US20090155106A1 - Extended compressor operation for auxiliary air supply - Google Patents
Extended compressor operation for auxiliary air supply Download PDFInfo
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- US20090155106A1 US20090155106A1 US11/954,699 US95469907A US2009155106A1 US 20090155106 A1 US20090155106 A1 US 20090155106A1 US 95469907 A US95469907 A US 95469907A US 2009155106 A1 US2009155106 A1 US 2009155106A1
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- United States
- Prior art keywords
- air
- compressor
- air circuit
- primary
- machine
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B41/00—Pumping installations or systems specially adapted for elastic fluids
- F04B41/06—Combinations of two or more pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B5/00—Machines or pumps with differential-surface pistons
- F04B5/02—Machines or pumps with differential-surface pistons with double-acting pistons
Abstract
A machine air supply system includes a primary air circuit and a secondary air circuit and a single compressor for supplying compressed air to both circuits. In an embodiment, the compressor is a reciprocating piston compressor having a primary air circuit including a compression chamber of the compressor and a secondary air circuit including a crankcase chamber of the compressor. In an aspect, the compressor may be a multi-cylinder compressor.
Description
- This patent disclosure relates generally to vehicle air systems and, more particularly to a compressor for supplying a primary vehicle air supply via a pump chamber and for supplying a secondary vehicle air supply via a secondary chamber associated with the pump chamber.
- Large on-highway machines typically require pressurized air to operate properly. For example, the braking systems for such machines are typically air driven, using a source of pressurized air to drive a piston in a regulated maimer, providing the necessary force for braking the machine. The air driven systems, e.g., pistons, are often mechanically sensitive high tolerance devices, requiring that the pressurized air be essentially free of debris and contaminants. For this reason, the air delivery system for the machine may include an oil filter, desiccant filter, e.g., dryer, and/or other air cleaning device between the compressor and the air driven system.
- Because the drag imposed by the compressor on the machine engine is related to the compressor size, it is typical to use a small compressor without significant additional capacity beyond that required by the braking system. Moreover, because of the packing requirements in and around the engine of such machines, a larger compressor is not suitable in most such machines.
- However, there are increasingly other auxiliary machine systems, especially related to engine and emissions operations, that are air driven or that utilize pressurized air to perform a function. Because the main compressor of the machine is operating near capacity, it is not practical in most cases to bleed air from the main compressor to supply the auxiliary functions. Moreover, these functions often require clean air, and the compressor filter system may be located on the chassis, remote from the engine compartment.
- There have been attempts to solve the problem of compressor capacity by using separate pumps. For example, U.S. Pat. No. 7,226,273 entitled “Method of Generating Compressed Air and Compressor Arrangement for Implementing the Method” describes a two-stage system for generating compressed air of sufficient flow rate and pressure for commercial vehicles. The system uses a compressor unit driven by an internal-combustion engine to generate low-pressure compressed air. The low-pressure compressed air is then used to generate higher-pressure compressed air via a separate auxiliary compressor unit. The compressor and auxiliary compressor unit are triggered based on the instantaneous pressure demand of the machine systems. However, the foregoing system is complex and cumbersome to operate, and requires an additional auxiliary compressor, thus complicating installation and maintenance as well.
- This background section is presented as a convenience to the reader who may not be of skill in this art. However, it will be appreciated that this section is too brief to attempt to accurately and completely survey the prior art. The preceding background description is a simplified narrative and is not intended to replace the reference being discussed. Therefore, interested readers should refer directly to the U.S. Pat. No. 7,226,273 patent instead of relying upon the foregoing simplified narrative. Moreover, the resolution of deficiencies, noted or otherwise, of the prior art is not a critical or essential limitation of the disclosed principles.
- In one aspect, the disclosure relates to a machine having a plurality of air-operated systems including at least one primary system and at least one secondary system. In this aspect, the machine comprises at least one air tank for containing a supply of compressed air for providing compressed air to the primary system and the secondary system. The machine includes a compressor for supplying compressed air to the air tank. The compressor is a reciprocating piston compressor having a primary air circuit including a compression chamber of the compressor and a secondary air circuit including a crankcase chamber of the compressor.
