WO2016068971A1 - Pompe à cylindrée variable et pressions multiples, à commande mécanique - Google Patents

Pompe à cylindrée variable et pressions multiples, à commande mécanique Download PDF

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Publication number
WO2016068971A1
WO2016068971A1 PCT/US2014/063309 US2014063309W WO2016068971A1 WO 2016068971 A1 WO2016068971 A1 WO 2016068971A1 US 2014063309 W US2014063309 W US 2014063309W WO 2016068971 A1 WO2016068971 A1 WO 2016068971A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
control ring
spring
pump control
chamber
Prior art date
Application number
PCT/US2014/063309
Other languages
English (en)
Inventor
Ayres Pinto DE ANDRADE FILHO
Joao Luiz De Carvalho Meira
Eduardo Gubbiotti Ribeiro
Original Assignee
Melling Tool Comapny
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 Melling Tool Comapny filed Critical Melling Tool Comapny
Priority to PCT/US2014/063309 priority Critical patent/WO2016068971A1/fr
Priority to US15/523,563 priority patent/US20170306948A1/en
Publication of WO2016068971A1 publication Critical patent/WO2016068971A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3441—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • F04C2/3442—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
    • F04C14/223—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam
    • F04C14/226—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members using a movable cam by pivoting the cam around an eccentric axis
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/14—Lubricant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure
    • F04C2270/185—Controlled or regulated

