WO2014141013A1 - Pompe à palettes ayant de multiples chambres de commande - Google Patents

Pompe à palettes ayant de multiples chambres de commande Download PDF

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Publication number
WO2014141013A1
WO2014141013A1 PCT/IB2014/059506 IB2014059506W WO2014141013A1 WO 2014141013 A1 WO2014141013 A1 WO 2014141013A1 IB 2014059506 W IB2014059506 W IB 2014059506W WO 2014141013 A1 WO2014141013 A1 WO 2014141013A1
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WO
WIPO (PCT)
Prior art keywords
pump
control ring
control
chamber
ring
Prior art date
Application number
PCT/IB2014/059506
Other languages
English (en)
Inventor
Matthew Williamson
David R. Shulver
Cezar Tanasuca
Original Assignee
Magna Powertrain Inc.
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
Priority claimed from US13/800,227 external-priority patent/US9181803B2/en
Application filed by Magna Powertrain Inc. filed Critical Magna Powertrain Inc.
Priority to CN201480013705.5A priority Critical patent/CN105074217B/zh
Priority to KR1020157027875A priority patent/KR101789899B1/ko
Priority to MX2015012591A priority patent/MX365215B/es
Priority to JP2015562455A priority patent/JP6130525B2/ja
Priority to CA2902472A priority patent/CA2902472C/fr
Priority to EP14763782.1A priority patent/EP2971779B1/fr
Publication of WO2014141013A1 publication Critical patent/WO2014141013A1/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
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • 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

Definitions

  • the present invention relates to a variable capacity vane pump. More specifically, the present invention relates to a variable capacity vane pump including multiple control chambers. Different sources of pressurized fluid may be provided to the control chambers to control the pump displacement.
  • Variable capacity vane pumps are well known and can include a capacity adjusting element, 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 flow of the pump is equivalent to changing the pressure produced by the pump.
  • the equilibrium pressure is determined by the area of the control ring against which the working fluid in the control chamber acts, the pressure of the working fluid supplied to the chamber and the bias force generated by the return spring.
  • the equilibrium pressure is selected to be a pressure which is acceptable for the 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 higher engine operating speeds.
  • the engine designers will select an equilibrium pressure for the pump which meets the worst case (high operating speed) conditions.
  • the pump will be operating at a higher capacity than necessary for those speeds, wasting energy pumping the surplus, unnecessary, working fluid.
  • variable capacity vane pump which can provide at least two selectable equilibrium pressures in a reasonably compact pump housing. It is also desired to have a variable capacity vane pump wherein reaction forces on the pivot pin for the pump control ring are reduced.
  • a variable capacity vane pump includes a first control chamber between a pump casing and a first portion of a pump control ring.
  • the first portion of the control ring circumferentially extends on either side of a pivot pin.
  • a second control chamber is provided between the pump casing and a second portion of the pump control ring.
  • the first and second control chambers are operable to receive pressurized fluid to create a force to move the pump control ring to reduce the volumetric capacity of the pump.
  • a return spring biases the pump ring toward a position of maximum volumetric capacity.
  • a variable volumetric capacity vane pump includes a pump casing including a pump chamber having an inlet port and an outlet port.
  • a pump control ring pivots within the pump chamber to alter the volumetric capacity of the pump.
  • a rotor is rotatably mounted within the pump control ring and includes slots in receipt of slidable vanes.
  • First, second, and third control chambers are formed between the pump casing and an outer surface of the pump control ring. The first and second control chambers are selectively operable to receive pressurized fluid to create forces to move the pump control ring to reduce the volumetric capacity of the pump.
  • the third chamber is in constant receipt of pressurized fluid from the outlet of the pump.
  • a return spring is positioned within the casing to act between the pump ring and the casing to bias the pump ring toward a position of maximum volumetric capacity and act against the force generated by the pressurized fluid within the first and second control chambers.