- In a further aspect, the disclosure relates to a machine air supply system for providing compressed air to two or more air-operated features of a machine. In this aspect, the air supply system includes a primary air circuit for providing compressed air to one of the air-operated features of the machine and a secondary air circuit for providing compressed air to another of the air-operated features of the machine. In this aspect, the primary air circuit and the secondary air circuit share a single compressor while operating at different air pressures.
- In another aspect, the disclosure relates to a method for managing an air supply in a machine having a high-pressure air circuit and a secondary air circuit, the secondary air circuit having a lower pressure than the high-pressure air circuit. In this aspect, the high-pressure air circuit and a secondary air circuit are driven by a single compressor. The method comprises sensing a pressure in the high-pressure air circuit to establish a first sensed pressure and holding open a first intake valve on the compressor if the sensed pressure exceeds a first deactivation threshold, and releasing the first intake valve if the sensed pressure is less than a first activation threshold. The method also comprises sensing a pressure in the secondary air circuit to establish a second sensed pressure, and holding open a second intake valve on the compressor if the sensed pressure exceeds a second deactivation threshold, and releasing the second intake valve if the sensed pressure is less than a second activation threshold.
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FIG. 1 is schematic view of a machine and associated air supply system according to an aspect of the disclosed principles; -
FIG. 2 is a partial cross-sectional side view of a single-piston compressor according to an aspect of the disclosed principles; -
FIG. 3 is a partial cross-sectional side view of a multi-piston compressor according to a further aspect of the disclosed principles; and -
FIG. 4 is a flow chart illustrating a process of controlling primary and secondary air circuits in a machine such as illustrated in connection withFIG. 1 . - This disclosure relates to a machine air supply system having a primary air circuit and a secondary air circuit with a single compressor for supplying compressed air to both circuits. In an embodiment, the compressor is a reciprocating piston compressor having a primary air circuit including a compression chamber of the compressor and a secondary air circuit including a crankcase chamber of the compressor. In a further embodiment, the compressor may be a multi-cylinder compressor.
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FIG. 1 is a schematic view of a power and air delivery system for a machine 1 such as an on-highway machine. The air delivery system comprises an engine 2 or other power source of the machine 1. Generally, the engine 2 supplies power through adrive train 4 for movement of the machine 1. Acompressor 3 is linked to the engine 2 via a gear drive, pulley, or other transmission means so that as the engine 2 shaft rotates, thecompressor 3 is driven at a speed that is generally at or proportional to the speed of the engine 2. - The
compressor 3 supplies compressed air at anoutlet 6. The compressed air is supplied to anair tank 7 via a filter system 8. The filter system 8 typically comprises one or more filters, typically including filters to remove water, debris, and oil from the compressed air. These contaminants may arise from the operation of thecompressor 3 itself or from contaminants in the air compressed by thecompressor 3. - An air pressure in the
tank 7 is maintained within a desired range, such as 110-150 PSI in the United States and 250-280 PSI is Europe. The air pressure in thetank 7 is affected by the supply of air to thetank 7 as well as the release of air from thetank 7 viatank outlet 9. In particular, air from thetank 7 is released fromtank outlet 9 to various machine 1 systems such as anair brake system 10. It will be appreciated that the disclosed principles apply in various machine systems regardless of whether such machines include an air brake system or instead include some other type of air-driven system. - A
regulator module 11 senses the air pressure in thetank 7 via asensor 12 and modifies the operation of thecompressor 3 in response to the sensed pressure. In particular, if the sensed pressure falls below a specified range, theregulator module 11 causes thecompressor 3 to supply compressed air to thetank 7. If, on the other hand the sensed pressure exceeds the specified range, then theregulator module 11 causes thecompressor 3 to cease supplying compressed air. It will be appreciated that theregulator module 11 may apply hysteresis to the control of thecompressor 3 to avoid rapid on-off cycling when the air from thetank 7 is being released fromtank outlet 9 to theair brake system 10 of other machine 1 system. - As noted above, the drag imposed by the