Definitions

  • This disclosure relates to the field of variable displacement vane pumps, and more particularly, to a variable displacement vane pump having a biasing assembly that can provide multiple equilibrium pressures within a control chamber.
  • Variable displacement vane pumps are well-known and can include a displacement adjusting structure in the form of a pump control ring that can be moved to alter the rotor eccentricity of the pump and hence alter the volumetric capacity of the pump. If the pump is supplying a system with a substantially constant orifice size, such as an automobile engine lubrication system, changing the output volume of the pump is equivalent to changing the pressure produced by the pump.
  • the equilibrium pressure is selected to be a pressure which is acceptable for expected operating range of the engine and is thus somewhat of a compromise, as, for example, the engine may be able to operate acceptably at lower operating speeds with a lower working fluid pressure than is required at a higher operating engine speeds.
  • the engine designers will select an equilibrium pressure for the pump which meets the worst case (higher operating speeds) conditions.
  • the pump will be operating at a higher capacity than necessary for those speeds, wasting energy pumping the surplus, unnecessary working fluid.
  • variable displacement vane pumps having a housing, a biasing assembly, and a control chamber.
  • the housing has a pump chamber.
  • the pump chamber has a fluid inlet, a fluid outlet, a pump control ring, and a vane pump rotor.
  • the pump control ring is disposed within the housing for altering the displacement of the pump by rotating between a first position that corresponds to a maximum volumetric capacity of the pump, a second position that corresponds to an intermediary volumetric capacity of the pump, and a third position that corresponds to a minimum volumetric capacity of the pump.
  • the vane pump rotor is rotatably mounted within the pump control ring and has a plurality of slidably mounted vanes engaging an inside surface of the pump control ring.
  • the vane pump rotor also has an axis of rotation eccentric from a center of the pump control ring.
  • the vane pump rotor rotates to pressurize fluid as the fluid moves from the fluid inlet to the fluid outlet.
  • the biasing assembly urges the pump control ring toward the first position.
  • the biasing assembly applies a first biasing force to the pump control ring when the pump control ring is located between the first position and the second position and applies a second biasing force to the pump control ring when the pump control ring is located between the second position and the third position.
  • the control chamber is formed between the housing and the pump control ring. The fluid pressure within the control chamber urges the pump control ring toward the third position.
  • a second aspect of the disclosed embodiments is a variable displacement vane pump having a housing, a biasing assembly, a control chamber, a feedback path, and a spring chamber.
  • the housing has a pump chamber.
  • the pump chamber has a fluid inlet, a fluid outlet, a pump control ring, and a vane pump rotor.
  • the pump control ring is disposed within the housing for altering the displacement of the pump by rotating between a first position that corresponds to a maximum volumetric capacity of the pump, a second position that corresponds to an intermediary volumetric capacity of the pump, and a third position that corresponds to a minimum volumetric capacity of the pump.
  • the vane pump rotor is rotatably mounted within the pump control ring and has a plurality of slidably mounted vanes engaging an inside surface of the pump control ring.
  • the vane pump rotor also has an axis of rotation eccentric from a center of the pump control ring.
  • the vane pump rotor rotates to pressurize fluid as the fluid moves from the fluid inlet to the fluid outlet.
  • the biasing assembly applies a first biasing force to the pump control ring when the pump control ring is located between the first position and the second position and applies a second biasing force to the pump control ring when the pump control ring is located between the second position and the third position.
  • the control chamber is formed between the housing and the pump control ring.
  • the fluid pressure within the control chamber urges the pump control ring toward the third position.
  • the feedback path is in communication with the fluid outlet supplying a pressurized fluid to the control chamber.
  • the spring chamber is formed between the housing and the pump control ring. The spring chamber has a maximum volume when the pump control ring is in the first position and a minimum volume when the pump control ring is in the third position.
  • the biasing assembly is disposed within the spring chamber.
  • FIG. 1 is a perspective view showing a variable displacement vane pump and an automotive oil sump reservoir
  • FIG. 2 is an exploded perspective view showing the variable displacement vane pump and the automotive oil sump reservoir of FIG. 1;
  • FIG. 3 is an illustration showing a control ring of the variable displacement vane pump in a first position that corresponds to a maximum volumetric capacity of the variable displacement vane pump;
  • FIG. 4 is an illustration showing the control ring of the variable displacement vane pump in a second position that corresponds to an intermediary volumetric capacity of the variable displacement vane pump and a first stage equilibrium pressure;
  • FIG. 5 is an illustration showing the control ring of the variable displacement vane pump in a third position that corresponds to a minimum volumetric capacity of the variable displacement vane pump and a second stage equilibrium pressure;
  • FIG. 6 is a cross-sectional plain view of a biasing assembly of the variable displacement vane pump
  • FIG. 7 is a diagram showing the variable displacement vane pump incorporated into a lubricating system of an automobile engine.
  • FIG. 8 is a graph showing operation of the variable displacement vane pump with the biasing assembly.
  • the present invention provides a pump that may be utilized to pump a fluid, such as automotive engine lubricant.
  • the pump 10 may be a variable displacement vane pump. In automobile engine applications, the pump 10 may be connected to an oil sump reservoir 12.
  • a housing 14 of the pump 10 may include a back side 16, a midsection 18, a cover 20, and a plate 22.
  • the midsection 18 forms the peripheral walls of the housing 14, in which pumping and control chambers are formed, as will be explained herein.
