US3606591A - Pump and driving motor assembly - Google Patents

Pump and driving motor assembly Download PDF

Info

Publication number
US3606591A
US3606591A US864580A US3606591DA US3606591A US 3606591 A US3606591 A US 3606591A US 864580 A US864580 A US 864580A US 3606591D A US3606591D A US 3606591DA US 3606591 A US3606591 A US 3606591A
Authority
US
United States
Prior art keywords
piston
pump
resetting
motor
cylinder
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US864580A
Inventor
Theodorus Gerhardus Potma
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Application granted granted Critical
Publication of US3606591A publication Critical patent/US3606591A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B71/00—Free-piston engines; Engines without rotary main shaft
    • F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
    • F02B71/045—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby with hydrostatic transmission
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01B—MACHINES OR ENGINES, IN GENERAL OR OF POSITIVE-DISPLACEMENT TYPE, e.g. STEAM ENGINES
    • F01B11/00—Reciprocating-piston machines or engines without rotary main shaft, e.g. of free-piston type
    • F01B11/02—Equalising or cushioning devices

Definitions

  • a pump is driven by an internal combustion motor of the so-called free piston type.
  • the motor piston is fixedly attached to the pump piston.
  • the return stroke of the motor piston is effected by the application of a pressure medium either to the pump piston or to a separate resetting piston fixedly attached to the motor piston.
  • the working frequency of the assembly is controlled by means of a regulating valve restricting the fiow of the pressure medium in a first portion .of the return stroke.
  • the invention relates to a pump and driving motor assembly, and in particular to an assembly of this kind wherein the return or compression stroke of the motor piston is effected by a pressure medium supplied from a pressure vessel to a resetting cylinder enclosing a resetting piston attached to the motor piston.
  • the required pumping capacity of such an assembly may vary within wide limits, for instance in dependence on the load of a hydraulic motor driven by the medium which is compressed by the pump.
  • FIG. 1 shows a first embodiment of the assembly according to the invention.
  • the working frequency is only variable within relatively narrow limits.
  • the pumping capacity must be variable within wide limits, it is necessary to vary, in addition to the frequency, the pumping capacity for each stroke.
  • the pumping capacity for each stroke may be regulated, for instance in fuel injection pumps, by recirculating a variable portion of the fuel displaced during each stroke to the supply vessel.
  • the efrficiency is considerably reduced by flow losses, and the control equipment is rather complicated.
  • the working frequency is controlled by means of a regulating valve restricting the passage of the pressure medium during a first portion of the return stroke.
  • the working frequency may be controlled by simple means within very wide limits, and even between zero and a maximum value, so that the pumping capacity may always be adapted to the requirements without any change of the capacity for each stroke.
  • FIG. 2 shows a second, simplified embodiment.
  • the driving motor comprises a motor cylinder 1, and a plunger-shaped motor piston 2, freely reciprocating within the cylinder 1.
  • a scavenging piston 3, which is integral with the motor piston 2, is displaceable in a scavenging cylinder 4.
  • the cylinder 4 is connected with a suction valve 4a for the scavenging air, and with a scavenging channel 5.
  • the outlet of the motor cylinder is indicated at 6.
  • the piston 3 is connected with a plunger 7 operating as a pump piston within the pump cylinder 8.
  • the medium to be displaced by the pump is sucked in from a tank 9 through a back pressure valve 10, and pumped into a pressure vessel or hydraulic storage vessel 11 through a back pressure valve 12.
  • Hydraulic devices such as a hydraulic motor (not shown) may be driven by the com pressed medium in the vessel 12.
  • the plunger 7 is further connected with a plunger 12, operating as a resetting piston in the resetting cylinder 14, and serving to return the pistons 2 and 3 to their original positions after each expansion stroke.
  • the pressure medium for operating the plunger 13 is taken from a pressure vessel or hydraulic storage vessel 15, which comprises a membrane 16.
  • the control device for regulating the working frequency of the assembly is inserted in the connecting channel 17 between the pressure vessel 15 and the end of the resetting cylinder (14, and is formed as an adjustable valve 18, which might be indicated as a frequency control valve.
  • the valve 18 would be fully opened during the expansion stroke of the piston 2 in which the piston 13 presses the medium from the cylinder 14 into the pressure vessel 15, then partially closed during the first portion of the compression stroke in order to control the duration of said first portion, and fully opened during the remaining portion of the compression stroke in order to impart the required kinetic energy to the piston 2.