compressor 3 on the engine 2 is related to the size of thecompressor 3. Moreover, the space constraints in and around the engine 2 limit the area available for thecompressor 3. Thus, it is generally desirable to use thesmallest compressor 3 able to supply the requirements of thebraking system 10 without significant additional capacity. - However, there are other
auxiliary air systems 13, especially related to engine and emissions operations, which are air driven or which utilize pressurized air to perform a function. For example, pressurized air may be used to supply a regeneration purge system, a selective catalytic reduction (SCR) air-assisted urea injector, a crankcase purge system, etc. Because thecompressor 3 of the machine 1 is operating near capacity, it is not practical in most cases to bleed air from thecompressor 3 to supply theauxiliary air systems 13. Moreover, theseauxiliary air systems 13 often require clean air, and the compressor filter system 8 may be located on the machine 1 chassis, remote from the engine 2. - Although the foregoing discussion illustrates a
tank 14 and filter 15 associated with the secondary circuit, it is not critical that the secondary circuit have such components, nor are they required for the primary circuit in every implementation. Moreover, although the above example describes each circuit as being regulatable at thecompressor 3, this need not be true of one or both circuits. For example, for simplicity or other reasons, it may be desirable in a particular implementation to control circuit pressure and/or flow in the secondary and/or primary air circuit via one or more throttling orifices or pressure relief valves. - In an embodiment, the
compressor 3 is modified to supply additional air via a secondary pump circuit andsecondary tank 14 and filter 15 without increasing the size of thecompressor 3, without bleeding air from the primary circuit ortank 7 used to supply theair brake system 10, and without requiring an additional pump or compressor. In particular, in this embodiment, thecompressor 3 is piston-operated, with apiston 20 slidably fitting within acylinder 21 so that thecylinder 21 andpiston 20 form acompression chamber 22 as shown inFIG. 2 . - A one-
way intake valve 23 allows air into thecompression chamber 22 on an intake stroke but does not allow air egress during a compression stroke. A one-way outlet valve 24 allows air egress from thecompression chamber 22 during the compression stroke, but does not allow air entry during the intake stroke. In this manner, as thepiston 20 reciprocates within thecylinder 21, air is drawn into thecompression chamber 22 through theintake valve 23 and is forced out of thecompression chamber 22 through theoutlet valve 24, thus supplying compressed air, i.e. to thetank 7. Theintake valve 23 and theoutlet valve 24 may be of any suitable types and configuration. However, in an embodiment, theintake valve 23 and theoutlet valve 24 are reed valves. In another embodiment, theintake valve 23 and theoutlet valve 24 are disk valves or ball valves. It will be appreciated that thecompressor 3 may be an oil-less compressor in order to avoid oil contamination of the air provided by the secondary air circuit. - The
piston 20 is reciprocally driven by a connectingrod 25 driven by acrankshaft 26. Thecrankshaft 26 is driven from the engine 2 via a gearing or pulley system, not shown. Thecrankshaft 26 rotates within achamber 28 formed by thecrankcase 27. Thecrankshaft 26 is rotatably supported within thecrankcase 27 by one ormore bearings 29 or bushings. - To provide an auxiliary flow path for supplying compressed air, the
crankcase 27 is formed with asecondary intake 30 controlled by asecondary intake valve 32 and asecondary outlet 31 controlled by asecondary outlet valve 33. The crankcase is substantially sealed against the ambient atmosphere via arotary seal 34, e.g., a U-cup or other suitable seal as will be appreciated by those of skill in the art. - In operation, as the
piston 20 rises in thechamber 22, the volume of thecrankcase chamber 28 increases, causing a drop in pressure therein. This causes an influx of air into thecrankcase chamber 28 through thesecondary intake 30 via thesecondary intake valve 32. Once thepiston 20 passes top dead center and begins to descend, the volume of thecrankcase chamber 28 decreases, causing a rise in pressure therein. This causes an egress of air out of thecrankcase chamber 28 through thesecondary outlet 31 via thesecondary outlet valve 33. - In this manner, as the
piston 20 reciprocates within thecylinder 21, a primary air circuit including theintake valve 23,outlet valve 24, andcompression chamber 22 provides a first source of compressed air. At the same time, a secondary air circuit including thesecondary intake 30,secondary intake valve 32 and asecondary outlet 31 controlled by asecondary outlet valve 33 provides a first source of compressed air. Because the compression ratio (the ratio of largest to smallest volume) of thecompression chamber 22 is greater than that of thecrankcase chamber 28, the primary air circuit provides air at a higher pressure than the secondary air circuit. Thus, while the first air circuit is a suitable source of high-pressure air for anair brake system 10 or the like, the secondary air circuit is suitable for auxiliary functions that operate on a lower pressure supply, e.g., a regeneration purge system, an SCR air-assisted urea injector, a crankcase purge system, etc. - In an embodiment, a