  • Figure 1 is a front view of a variable capacity vane pump in accordance with the present invention with the control ring positioned for maximum rotor eccentricity;
  • Figure 2 is a front perspective view of the pump of Figure 1 with the control ring positioned for maximum rotor eccentricity;
  • Figure 3 is the a front view of the pump of Figure 1 with the control ring position for minimum eccentricity and wherein the areas of the pump control chambers are in hatched line;
  • Figure 4 shows a schematic representation of a prior art variable capacity vane pump
  • Figure 5 shows a front view of the pump of Figure 1 wherein the rotor and vanes have been removed to illustrate the forces within the pump;
  • Figure 6 provides an exploded perspective view of an alternate variable displacement pump
  • Figure 7 provides another exploded perspective view of the pump depicted in Figure 6;
  • Figure 8 is a cross-sectional view taken through the pump depicted in Figures 6 and 7;
  • Figure 9 is a schematic including a cross-sectional view of another alternate variable capacity vane pump
  • Figure 10 is an exploded perspective view of the vane pump depicted in Figure 9.
  • Figure 1 1 is a partial plan view of the pump depicted in Figures
  • variable capacity vane pump in accordance with an embodiment of the present invention is indicated generally at 20 in Figures 1 , 2 and 3.
  • pump 20 includes a housing or casing 22 with a front face 24 which is sealed with a pump cover (not shown) and a suitable gasket, to an engine (not shown) or the like for which pump 20 is to supply pressurized working fluid.
  • Pump 20 includes an input member or drive shaft 28 which is driven by any suitable means, such as the engine or other mechanism to which the pump is to supply working fluid, to operate pump 20.
  • a pump rotor 32 located within a pump chamber 36 is turned with drive shaft 28.
  • a series of slidable pump vanes 40 rotate with rotor 32, the outer end of each vane 40 engaging the inner surface of a pump control ring 44, which forms the outer wall of pump chamber 36.
  • Pump chamber 36 is divided into a series of working fluid chambers 48, defined by the inner surface of pump control ring 44, pump rotor 32 and vanes 40.
  • the pump rotor 32 has an axis of rotation that is eccentric from the center of the pump control ring 44.
  • Pump control ring 44 is mounted within casing 22 via a pivot pin 52 which allows the center of pump control ring 44 to be moved relative to the center of rotor 32.
  • the volume of working fluid chambers 48 changes as the chambers 48 rotate around pump chamber 36, with their volume becoming larger at the low pressure side (the left hand side of pump chamber 36 in Figure 1 ) of pump 20 and smaller at the high pressure side (the right hand side of pump chamber 36 in Figure 1 ) of pump 20.
  • This change in volume of working fluid chambers 48 generates the pumping action of pump 20, drawing working fluid from an inlet port 50 and pressurizing and delivering it to an outlet port 54.
  • pump 20 includes two control chambers 60 and 64, best seen in Figure 3, to control pump ring 44.
  • Control chamber 60 the rightmost hatched area in Figure 3, is formed between pump casing 22, pump control ring 44, pivot pin 52 and a resilient seal 68, mounted on pump control ring 44 and abutting casing 22.
  • control chamber 60 is in direct fluid communication with pump outlet 54 such that pressurized working fluid from pump 20 which is supplied to pump outlet 54 also fills control chamber 60.
  • control chamber 60 need not be in direct fluid communication with pump outlet 54 and can instead be supplied from any suitable source of working fluid, such as from an oil gallery in an automotive engine being supplied by pump 20.
  • Pressurized working fluid in control chamber 60 acts against pump control ring 44 and, when the force on pump control ring 44 resulting from the pressure of the pressurized working is sufficient to overcome the biasing force of return spring 56, pump control ring 44 pivots about pivot pin 52, as indicated by arrow 72 in Figure 3, to reduce the eccentricity of pump 20.