  • the operation has been considerably simplified by providing a separate connecting channel 19 between the pressure vessel and the resetting cylinder, terminating in a gate 20 in the wall of the resetting cylinder which is closed off by the plunger 13 during the first portion of the compression stroke.
  • the frequency control valve 18 regulates the drive of the plunger 13 during the first portion of the compression stroke, before the gate 20 has been released.
  • the distance covered by the resetting piston during this first portion of the compression stroke has been indicated at e in FIG. 1. After release of the gate 20, the remaining portion of the compression stroke is automatically performed, independentlv of the Working frequency, with the full pressure of vessel 15. 1
  • an additional connecting channel 21 has been provided between the end of the resetting cylinder 14 and the pressure vessel 15; this channel contains a back pressure valve 21a.
  • FIG. 2 shows a simplified embodiment in which the cylinders 8 and 14 (as shown in FIG. 1) have been combined into a single auxiliary cylinder 24, enclosing a plunger 25 which serves both as a resetting piston and as a pump piston.
  • the connecting channels 17 and 19 and the regulating valve 18 are substantially the same as in FIG. 1. However, both channels are provided with a back pressure valve 26a, and 26, respectively, in order to prevent the medium from being returned to the vessel 22 during the expansion stroke.
  • the connecting channel 21, which contains the back pressure valve 21a, is now connected with a pressure vessel 23, so that the medium is pressed into this vessel during the expansion stroke.
  • the pressure medium in the vessel 23 is used to drive any desired hydraulic devices and is returned to the vessel 22 after use.
  • the pressure in the vessel 23 will be usually higher, and never lower than the pressure in the vessel 22.
  • the assembly according to the invention may be started and stopped in a very simple manner.
  • the engine may be stopped by cutting the fuel supply or by interrupting the connection with the resetting vessel. In both cases, the engine will come to a stand-still in an arbitrary position. The piston must then be manually returned to its initial position, after which the engine may be restarted by means of a separate starting device.
  • the starting procedure is extremely simple, because the engine always stops in the same final position after closure of the regulating valve 18, and may be restarted from this position by re-opening the regulating valve.
  • the assembly may be constructed in such mannor that the pressure medium is applied to the resetting piston with an adjustable delay after the end of the expansion stroke.
  • the regulating valve in a bypass-circuit connecting the spaces before and behind the resetting piston; in this case, the main connecting channel 19 is always open, but the pressure medium is only effective after the counterpressure on the resetting piston has been relieved by means of the regulating valve.
  • the piston surface must be smaller on the backside than on the frontside of the piston.
  • a pump and driving motor assembly comprising a motor cylinder, a motor piston adapted to perform a forward stroke in said motor cylinder in response to an internal combustion, a pump cylinder, a pump piston displaceable in said pump cylinder and fixedly attached to said motor piston, a pressure vessel, resetting means adapted to effect a return stroke of said motor piston in revessel, at least one" connecting channel between said pres sure vessel and said resetting means, a regulating valve in said connecting channel, said resetting means including a resetting cylinder, a resetting piston displaceable in said resetting cylinder and fixedly attached to said motor piston, and including a first and a second connecting channel between said pressure vessel and the pressure side of said resetting cylinder, the first connecting channel being attached to the end of said resetting cylinder and containing said regulating valve, said regulating valve being operative during a first portion of said return stroke to restrict the passage of said pressure medium in order to control the working frequency of said assembly, and the second connecting channel being operative only
  • said resetting means is formed by said pump piston, further comprising a first and a second connecting channel between said pressure vessel and the pressure side of said pump cylinder, of which the first connecting channel is attached to the end of said pump cylinder and contains said regulating valve, and the second connecting channel is only operative during a second portion of the return stroke, a first back pressure valve in said second connecting channel passing said pressure medium in the direction to said pump cylinder, a second pressure vessel, 21 third connecting channel between the pressure side of said pump cylinder and said second pressure vessel, and a second back pressure valve in said third connecting channel passing said pressure medium in the direction to said second pressure vessel.