multi-cylinder compressor 40 is adapted as shown inFIG. 3 to provide a secondary air circuit. Typically, a multi-cylinder compressor uses cylinders that rise and fall at different times for purposes of reducing vibration, although it will be appreciated that the disclosed adaptation may be used with multi-cylinder compressors regardless of the number of cylinders and the manner in which the cylinders are coordinated. - A first
primary intake valve 56 allows air into thefirst compression chamber 57 on an intake stroke and a firstprimary outlet valve 58 allows air egress from thefirst compression chamber 57 during the compression stroke. Similarly, a secondprimary intake valve 59 allows air into thesecond compression chamber 60 on an intake stroke and a secondprimary outlet valve 61 allows air egress from thesecond compression chamber 60 during the compression stroke. In this manner, a primary air circuit is provided. - In an embodiment however, the crankcase pressure of the
compressor 40 is used to provide a secondary air circuit. To ensure that the pressure rise and fall potentially caused by one of thefirst piston 41 andsecond piston 42 is not negated by an opposite movement of the other of thefirst piston 41 andsecond piston 42, the pistons do not share a common crankcase chamber. Rather, thefirst piston 41 has associated with it afirst crankcase chamber 43 and thesecond piston 42 has associated with it asecond crankcase chamber 44. Thefirst crankcase chamber 43 and thesecond crankcase chamber 44 are sealed against one another via one or more rotary seals 45. Similarly, thesecond crankcase chamber 44 is sealed against the ambient atmosphere where thecrankshaft 46 exits by anotherrotary seal 47. - To provide the secondary air circuit, the
first crankcase chamber 43 has associated therewith a firstsecondary intake 48 controlled by a firstsecondary intake valve 49 and a firstsecondary outlet 50 controlled by a firstsecondary outlet valve 51. Similarly, thesecond crankcase chamber 44 has associated therewith a secondsecondary intake 52 controlled by a secondsecondary intake valve 53 and a secondsecondary outlet 54 controlled by a secondsecondary outlet valve 55. It will be appreciated that thecompressor 40 may be an oil-less compressor in order to avoid oil contamination of the air provided by the secondary air circuit. Thecompressor 40 may include a sealedshaft 62 passing between thecrankcase chambers - A compressor such as the
compressor 3 or thecompressor 40 imposes a drag on the machine engine 2 when operating. In order to impose this drag only when the compressor is providing useful work, the compressor may be disengaged when not needed. Because disengagement may require the mechanical complexities required by disengagement of gears or pulleys, in an embodiment the compressor is allowed to turn when inactive, but the associated drag is reduced by deactivation of one or both of the primary and secondary air circuits. - Referring to the
compressor 3 ofFIG. 2 , with the understanding that the same principles apply to thecompressor 40 ofFIG. 3 , the primary air circuit may be deactivated by holding open the one-way intake valve 23. Thus, when thepiston 20 causes the volume of thecompression chamber 22 to rise and fall, air is allowed both into and out of the one-way intake valve 23. In this manner, the primary air circuit is deactivated and does not supply compressed air. Similarly, the secondary air circuit may be deactivated by holding open thesecondary intake valve 32. Thus, when thepiston 20 causes the volume of thecrankcase chamber 28 to rise and fall, air is allowed both into and out of thesecondary intake valve 32. In this manner, the secondary air circuit is deactivated and does not supply compressed air. - The flow chart of
FIG. 4 illustrates a process 70 for controlling a compressor to provide compressed air from a primary and secondary air circuit of a compressor to machine systems as needed. It will be assumed in this example that the compressor is as illustrated inFIG. 2 , although it will be appreciated that the compressor may instead be a multi-cylinder compressor as shown inFIG. 3 . At stage 71 of the process 70 the machine 1 is started, i.e., the engine 2 is started, which also starts the rotation of thecompressor 3. At this point, the air tanks of the machine 1 are not pressurized and the primary and secondary air circuits are not deactivated. At stage 72, theregulator module 11 checks the air pressure in theprimary tank 7 and if the air pressure in theprimary tank 7 falls below a predetermined activation threshold, e.g., 110 PSI then theregulator module 11 ensures that the primary air circuit is active, i.e., that none of the primary circuit valves are held open at stage 73. At stage 74, theregulator module 11 checks the air pressure in theprimary tank 7 and if the air pressure in theprimary tank 7 is greater than a predetermined deactivation threshold, e.g., 140 PSI, then theregulator module 11 deactivates the primary air circuit at stage 75, e.g., by holding an intake valve open. In an embodiment, the activation threshold is different from and greater than the deactivation threshold. In this manner, theregulator module 11 will not cause rapid on/off cycling of the primary air circuit when the pressure is near a threshold. As the machine 1 operates and air is released from thetank 7, e.g., to operate theair brake system 10, theregulator module 11 continues to loop through stages 72-75 to maintain the air pressure in thetank 7 at an appropriate level. - Similarly, at stages 76-79, the