  • the cover 20 is connected to and sealed to the midsection 18.
  • the back side 16 of the housing defines fluid flow paths for the pump 10 to allow fluid to enter and exit the pump 10.
  • the plate 22 is mounted between the back side 16 and the midsection 18 of the housing 14 and includes apertures that define locations where fluid can pass between the back side 16 of the housing 14 and the chambers defined within the midsection 18 of the housing.
  • a pump control ring 28 is pivotally connected to the housing 14 by a pivot pin 30 and, optionally, a needle bearing 32.
  • the pivot pin 30 extends through an aperture 31 that is formed near an outer periphery of a generally circular portion 60 (shown in FIGS. 3-5) of the pump control ring 28.
  • the needle bearing 32 is mounted between the pivot pin 30 and the pump control ring 28 so as to provide easy pivoting of the pump control ring 28 relative to the pivot pin 30.
  • a regulating member 62 (shown in FIGS. 3-5) extends outward from the circular portion 60 of the pump control ring 28.
  • the vane pump rotor 34 and the pump control ring 28 are substantially circular in shape.
  • the center of the pump control ring 28 is located eccentrically with respect to the center of a vane pump rotor 34 is mounted within the pump control ring 28.
  • the vane pump rotor 34 has a plurality of vanes 36 that are mounted for sliding within slots that are formed in the vane pump rotor 34.
  • the vane pump rotor 34 includes a ring 35 (shown in FIGS. 3-5).
  • the vanes 36 pass through openings formed in the ring 35 and are engaged by the ring 35 such that rotation of the ring 35 causes rotation of the vanes 36.
  • a single ring 35 is shown, some implementations includes two or more rings to help keep the vanes 36 in contact with the pump control ring 28, especially at low speeds.
  • the vanes 36 engage an inside surface (not shown) of the pump control ring 28, and the vanes 36 slide within the slots in response to movement of the pump control ring 28 with respect to the vane pump rotor 34.
  • the vane pump rotor 34 has an axis of rotation that is eccentric from the center of the pump control ring 28, as will be described further herein.
  • a drive shaft 38 is driven by any suitable means, such as an automotive engine or other mechanism that can supply working fluid to operation the pump 10.
  • the drive shaft 38 engages the vane pump rotor 34 and rotates the vane pump rotor 34 as the drive shaft 38 is driven. [0021] As shown in FIGS.
  • the pump control ring 28, the vane pump rotor 34, and the vanes 36 cooperate to define working chambers 50 that are located between successive pairs of vanes 36.
  • Pumping from a fluid inlet 42 of the pump 10 to the fluid outlet 44 of the pump 10 occurs because the volume of each working chamber 50 changes as it passes from the fluid inlet 42 to the fluid outlet 44, thereby increasing the pressure of the fluid.
  • the fluid inlet 42 is the low pressure side of the pump 10
  • the fluid outlet 44 is the high pressure side of the pump 10.
  • Pivoting of the pump control ring 28 is operable to vary the amount of volumetric change of each working chamber 50 during rotation, which in turn changes the volumetric displacement of the pump 10.
  • the pump control ring 28 pivots between a first position (shown in FIG. 3), a second position (shown in FIG. 4), and a third position (shown in FIG. 5).
  • the first position corresponds to a maximum volumetric capacity of the pump 10.
  • the pump control ring 28 has reached its end limit of travel in a clockwise direction with respect to the pivot pin 30 by engagement of the pump control ring 28 with the housing 14.
  • the second position corresponds to an intermediary volumetric capacity of the pump 10.
  • the third position corresponds to a minimum volumetric capacity of the pump 10.
  • the pump control ring 28 In the third position, the pump control ring 28 has reached its end limit of travel in a counter-clockwise direction with respect to the pivot pin 30.
  • the volumetric capacity of the pump 10 varies as a function of the position of the pump control ring 28, which under working conditions, often will be disposed somewhere between the first position and the third position.
  • a spring chamber 40 and a control chamber 41 are defined within the housing 14 to regulate the position of the pump control ring 28.
  • a first seal 46 and a second seal 48 are mounted within respective recesses in the pump control ring 28 and engage an inner surface of the housing 14 to define the control chamber 41.
  • the control chamber 41 is formed within a space that is disposed outward of the pump control ring 28, between the pump control ring 28 and an interior surface of the housing 14.
  • a second side 66 of the regulating member 62 faces the control chamber 41.
  • the volume of the control chamber 41 changes based on the position of the pump control ring 28, given that the regulating member 62 moves with the pump control ring 28.
  • the control chamber 41 is at a minimum volume when the pump control ring 28 is in the first position.
  • the volume of the control chamber 41 increases as the pump control ring 28 moves toward the third position and reaches a maximum volume when the pump control ring 28 is in the third position.
  • the spring chamber 40 is formed within a space that is disposed outward of the pump control ring 28, between the pump control ring 28 and an interior surface of the housing 14.
  • a first side 64 of a regulating member 62 faces the spring chamber 40.
  • the volume of the spring chamber 40 is at a maximum volume when the pump control ring 28 is in the first position.
  • the volume of the spring chamber 40 decreases as the pump control ring 28 moves toward the third position and reaches a minimum volume when the pump control ring 28 is in the third position.
  • a feedback path 82 supplies pressurized fluid to the control chamber 41 from a fluid outlet 44 of the pump 10. This can be done directly, by routing the feedback path 82 directly to the control chamber 41 from the fluid outlet 44, or indirectly, by routing the feedback path 82 to another portion of the pump 10 that is in fluid communication with the fluid outlet 44 and is at equilibrium with the fluid outlet 44. Because the feedback path 82 is in fluid communication with the fluid outlet 44 of the pump 10, the feedback path 82 receives pressurized fluid at the outlet pressure of the pump 10. In some implementations, a restrictor (not shown) is formed along the feedback path 82 to control the amount of pressure provided via the feedback path 82.