Abstract

A PUMP IS DRIVEN BY AN INTERNAL COMBUSTION MOTOR OF THE SO-CALLED FREE PISTON TYPE. THE MOTOR PISTON IS FIXEDLY ATTACHED TO THE PUMP PISTON. THE RETURN STOKE OF THE MOTOR PISTON IS EFFECTED BY THE APPLICATION OF A PRESSURE MEDIUM EITHER TO THE PUMP PISTON OR TO A SEPARATE RESETTING PISTON FIXEDLY ATTACHED TO THE MOTOR PISTON. THE WORKING FREQUENCY OF THE ASSEMBLY IS CONTROLLED BY MEANS OF A REGULATING VALVE RESTRICTING THE FLOW OF THE PRESSURE MEDIUM IN A FIRST PORTION OF THE RETURN STROKE.

Description

Sept. 20, 1971 PQTMA 3,606,591
PUMP AND DRIVING MOTOR ASSEMBLY Filed Oct. 8, 1969 United States Patent O 814405 Int. Cl. F02b 71/00; F04b 31/00 U.S. Cl. 417364 5 Claims ABSTRACT OF THE DISCLOSURE A pump is driven by an internal combustion motor of the so-called free piston type. The motor piston is fixedly attached to the pump piston. The return stroke of the motor piston is effected by the application of a pressure medium either to the pump piston or to a separate resetting piston fixedly attached to the motor piston. The working frequency of the assembly is controlled by means of a regulating valve restricting the fiow of the pressure medium in a first portion .of the return stroke.
BACKGROUND OF THE INVENTION The invention relates to a pump and driving motor assembly, and in particular to an assembly of this kind wherein the return or compression stroke of the motor piston is effected by a pressure medium supplied from a pressure vessel to a resetting cylinder enclosing a resetting piston attached to the motor piston. The required pumping capacity of such an assembly may vary within wide limits, for instance in dependence on the load of a hydraulic motor driven by the medium which is compressed by the pump.
3,6fi6,59l Patented Sept. 20, 1971 cyclinder to its final pressure during the last portion of the return stroke.
BRIEF DESCRIPTION OF THE DRAWING FIG. 1 shows a first embodiment of the assembly according to the invention.
In the known free piston compressors, the working frequency is only variable within relatively narrow limits. Thus, if the pumping capacity must be variable within wide limits, it is necessary to vary, in addition to the frequency, the pumping capacity for each stroke.
The pumping capacity for each stroke may be regulated, for instance in fuel injection pumps, by recirculating a variable portion of the fuel displaced during each stroke to the supply vessel. However, in this case, the efrficiency is considerably reduced by flow losses, and the control equipment is rather complicated.
It is the main object of the invention to remove these disadvantages.
SUMMARY OF THE INVENTION According to the invention, the working frequency is controlled by means of a regulating valve restricting the passage of the pressure medium during a first portion of the return stroke.
In this manner, the working frequency may be controlled by simple means within very wide limits, and even between zero and a maximum value, so that the pumping capacity may always be adapted to the requirements without any change of the capacity for each stroke.
Further objects of the invention are to realise a maximum efficiency with a simple construction of the assembly and to avoid undesirable phenomena, such as cavitation.
An important factor in the operation of the invention is the time expiring between the end of the forward stroke, and the end of the first portion of the return stroke, during which the flow of the pressure medium is re stricted. I have found that it is possible to control the speed of the resetting piston during the first portion of the return stroke from zero to a maximum value, and that the remaining portion of the return stroke is still sufiicient to impart to the resetting piston the kinetic energy required to compress the combustible mixture in the motor FIG. 2 shows a second, simplified embodiment.
DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to FIG. 1, the driving motor comprises a motor cylinder 1, and a plunger-shaped motor piston 2, freely reciprocating within the cylinder 1. A scavenging piston 3, which is integral with the motor piston 2, is displaceable in a scavenging cylinder 4. The cylinder 4 is connected with a suction valve 4a for the scavenging air, and with a scavenging channel 5. The outlet of the motor cylinder is indicated at 6.