regulator module 11 maintains the pressure in thesecondary tank 14 at an appropriate level via the secondary air circuit of thecompressor 3. Although the stages of regulation are similar, it should be noted that the secondary air circuit will typically operate at a lower pressure and will supply air to devices different from those supplied by the primary air circuit. Therefore, the secondary activation threshold may be different from the activation threshold of the primary circuit and the secondary deactivation threshold may be different from the deactivation threshold of the primary circuit. In an embodiment, the secondary activation threshold is lower than the activation threshold of the primary circuit and the secondary deactivation threshold is lower than the deactivation threshold of the primary circuit. In a further embodiment, the secondary activation threshold is lower than the secondary deactivation threshold. When the machine 1 is turned off, theregulator module 11 may causetank 7 andtank 14 to be vented or may allow thetanks - The present disclosure is applicable to machines that utilize compressed air from a single compressor for multiple machine functions. A primary air circuit including the compressor's compression chamber is used to supply high-pressure air to machine systems that require high-pressure air. Examples of such systems include air brake systems and other critical or non-critical systems.
- In addition, a secondary air circuit that includes the compressor crankcase chamber provides a secondary supply of compressed air to auxiliary machine systems. For example, pressurized air may be used to supply a regeneration purge system, a selective catalytic reduction air-assisted urea injector, a crankcase purge system, etc. Because machine compressors typically operate near capacity and because the space available to place an additional compressor is limited, the compressor according to the disclosed principles supplies the secondary supply of compressed air without substantially increasing the size of the compressor, without bleeding air from the primary circuit, and without requiring an additional pump or compressor.
- It will be appreciated that the foregoing description provides examples of the disclosed system and technique. However, it is contemplated that other implementations of the disclosure may differ in detail from the foregoing examples. All references to the disclosure or examples thereof are intended to reference the particular example being discussed at that point and are not intended to imply any limitation as to the scope of the disclosure more generally. All language of distinction and disparagement with respect to certain features is intended to indicate a lack of preference for those features, but not to exclude such from the scope of the disclosure entirely unless otherwise indicated.
- Recitation of ranges of values herein are merely intended to serve as a shorthand method of referring individually to each separate value falling within the range, unless otherwise indicated herein, and each separate value is incorporated into the specification as if it were individually recited herein. All methods described herein can be performed in any suitable order unless otherwise indicated herein or otherwise clearly contradicted by context.
- Accordingly, this disclosure includes all modifications and equivalents of the subject matter recited in the claims appended hereto as permitted by applicable law. Moreover, any combination of the above-described elements in all possible variations thereof is encompassed by the disclosure unless otherwise indicated herein or otherwise clearly contradicted by context.
Claims (20)
1. A machine having a plurality of air-operated systems including at least one primary system and at least one secondary system, the machine comprising:
at least one air tank for containing a supply of compressed air for providing compressed air to the at least one primary system; and
a compressor for supplying compressed air to the at least one air tank, the compressor being a reciprocating piston compressor having a primary air circuit including a compression chamber of the compressor and a secondary air circuit including a crankcase chamber of the compressor.
2. The machine according to claim 1 , further including a secondary air tank, separate from the primary tank, for providing compressed air to the at least one secondary system.
3. The machine according to claim 2 , wherein the primary tank operates at a higher air pressure than the secondary tank.