  • pump control ring 44 pivots about pivot pin 52, in the direction opposite to that indicated by arrow 72, to increase the eccentricity of pump 20.
  • Pump 20 further includes a second control chamber 64, the leftmost hatched area in Figure 3, which is formed between pump casing 22, pump control ring 44, resilient seal 68 and a second resilient seal 76.
  • Resilient seal 76 abuts the wall of pump casing 22 to separate control chamber 64 from pump inlet 50 and resilient seal 68 separates chamber 64 from chamber 60.
  • Control chamber 64 is supplied with pressurized working fluid through a control port 80.
  • Control port 80 can be supplied with pressurized working fluid from any suitable source, including pump outlet 54 or a working fluid gallery in the engine or other device supplied from pump 20.
  • a control mechanism (not shown) such as a solenoid operated valve or diverter mechanism is employed to selectively supply working fluid to chamber 64 through control port 80, as discussed below.
  • pressurized working fluid supplied to control chamber 64 from control port 80 acts against pump control ring 44.
  • pump 20 can operate in a conventional manner to achieve an equilibrium pressure as pressurized working fluid supplied to pump outlet 54 also fills control chamber 60.
  • pump 20 can be operated at a second equilibrium pressure. Specifically, by selectively supplying pressurized working fluid to control chamber 64, via control port 80, a second equilibrium pressure can be selected.
  • a solenoid-operated valve controlled by an engine control system can supply pressurized working fluid to control chamber 64, via control port 80, such that the force created by the pressurized working fluid on the relevant area of pump control ring 44 within chamber 64 is added to the force created by the pressurized working fluid in control chamber 60, thus moving pump control ring 44 further than would otherwise be the case, to establish a new, lower, equilibrium pressure for pump 20.
  • pressurized working fluid can be provided to both chambers 60 and 64 and pump ring 44 will be moved to a position wherein the capacity of the pump produces a first, lower, equilibrium pressure which is acceptable at low operating speeds.
  • control mechanism can operate to remove the supply of pressurized working fluid to control chamber 64, thus moving pump ring 44, via return spring 56, to establish a second equilibrium pressure for pump 20, which second equilibrium pressure is higher than the first equilibrium pressure.
  • chamber 60 is in fluid communication with pump outlet 54, it will be apparent to those of skill in the art that it is a simple matter, if desired, to alter the design of control chamber 60 such that it is supplied with pressurized working fluid from a control port, similar to control port 80, rather than from pump outlet 54.
  • a control mechanism such as a solenoid operated valve or a diverter mechanism can be employed to selectively supply working fluid to chamber 60 through the control port.
  • a control mechanism such as a solenoid operated valve or a diverter mechanism can be employed to selectively supply working fluid to chamber 60 through the control port.
  • pump casing 22 and pump control ring 44 can be fabricated to form one or more additional control chambers, as necessary.
  • Pump 20 offers a further advantage over conventional vane pumps such as pump 200 shown in Figure 4.
  • conventional vane pumps such as pump 200
  • the low pressure fluid 204 in the pump chamber exerts a force on pump ring 216 as does the high pressure fluid 208 in the pump chamber.
  • These forces result in a significant net force 212 on the pump control ring 216 and this force is largely carried by pivot pin 220 which is located at the point where force 212 acts.
  • pivot pin 220 carries large reaction forces 240 and 244, to counter net forces 212 and 228 respectively, and these forces can result in undesirable wear of pivot pin 220 over time and/or "stiction" of pump control ring 216, wherein it does not pivot smoothly about pivot pin 220, making fine control of pump 200 more difficult to achieve.
  • the low pressure side 300 and high pressure side 304 of pump 20 result in a net force 308 which is applied to pump control ring 44 almost directly upon pivot pin 52 and a corresponding reaction force, shown as a horizontal (with respect to the orientation shown in the Figure) force 312, is produced on pivot pin 52.