1 The piston 3 is connected with a plunger 7 operating as a pump piston within the pump cylinder 8. The medium to be displaced by the pump is sucked in from a tank 9 through a back pressure valve 10, and pumped into a pressure vessel or hydraulic storage vessel 11 through a back pressure valve 12. Hydraulic devices, such as a hydraulic motor (not shown) may be driven by the com pressed medium in the vessel 12.
The plunger 7 is further connected with a plunger 12, operating as a resetting piston in the resetting cylinder 14, and serving to return the pistons 2 and 3 to their original positions after each expansion stroke.
The pressure medium for operating the plunger 13 is taken from a pressure vessel or hydraulic storage vessel 15, which comprises a membrane 16.
The control device for regulating the working frequency of the assembly is inserted in the connecting channel 17 between the pressure vessel 15 and the end of the resetting cylinder (14, and is formed as an adjustable valve 18, which might be indicated as a frequency control valve. In principle, a procedure would be possible wherein the valve 18 would be fully opened during the expansion stroke of the piston 2 in which the piston 13 presses the medium from the cylinder 14 into the pressure vessel 15, then partially closed during the first portion of the compression stroke in order to control the duration of said first portion, and fully opened during the remaining portion of the compression stroke in order to impart the required kinetic energy to the piston 2. However, in the preferred embodiment as shown, the operation has been considerably simplified by providing a separate connecting channel 19 between the pressure vessel and the resetting cylinder, terminating in a gate 20 in the wall of the resetting cylinder which is closed off by the plunger 13 during the first portion of the compression stroke. Thus, the frequency control valve 18 regulates the drive of the plunger 13 during the first portion of the compression stroke, before the gate 20 has been released. The distance covered by the resetting piston during this first portion of the compression stroke has been indicated at e in FIG. 1. After release of the gate 20, the remaining portion of the compression stroke is automatically performed, independentlv of the Working frequency, with the full pressure of vessel 15. 1
In order to avoid the necessity of opening the regulating valve 18 during each expansion stroke in order that the medium may be returned to the vessel 15 without an excessive resistance, after the gate 20 has been closed by the plunger 13, an additional connecting channel 21 has been provided between the end of the resetting cylinder 14 and the pressure vessel 15; this channel contains a back pressure valve 21a.
Due to the fact that the number of strokes per time unit may be controlled in a simple maner, the amount of liquid displaced by the pump need never be larger than required, and the efiiciency will be substantially constant through the entire capacity range.
FIG. 2 shows a simplified embodiment in which the cylinders 8 and 14 (as shown in FIG. 1) have been combined into a single auxiliary cylinder 24, enclosing a plunger 25 which serves both as a resetting piston and as a pump piston.
The connecting channels 17 and 19 and the regulating valve 18 are substantially the same as in FIG. 1. However, both channels are provided with a back pressure valve 26a, and 26, respectively, in order to prevent the medium from being returned to the vessel 22 during the expansion stroke. The connecting channel 21, which contains the back pressure valve 21a, is now connected with a pressure vessel 23, so that the medium is pressed into this vessel during the expansion stroke. The pressure medium in the vessel 23 is used to drive any desired hydraulic devices and is returned to the vessel 22 after use. The pressure in the vessel 23 will be usually higher, and never lower than the pressure in the vessel 22.
The assembly according to the invention may be started and stopped in a very simple manner. In the known motor compressors, the engine may be stopped by cutting the fuel supply or by interrupting the connection with the resetting vessel. In both cases, the engine will come to a stand-still in an arbitrary position. The piston must then be manually returned to its initial position, after which the engine may be restarted by means of a separate starting device.