4. The machine according to claim 1 , wherein the compressor is an oil-less compressor.
5. The machine according to claim 1 , wherein the compressor includes multiple reciprocating pistons associated with respective separate compression chambers and respective separate crankcase chambers, wherein the primary air circuit includes the respective separate compression chambers and the secondary air circuit includes the respective separate crankcase chambers.
6. The machine according to claim 5 , further including at least one sealed shaft passing between the respective separate crankcase chambers.
7. The machine according to claim 1 , further including at least one filter in the primary air circuit and at least one filter in the secondary air circuit.
8. The machine according to claim 1 , wherein the at least one primary system includes an air brake system and the at least one secondary system includes one of a regeneration purge system, a selective catalytic reduction air-assisted urea injector, and a crankcase purge system.
9. The machine according to claim 1 , further including a regulator module for controlling the primary air circuit and the secondary air circuit separately by controlling the operation of the compressor.
10. The machine according to claim 9 , wherein the primary air circuit and the secondary air circuit each include an air intake valve, wherein the regulator module separately controls the primary air circuit and the secondary air circuit by independently controlling the air intake valves.
11. A machine air supply system for providing compressed air to two or more air-operated features of a machine, the air supply system including:
a primary air circuit for providing compressed air to one of the two or more air-operated features of the machine; and
a secondary air circuit for providing compressed air to another of the two or more air-operated features of the machine, wherein the primary air circuit and the secondary air circuit share a single compressor while operating at different air pressures.
12. The machine air supply system according to claim 11 , wherein the primary air circuit includes a primary tank and the secondary air circuit includes a secondary tank separate from the primary tank.
13. The machine air supply system according to claim 12 , wherein the primary tank operates at a higher air pressure than the secondary tank.
14. The machine air supply system according to claim 11 , wherein the single compressor includes multiple reciprocating pistons associated with respective separate compression chambers and respective separate crankcase chambers, wherein the primary air circuit includes the respective separate compression chambers and the secondary air circuit includes the respective separate crankcase chambers.
15. The machine air supply system according to claim 11 , further including at least one filter in the primary air circuit and at least one filter in the secondary air circuit.
16. The machine air supply system according to claim 11 , wherein the two or more air-operated features of the machine include an air brake system and at least one of a regeneration purge system, a selective catalytic reduction air-assisted urea injector, and a crankcase purge system.
17. The machine air supply system according to claim 11 , further including a regulator module for controlling the primary air circuit and the secondary air circuit separately by controlling the operation of the single compressor.
18. The machine air supply system according to claim 17 , wherein the primary air circuit and the secondary air circuit each include an air intake valve, wherein the regulator module separately controls the primary air circuit and the secondary air circuit by controlling the air intake valve of the primary air circuit and the secondary air circuit.
19. A method for managing an air supply in a machine having a high-pressure air circuit and a secondary air circuit having a lower pressure than the high-pressure air circuit, the high-pressure air circuit and the secondary air circuit being driven by a single compressor, the method comprising:
sensing a pressure in the high-pressure air circuit to establish a first sensed pressure;
holding open a first intake valve on the compressor if the sensed pressure exceeds a first deactivation threshold, and releasing the first intake valve if the sensed pressure is less than a first activation threshold;
sensing a pressure in the secondary air circuit to establish a second sensed pressure; and
holding open a second intake valve on the compressor if the sensed pressure exceeds a second deactivation threshold, and releasing the second intake valve if the sensed pressure is less than a second activation threshold.
20. The method according to claim 19 , wherein the compressor includes a reciprocating piston, and wherein the high-pressure air circuit includes a compression chamber associated with the reciprocating piston and the secondary air circuit includes a crankcase chamber associated with the reciprocating piston.