  • the feedback path 82 is formed in housing 14 and is fluid communication with the control chamber 41 and the fluid outlet 44.
  • a biasing assembly 90 may be formed within the spring chamber 40 to control the position of the pump control ring 28 and the volume of the control chamber 41.
  • the biasing assembly 90 urges the pump control ring 28 toward the first position by applying a first biasing force to the pump control ring 28 when the pump control ring 28 is located between the first position and the second position.
  • the pressure will eventually be able to overcome the first biasing force and move the pump control ring 28 toward the second position.
  • the pressure within the control chamber 41 will remain substantially constant, resulting in a first equilibrium pressure.
  • a second biasing force is activated and applied to urge the pump control ring 28 toward the second position. If the pressure continues to increase within the control chamber 41, the pressure will eventually be sufficient to overcome the second biasing force and the pump control ring 28 will pivot toward the third position. As the pump control ring 28 pivots toward the third position, the pressure within the control chamber 41 will remain substantially constant, resulting in a second equilibrium pressure.
  • two biasing forces are described, it will be obvious to one skilled in the art that the number of biasing forces acting on the pump control ring 28 could be varied to alter the number of equilibrium pressures that the pump 10 can maintain.
  • the biasing assembly 90 has a first compression spring 51, a second compression spring 52, and a control pin 53.
  • the first compression spring 51 and the second compression spring 52 are substantially coaxially aligned with the first compression spring 51 positioned closer to the regulating member 62.
  • the first compression spring 51 applies a first spring load to the pump control ring 28 and the second compression spring 52 applies a second spring load to the pump control ring 28.
  • the second spring load is greater than the first spring load.
  • the control pin 53 has a substantially T-shaped configuration with a first leg 54 extending through the radial center of the first compression spring 51 and a second leg 55 located between the first compression spring 51 and the second compression spring 52.
  • the spring chamber 40 may an annular shoulder 43 that the second leg 55 of the control pin 53 may abut to prevent the first leg 54 of the control pin 53 from engaging the regulating member 62 of the pump control ring 28 when the first compression spring 51 is not compressed.
  • the first side 64 of the regulating member 62 engages a first end 56 of the first compression spring 51 and compresses the first compression spring 51 toward the second leg 55 of the control pin 53.
  • the second leg 55 of the control pin 53 will compress the second compression spring 52 toward the housing 14.
  • first compression spring 51 and the second compression spring 52 act independently in the illustrated example, it is anticipated that the first compression spring 51 and the second compression spring 52 could combine to provide the second biasing force.
  • first compression spring 51 may have substantially the diameter as the width of the spring chamber 40.
  • the biasing assembly is not limited to being housed within the spring chamber 40 or utilizing compression springs. Other biasing assemblies could be utilized. For example, there could be two tension springs or two compression springs could be used in a location other than the spring chamber 40.
  • the first compression spring 51 and the second compression spring 52 have the same spring rate. In other implementations, the first compressions spring 51 and the second compression spring 52 have different spring rates. For example, the first compression spring 51 can have a first spring rate and the second compression spring 52 can have a second spring rate that is greater than the first spring rate 51.
  • FIG. 7 is a diagram showing the pump 10 incorporated in a lubricating system of an automobile engine 100.
  • the pump 10 receives fluid, such as oil, from the oil sump reservoir 12 at an inlet pressure PI via the fluid inlet 42 of the pump 10.
  • the pump 10 increases the pressure of the fluid to an outlet pressure P2, and the fluid exits the pump 10 at the fluid outlet 44.
  • the fluid travels from the fluid outlet 44 of the pump 10 to the automobile engine 100 via a supply circuit 102 and is subsequently returned to the oil sump reservoir 12 via a return circuit 104.
  • a portion of the fluid at the outlet pressure P2 is diverted from the fluid outlet 44 of the pump 10 to the control chamber 41 via the feedback path 82.
  • the pump control ring 28 is rotated toward the third position, thereby decreasing the volumetric output of the pump 10.
  • the use of the biasing assembly 90 allows the pump 10 to provide multiple equilibrium pressures in the control chamber 41, as shown in FIG. 8.
  • the pump control ring 28 is in the first position as the pressure in the control chamber 41 is not sufficient to overcome the first biasing force of the first compression spring 51 to compress the first compression spring 51, which is shown as segment 701.
  • the pump 10 will have the maximum per- rotation volumetric capacity.
  • the pump control ring 28 will move toward the second position, which is shown as segment 702.
  • the movement of the pump control ring 28 toward the second position linearly decreases the per-rotation volumetric capacity of the pump 10 and allows the pressure within the control chamber 41 to remain substantially constant at the first equilibrium pressure.
  • the pressure in the control chamber 41 continues to rise, there will be a point where the regulating member 62 will engage the control pin 53, preventing the first compression spring 51 from compressing further.
  • the per-rotation volumetric capacity of the pump 10 will remain constant because the pressure within the control chamber 41 is unable to overcome the second biasing force of the second compression spring 52 to compress the second compression spring 52.
  • the pump control ring 28 remains in the second position.
  • the pump control ring 28 will move toward the third position, which is shown as segment 704.
  • the movement of the pump control ring 28 toward the third position linearly decreases the per-rotation volumetric capacity of the pump 10 and allows the pressure within the control chamber 41 to remain substantially constant at the second equilibrium pressure.
  • the pump 10 will have the minimum volumetric capacity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