In the assembly according to the invention, the starting procedure is extremely simple, because the engine always stops in the same final position after closure of the regulating valve 18, and may be restarted from this position by re-opening the regulating valve.
The invention is not restricted to the embodiments described hereinbefore, which may be varied and modified in several ways within the scope of the invention. For instance, the assembly may be constructed in such mannor that the pressure medium is applied to the resetting piston with an adjustable delay after the end of the expansion stroke. It is also possible to arrange the regulating valve in a bypass-circuit connecting the spaces before and behind the resetting piston; in this case, the main connecting channel 19 is always open, but the pressure medium is only effective after the counterpressure on the resetting piston has been relieved by means of the regulating valve. For this purpose the piston surface must be smaller on the backside than on the frontside of the piston.
I claim:
1. A pump and driving motor assembly, comprising a motor cylinder, a motor piston adapted to perform a forward stroke in said motor cylinder in response to an internal combustion, a pump cylinder, a pump piston displaceable in said pump cylinder and fixedly attached to said motor piston, a pressure vessel, resetting means adapted to effect a return stroke of said motor piston in revessel, at least one" connecting channel between said pres sure vessel and said resetting means, a regulating valve in said connecting channel, said resetting means including a resetting cylinder, a resetting piston displaceable in said resetting cylinder and fixedly attached to said motor piston, and including a first and a second connecting channel between said pressure vessel and the pressure side of said resetting cylinder, the first connecting channel being attached to the end of said resetting cylinder and containing said regulating valve, said regulating valve being operative during a first portion of said return stroke to restrict the passage of said pressure medium in order to control the working frequency of said assembly, and the second connecting channel being operative only during a second portion of said return stroke.
2. An assembly as claimed in claim 1, wherein said resetting piston is shaped as a plunger, and wherein said second connecting channel terminates in a gate in the wall of said resetting cylinder which is closed off by said resetting piston during said first portion of the return stroke.
3. An assembly as claimed in claim 1, further comprising a third connecting channel between said pressure valve and the pressure side of said resetting cylinder attached to the end of said resetting cylinder, and a back pressure valve in said third connecting channel passing said pressure medium in the direction to said pressure vessel.
4. An assembly as claimed in claim 1, wherein said resetting means is formed by said pump piston, further comprising a first and a second connecting channel between said pressure vessel and the pressure side of said pump cylinder, of which the first connecting channel is attached to the end of said pump cylinder and contains said regulating valve, and the second connecting channel is only operative during a second portion of the return stroke, a first back pressure valve in said second connecting channel passing said pressure medium in the direction to said pump cylinder, a second pressure vessel, 21 third connecting channel between the pressure side of said pump cylinder and said second pressure vessel, and a second back pressure valve in said third connecting channel passing said pressure medium in the direction to said second pressure vessel.
5. An assembly as claimed in claim 4, further comprising a third back pressure valve in said first connecting channel passing said pressure medium in the direction to said pump cylinder.
References Cited UNITED STATES PATENTS 1,757,215 5/1930 Pescara 417364 2,434,280 1/1948 Morain 12346 3,077,188 2/1963 Herrmann 12346 ROBERT M. WALKER, Primary Examiner US. Cl. X.R.
US864580A 1968-10-08 1969-10-08 Pump and driving motor assembly Expired - Lifetime US3606591A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NL6814405.A NL160632C (en) 1968-10-08 1968-10-08 FREE PISTON PUMP INSTALLATION.