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US11/954,699 US20090155106A1 (en) | 2007-12-12 | 2007-12-12 | Extended compressor operation for auxiliary air supply |
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US11/954,699 US20090155106A1 (en) | 2007-12-12 | 2007-12-12 | Extended compressor operation for auxiliary air supply |
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Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20090016908A1 (en) * | 2005-08-26 | 2009-01-15 | Michael Hartl | Multi-cylinder, dry-running piston compressor a cooling air flow |
US20140020595A1 (en) * | 2011-03-31 | 2014-01-23 | Nippon Steel & Sumitomo Metal Corporation | Method for control of vehicle body tilting of railway vehicle |
JP2016128673A (en) * | 2015-01-09 | 2016-07-14 | 株式会社日立産機システム | Reciprocation compressor |
CN114517783A (en) * | 2020-11-18 | 2022-05-20 | 纳博特斯克有限公司 | Air compressor and air suction device |
Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3554175A (en) * | 1969-12-08 | 1971-01-12 | Chrysler Corp | Evaporative emission control system |
US3613646A (en) * | 1969-09-10 | 1971-10-19 | Souichi Hisada | Secondary air injection system for an internal combustion engine |
US4097202A (en) * | 1976-06-21 | 1978-06-27 | Billy Frank Price | Auxiliary compressor assembly |
US4486157A (en) * | 1981-12-16 | 1984-12-04 | Nissan Motor Company, Limited | Reciprocating compressor |
US5107960A (en) * | 1990-06-28 | 1992-04-28 | Rix Industries, Inc. | Crankcase oil-barrier system |
US5762480A (en) * | 1996-04-16 | 1998-06-09 | Adahan; Carmeli | Reciprocating machine |
US5954690A (en) * | 1996-04-14 | 1999-09-21 | Medela Holding Ag | Alternating suction breastpump assembly and method |
US6056516A (en) * | 1997-10-11 | 2000-05-02 | Wabco Standard Gmbh | Compressor installation having a control valve arrangement for independently switching compression chambers between delivery partial delivery and idle operation |
US20020155007A1 (en) * | 2001-04-19 | 2002-10-24 | Mietto Virgilio | Intake regulator for compressed air in a reservoir |
US6561159B1 (en) * | 2000-12-05 | 2003-05-13 | Louis W Mower | Crankcase inducted self-supercharging four cycle internal combustion engine |
US20050123426A1 (en) * | 2003-12-03 | 2005-06-09 | Schaake Mark D. | Multi-directional pump |
US7153106B2 (en) * | 2003-01-16 | 2006-12-26 | R. Conrader Company | Air compressor unit inlet control |
US7226273B2 (en) * | 2002-09-03 | 2007-06-05 | Knorr-Brense Systeme Fuer Nutzfahrzeuge Gmbh | Method of generating compressed air, and compressor arrangement for implementing the method |
US7270110B2 (en) * | 2000-04-24 | 2007-09-18 | Frank Keoppel | Four stroke internal combustion engine with inlet air compression chamber |
-
2007
- 2007-12-12 US US11/954,699 patent/US20090155106A1/en not_active Abandoned
Patent Citations (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3613646A (en) * | 1969-09-10 | 1971-10-19 | Souichi Hisada | Secondary air injection system for an internal combustion engine |
US3554175A (en) * | 1969-12-08 | 1971-01-12 | Chrysler Corp | Evaporative emission control system |
US4097202A (en) * | 1976-06-21 | 1978-06-27 | Billy Frank Price | Auxiliary compressor assembly |
US4486157A (en) * | 1981-12-16 | 1984-12-04 | Nissan Motor Company, Limited | Reciprocating compressor |
US5107960A (en) * | 1990-06-28 | 1992-04-28 | Rix Industries, Inc. | Crankcase oil-barrier system |
US5954690A (en) * | 1996-04-14 | 1999-09-21 | Medela Holding Ag | Alternating suction breastpump assembly and method |
US5762480A (en) * | 1996-04-16 | 1998-06-09 | Adahan; Carmeli | Reciprocating machine |
US6056516A (en) * | 1997-10-11 | 2000-05-02 | Wabco Standard Gmbh | Compressor installation having a control valve arrangement for independently switching compression chambers between delivery partial delivery and idle operation |
US7270110B2 (en) * | 2000-04-24 | 2007-09-18 | Frank Keoppel | Four stroke internal combustion engine with inlet air compression chamber |
US6561159B1 (en) * | 2000-12-05 | 2003-05-13 | Louis W Mower | Crankcase inducted self-supercharging four cycle internal combustion engine |
US20020155007A1 (en) * | 2001-04-19 | 2002-10-24 | Mietto Virgilio | Intake regulator for compressed air in a reservoir |
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