  • resilient seal 68 is located relatively closely to pivot pin 52 to reduce the area of pump control ring 44 upon which the pressurized working fluid in control chamber 60 acts and thus to significantly reduce the magnitude of the force 316 produced on pump control ring 44.
  • control chamber 60 is positioned such that force 316 includes a horizontal component, which acts to oppose force 308 and thus reduce reaction force 312 on pivot pin 52.
  • the vertical (with respect to the orientation shown in the Figure) component of force 316 does result in a vertical reaction force 320 on pivot pin 52 but, as mentioned above, force 316 is of less magnitude than would be the case with conventional pumps and the vertical reaction force 320 is also reduced by a vertical component of the biasing force 324 produced by return spring 56
  • control chamber 60 and return spring 56 results in reduced reaction forces on pivot pin 52 and can improve the operating lifetime of pump 20 and can reduce "stiction" of pump control ring 44 to allow smoother control of pump 20.
  • this unique positioning is not limited to use in variable capacity vane pumps with two or more equilibrium pressures and can be employed with variable capacity vane pumps with single equilibrium pressures.
  • FIG. 6-8 depict another variable capacity vane pump constructed in accordance with the teachings of the present disclosure and identified at reference numeral 400.
  • Pump 400 includes a housing 402 including a first cover 404 fixed to a second cover 406 by a plurality of fasteners 408.
  • a dowel pin 409 aligns the first and second covers.
  • Pump 400 includes an input or a drive shaft 410 having at least one end protruding from housing 402.
  • Drive shaft 410 may be driven by any suitable means such as an internal combustion engine.
  • a rotor 412 is fixed for rotation with drive shaft 410 and positioned within a pumping chamber 414 defined by pump housing 402. Vanes 416 are slidably engaged within radially extending slots 418 defined by rotor 412.
  • Sealing surface 422 is shaped as a circular cylinder having a center which may be offset from a center of drive shaft 410. Retaining rings 425 limit the inboard extent to which the vanes may slide to maintain engagement of surfaces 420 with surface 422.
  • Pump control ring 424 is positioned within chamber 414 and is pivotally coupled to housing 402 via a pivot pin 426.
  • Pump control ring 424 includes a radially outwardly extending arm 428.
  • a bias spring 430 engages arm 428 to urge pump control ring 424 toward a position of maximum capacity.
  • Pump control ring 424 includes first through third projections identified at reference numerals 432, 434, 436. Each of the first through third projections includes an associated groove 438, 440, 442. A first seal assembly 446 is positioned within first groove 438 to sealingly engage housing 402. A second seal assembly 448 is positioned within second groove 440 to sealingly engage a different portion of housing 402. A third seal assembly 450 is positioned within third groove 442. Third seal assembly 450 sealingly engages another portion of housing 402. Each seal assembly includes a cylindrically shaped first elastomer 452 engaging a second elastomer 454 having a substantially rectangular cross-section. Each seal assembly is positioned within an associated seal groove.
  • a first chamber 460 extends between first seal assembly 446 and third seal assembly 450 and between an outer surface of pump control ring 424 and housing 402.
  • a second chamber 462 is defined between first seal assembly 446 and second seal assembly 448, as well as the other surface of pump control ring 424 and housing 402.
  • First seal assembly 446 is positioned relative to pivot pin 426 to define a first radius or moment arm Ri.
  • the position of third seal assembly 450 also defines a radius or moment arm R 2 in relation to the center of pivot pin 426.
  • the length of moment arm R defined by first seal assembly 446 is greater than the length of moment arm R 2 defined by the position of third seal assembly 450 such that a turning moment is generated when first chamber 460 is pressurized. The turning moment urges pump control ring 424 to oppose the force applied by bias spring 430.