Publications (1)

Publication Number Publication Date
US3606591A true US3606591A (en) 1971-09-20

Family

ID=19804880

Family Applications (1)

Application Number Title Priority Date Filing Date
US864580A Expired - Lifetime US3606591A (en) 1968-10-08 1969-10-08 Pump and driving motor assembly

Country Status (3)

Country Link
US (1) US3606591A (en)
DE (1) DE1950769C2 (en)
NL (1) NL160632C (en)

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4307999A (en) * 1979-06-25 1981-12-29 Pneumo Corporation Free piston engine pump including variable energy rate and acceleration-deceleration controls
WO1982004290A1 (en) * 1981-05-26 1982-12-09 Garry E Clark Internal combustion driven pumping system and variable torque transmission
US4382748A (en) * 1980-11-03 1983-05-10 Pneumo Corporation Opposed piston type free piston engine pump unit
US4415313A (en) * 1980-08-05 1983-11-15 Regie Nationale Des Usines Renault Hydraulic generator with free-piston engine
US4461613A (en) * 1981-03-23 1984-07-24 Airmachines Hydraulic pump with variable-stroke piston and generator using said pump
US4479765A (en) * 1982-09-29 1984-10-30 General Motors Corporation Exhaust gas operated vacuum pump assembly
WO1989000245A1 (en) * 1985-02-26 1989-01-12 Anton Braun Bounce chambers for multi-cylinder linear engine compressors
US4992031A (en) * 1987-02-25 1991-02-12 Toiminimi Kone-Sampo Internal combustion engine driven multiple pump
WO1993010345A1 (en) * 1991-11-19 1993-05-27 Innas B.V. Free-piston engine having a fluid pressure unit
US5482445A (en) * 1991-11-19 1996-01-09 Innas Free Piston B.V. Free-piston engine having a slidable ring for moving the piston
US5556262A (en) * 1991-11-19 1996-09-17 Innas Free Piston B.V. Free-piston engine having a fluid energy unit
US5934245A (en) * 1997-11-19 1999-08-10 Caterpillar Inc. Two cycle engine having a mono-valve integrated with a fuel injector
US6105541A (en) * 1999-02-22 2000-08-22 Caterpillar, Inc. Free piston internal combustion engine with rotating piston
US6135069A (en) * 1998-09-11 2000-10-24 Caterpillar Inc. Method for operation of a free piston engine
US6152091A (en) * 1999-02-22 2000-11-28 Caterpillar Inc. Method of operating a free piston internal combustion engine with a variable pressure hydraulic fluid output
US6158401A (en) * 1999-02-24 2000-12-12 Caterpillar Inc. Method of operating a free piston internal combustion engine with pulse compression
WO2001038706A1 (en) * 1999-11-24 2001-05-31 Mannesmann Rexroth Ag Free-piston engine
US6244226B1 (en) * 1999-08-06 2001-06-12 Caterpillar Inc. Free piston internal combustion engine with rotating piston
NL1013996C2 (en) * 1999-12-30 2001-07-03 Innas Free Piston Bv Free piston unit for generating hydraulic energy.
US6269783B1 (en) * 1999-02-22 2001-08-07 Caterpillar Inc. Free piston internal combustion engine with pulse compression
US6293231B1 (en) 1999-09-29 2001-09-25 Ingo Valentin Free-piston internal combustion engine
US6863507B1 (en) 1999-11-24 2005-03-08 Mannesmann Rexroth Ag Generic free-piston engine with transformer valve assembly for reducing throttling losses
WO2012075441A1 (en) * 2010-12-02 2012-06-07 Raytheon Company Regenerative hydraulic pump

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0085800B1 (en) * 1982-02-10 1987-05-13 Pneumo Abex Corporation Opposed piston type free piston engine pump unit
NL1001939C2 (en) * 1995-04-10 1996-10-11 Potma Beheer B V T Device for generating fast movement for controlling free piston aggregate in particular
AU5163896A (en) * 1995-04-10 1996-10-30 T. Potma Beheer B.V. Operation and control of a free piston aggregate
NL1000479C2 (en) * 1995-06-01 1996-12-03 Potma Beheer B V T Device for generating fast movement for controlling free piston aggregate in particular
AT502851B1 (en) * 2002-02-21 2007-12-15 Wildner Hans Dkfm INTERVAL CONTROL FOR PISTON INCINERATION MACHINES

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE844227C (en) * 1948-11-05 1952-07-17 Participations Eau Soc Et Flying piston machine, in particular flying piston propellant gas generator
GB874009A (en) * 1957-03-11 1961-08-02 Soc Es Energie Sa Improvements in and relating to automatic control of free-piston gas-generators