Cette invention concerne une pompe à ailettes à cylindrée variable, comprenant un ensemble de sollicitation qui applique une première force de sollicitation à une bague de régulation de pompe lorsque la bague de régulation de pompe est située entre une première position et une deuxième position et applique une seconde force de sollicitation lorsque la bague de régulation de pompe est située entre la deuxième position et une troisième position. La première position de la bague de régulation de pompe correspond à une capacité volumétrique maximale de la pompe, la deuxième position correspond à une capacité volumétrique intermédiaire de la pompe, et la troisième position correspond à une capacité volumétrique minimale de la pompe. La pression fluidique à l'intérieur d'une chambre de régulation pousse la bague de régulation vers la seconde position.
PCT/US2014/063309 2014-10-31 2014-10-31 Pompe à cylindrée variable et pressions multiples, à commande mécanique WO2016068971A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/US2014/063309 WO2016068971A1 (fr) 2014-10-31 2014-10-31 Pompe à cylindrée variable et pressions multiples, à commande mécanique
US15/523,563 US20170306948A1 (en) 2014-10-31 2014-10-31 Multiple Pressure Variable Displacement Pump with Mechanical Control

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US2014/063309 WO2016068971A1 (fr) 2014-10-31 2014-10-31 Pompe à cylindrée variable et pressions multiples, à commande mécanique

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WO2016068971A1 true WO2016068971A1 (fr) 2016-05-06

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Cited By (2)

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Publication number Priority date Publication date Assignee Title
CN110778496A (zh) * 2018-07-24 2020-02-11 通用汽车环球科技运作有限责任公司 具有滑动元件的弹簧结构
US20230023310A1 (en) * 2021-07-23 2023-01-26 Hamilton Sundstrand Corporation Variable displacement pump systems with direct actuation

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Publication number Priority date Publication date Assignee Title
DE102021119936A1 (de) 2021-07-30 2023-02-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit Stellstrukturfeder mit versetzter Wirklinie

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Publication number Priority date Publication date Assignee Title
US4538974A (en) * 1983-09-17 1985-09-03 Glyco Antriebstechnik Gmbh Vane-type oil pump for automotive vehicle
US20080308062A1 (en) * 2007-06-14 2008-12-18 Hitachi, Ltd. Variable Displacement Pump
US20110123379A1 (en) * 2009-11-25 2011-05-26 Hitachi Automotive Systems, Ltd. Variable displacement pump
US20130034460A1 (en) * 2011-08-02 2013-02-07 Hitachi Automotive Systems, Ltd. Variable Displacement Vane Pump
WO2013049929A1 (fr) * 2011-10-07 2013-04-11 Magna Powertrain, Inc. Commande de pompe à double ressort à précompression

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US2658456A (en) * 1948-07-29 1953-11-10 Gunnar A Wahlmark Fluid displacement device
US2768585A (en) * 1952-12-18 1956-10-30 Schwitzer Corp Pump control mechanism

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Publication number Priority date Publication date Assignee Title
US4538974A (en) * 1983-09-17 1985-09-03 Glyco Antriebstechnik Gmbh Vane-type oil pump for automotive vehicle
US20080308062A1 (en) * 2007-06-14 2008-12-18 Hitachi, Ltd. Variable Displacement Pump
US20110123379A1 (en) * 2009-11-25 2011-05-26 Hitachi Automotive Systems, Ltd. Variable displacement pump
US20130034460A1 (en) * 2011-08-02 2013-02-07 Hitachi Automotive Systems, Ltd. Variable Displacement Vane Pump
WO2013049929A1 (fr) * 2011-10-07 2013-04-11 Magna Powertrain, Inc. Commande de pompe à double ressort à précompression

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110778496A (zh) * 2018-07-24 2020-02-11 通用汽车环球科技运作有限责任公司 具有滑动元件的弹簧结构
US20230023310A1 (en) * 2021-07-23 2023-01-26 Hamilton Sundstrand Corporation Variable displacement pump systems with direct actuation

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