.

36. control convenience according to claim 21, wherein said box of tricks is a differential gear equipment, and described Coupling device comprises power-transfer clutch and/or drg, described power-transfer clutch can be operated so that any two elements in described first, second and the three element are connected to each other, and described drg can be operated so that described second element is fixed to described static component.

37. control convenience according to claim 36, wherein said differential gear equipment is the finishing bevel gear cuter formula.

38. control convenience according to claim 34, wherein said switching control meshes described power-transfer clutch so that described box of tricks can be 1 transmission operating as speed ratio, perhaps meshes described drg so that described box of tricks can be as having the speedup transmission operating that is lower than 1 speed ratio.

39. control convenience according to claim 21, wherein said power transfer path comprises the automatic transmission with hydraulic torque converter part, and described Vehicular drive system has the overall ratio that the speed ratio by the speed ratio of described automatic transmission with hydraulic torque converter part and described differential part defines.

40. according to the described control convenience of claim 39, wherein said automatic transmission with hydraulic torque converter partly is the step change automatic transmission with hydraulic torque converter according to the gear shift border line chart gear shift of being stored.

41. control convenience according to claim 21, also comprising can be to second electrical motor of drive wheel transferring power.

42. control convenience according to claim 7, also comprise engine output controller, be used to control the torque or the output of described driving engine, and wherein, described engine output controller limits the described torque or the output of described driving engine, the described torque or the output that prevent described driving engine thus exceed by the predetermined upper limit of the rated value of described first electrical motor, finish until the engagement action that described Coupling device is controlled by described switching control.

43. control convenience according to claim 15, wherein, described switching control and described clutch engagement so that described power splitting mechanism as change-speed box work, or cooperates with described drg so that the conduct of described power splitting mechanism has the deceleration change-speed box work that is lower than 1 speed ratio with speed ratio of 1.

44. control convenience according to claim 28, also comprise engine output controller, be used to control the torque or the output of described driving engine, and wherein, described engine output controller limits the described torque or the output of described driving engine, the described torque or the output that prevent described driving engine thus exceed by the predetermined upper limit of the rated value of described first electrical motor, finish until the engagement action that described Coupling device is controlled by described switching control.

45. control convenience according to claim 36, wherein, described switching control and described clutch engagement so that described box of tricks as change-speed box work, or cooperates with described drg so that the conduct of described box of tricks has the deceleration change-speed box work that is lower than 1 speed ratio with speed ratio of 1.