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4307999A (en) * 1979-06-25 1981-12-29 Pneumo Corporation Free piston engine pump including variable energy rate and acceleration-deceleration controls
US4415313A (en) * 1980-08-05 1983-11-15 Regie Nationale Des Usines Renault Hydraulic generator with free-piston engine
US4382748A (en) * 1980-11-03 1983-05-10 Pneumo Corporation Opposed piston type free piston engine pump unit
US4461613A (en) * 1981-03-23 1984-07-24 Airmachines Hydraulic pump with variable-stroke piston and generator using said pump
WO1982004290A1 (en) * 1981-05-26 1982-12-09 Garry E Clark Internal combustion driven pumping system and variable torque transmission
US4459084A (en) * 1981-05-26 1984-07-10 Clark Garry E Internal combustion driven pumping system and variable torque transmission
US4479765A (en) * 1982-09-29 1984-10-30 General Motors Corporation Exhaust gas operated vacuum pump assembly
WO1989000245A1 (en) * 1985-02-26 1989-01-12 Anton Braun Bounce chambers for multi-cylinder linear engine compressors
US4992031A (en) * 1987-02-25 1991-02-12 Toiminimi Kone-Sampo Internal combustion engine driven multiple pump
WO1993010345A1 (en) * 1991-11-19 1993-05-27 Innas B.V. Free-piston engine having a fluid pressure unit
US5473893A (en) * 1991-11-19 1995-12-12 Innas Free Piston B.V. Free-piston engine having a fluid pressure unit
US5482445A (en) * 1991-11-19 1996-01-09 Innas Free Piston B.V. Free-piston engine having a slidable ring for moving the piston
US5556262A (en) * 1991-11-19 1996-09-17 Innas Free Piston B.V. Free-piston engine having a fluid energy unit
US5934245A (en) * 1997-11-19 1999-08-10 Caterpillar Inc. Two cycle engine having a mono-valve integrated with a fuel injector
US6135069A (en) * 1998-09-11 2000-10-24 Caterpillar Inc. Method for operation of a free piston engine
US6105541A (en) * 1999-02-22 2000-08-22 Caterpillar, Inc. Free piston internal combustion engine with rotating piston
US6269783B1 (en) * 1999-02-22 2001-08-07 Caterpillar Inc. Free piston internal combustion engine with pulse compression
US6152091A (en) * 1999-02-22 2000-11-28 Caterpillar Inc. Method of operating a free piston internal combustion engine with a variable pressure hydraulic fluid output
US6463895B2 (en) * 1999-02-22 2002-10-15 Caterpillar Inc Free piston internal combustion engine with pulse compression
US6158401A (en) * 1999-02-24 2000-12-12 Caterpillar Inc. Method of operating a free piston internal combustion engine with pulse compression
JP2003506617A (en) * 1999-08-06 2003-02-18 キャタピラー インコーポレイテッド Free piston internal combustion engine with rotating piston
US6244226B1 (en) * 1999-08-06 2001-06-12 Caterpillar Inc. Free piston internal combustion engine with rotating piston
US6293231B1 (en) 1999-09-29 2001-09-25 Ingo Valentin Free-piston internal combustion engine
US6484674B2 (en) 1999-09-29 2002-11-26 Ingo Valentin Free-piston internal combustion engine
WO2001038706A1 (en) * 1999-11-24 2001-05-31 Mannesmann Rexroth Ag Free-piston engine
US6863507B1 (en) 1999-11-24 2005-03-08 Mannesmann Rexroth Ag Generic free-piston engine with transformer valve assembly for reducing throttling losses
NL1013996C2 (en) * 1999-12-30 2001-07-03 Innas Free Piston Bv Free piston unit for generating hydraulic energy.
US20030051682A1 (en) * 1999-12-30 2003-03-20 Achten Peter A.J. Free-piston unit for generating hydraulic energy
US6823671B2 (en) * 1999-12-30 2004-11-30 Innas Free Piston B.V. Free-piston unit for generating hydraulic energy
WO2012075441A1 (en) * 2010-12-02 2012-06-07 Raytheon Company Regenerative hydraulic pump

Also Published As

Publication number Publication date
DE1950769C2 (en) 1982-07-15
DE1950769A1 (en) 1970-06-25
NL160632B (en) 1979-06-15
NL160632C (en) 1979-11-15
NL6814405A (en) 1970-04-10

Similar Documents

Publication Publication Date Title
US3606591A (en) Pump and driving motor assembly
US4551076A (en) Fluid driven pump with one-way valve in fluid inlet
US3005412A (en) Automatic pressure compensator for reciprocating pumps
ES398006A1 (en) Pump and method of driving same
US2966776A (en) Pneumatic power transmission system
GB1164003A (en) Apparatus for providing High-Pressure Liquid
KR960701301A (en) Cyclic Hydraulic Pump
US3065703A (en) Free piston engine pump
US2780170A (en) Supercharging system for fluid pumps
ATE139824T1 (en) THICK MATERIAL PUMP
GB1171659A (en) Hydraulic starting system and valves therefor
US3496879A (en) Fluid pump with plural accumulators
US2661592A (en) Hydraulic drive internal-combustion engine
US2027877A (en) Motor compressor
AU762852B2 (en) Free piston internal combustion engine with pulse compression
US1261061A (en) Pump mechanism.
US3447313A (en) Supercharged two stroke cycle internal combustion piston engine
GB959726A (en) Hydraulic system for starting internal combustion engines
US3031972A (en) Free piston engine driven pump assembly
GB1576230A (en) Meshing-screw compressor
US4344742A (en) Engine apparatus
US3011450A (en) Pump
US1976040A (en) Injector
GB1374538A (en) Piston pump
US2298106A (en) Hydraulic driven air pump