  • First seal assembly 446 is circumferentially spaced apart from third seal assembly 450 an angle greater than 100 degrees with the angle vertex being the center of the pump control ring cavity bounded by surface 422. Figure 8 depicts this angle as approximately 1 17 degrees. It should be appreciated that the position of first seal assembly 446 and second seal assembly 448 relative to pivot pin 426 also causes the pressurized fluid entering the second chamber to impart a moment of pump control ring 424 that opposes the force applied by bias ring 430
  • An outlet port 470 extends through housing 402 to allow pressurized fluid to exit pump 400.
  • An enlarged discharge cavity 472 is defined by housing 402. Enlarged discharge cavity 472 extends from third seal assembly 450 to outlet port 470. It should be appreciated that enlarged discharge cavity extends on either side of pivot pin 426. This feature is provided by having the outer surface 476 of pump control ring 424 being spaced apart from an inner wall 478 of housing 402.
  • first cover 404 includes a stanchion 482 including an aperture 484 for receipt of pivot pin 426. Stanchion 482 is spaced apart from inner wall 478. Relatively low resistance to fluid discharge is encountered by incorporating this configuration.
  • pump 400 may be configured to operate in at least two different modes.
  • first chamber 460 is provided pressurized fluid at pump outlet pressure.
  • second chamber 462 may be selectively supplied pressurized fluid from any source of pressure through the use of an on/off solenoid valve.
  • an upper equilibrium pressure of pump 400 is defined by the pump outlet pressure and a lower equilibrium pressure may be defined by the second source.
  • pump 400 may be associated with a proportional solenoid valve which may be operable to continuously vary the pressure to second chamber 462 and allow intermediate equilibrium pressures. As such, pump 400 operates at an infinite number of equilibrium pressures and not only the two fixed pressures as provided in the first arrangement.
  • FIG. 9-1 1 depict another alternate variable displacement pump at reference numeral 500.
  • Pump 500 may form a portion of a lubrication system 502 useful for supplying pressurized lubricant to an engine, transmission or other vehicle power transfer mechanism.
  • Lubrication system 502 includes a reservoir 504 providing fluid to an inlet pipe 506 in fluid communication with an inlet 508 of pump 500.
  • An outlet 510 of pump 500 provides pressurized fluid to a cooler 512, a filter 514 and a main gallery 516. Pressurized fluid travelling through main gallery 516 is supplied to the component to be lubricated, such as an internal combustion engine. Pressurized fluid is also provided to a feedback line 518.
  • Feedback line 518 is in direct communication with a first control chamber 520 of pump 500.
  • a solenoid valve 522 acts to control the fluid communication between feedback line 518 and a second control chamber 524.
  • Pump 500 is similar to pump 400 regarding the use of a pivoting pump control ring 526, first through fourth seal assemblies 528, 530, 532, 534, a bias spring 536, vanes 538, a rotor 540, a rotor shaft 542 and retaining rings 544. Similar elements will not be described in detail.
  • First seal assembly 528 and second seal assembly 530 act in concert with an outer surface 546 of control ring 526 and a cavity wall 548 to at least partially define first control chamber 520.
  • Second control chamber 524 extends between second seal assembly 530 and third seal assembly 532 as well as between outer surface 546 and cavity wall 548.
  • An outlet passage 550 extends between first seal assembly 528 and fourth seal assembly 534.
  • a stanchion 554 includes an aperture 556 in receipt of a pivot pin 558 to couple control ring 526 for rotation with stanchion 554.
  • the enlarged outlet passage 550 substantially reduces restriction to pressurized fluid exiting pump 500.
  • pivot pin 558 may provide a sealing function and allow removal of fourth seal assembly 534.
  • First seal assembly 528 is positioned at a first distance from a center of pivot pin 558 to define a first moment arm R-i .
  • a moment arm R 2 is defined by the position of fourth seal assembly 534 in relation to pivot pin 558. If moment arm lengths Ri and R 2 are set to be equal, the pressure within outlet passage 550 provides no contribution to pressure regulation. On the other hand, moment arms Ri and R 2 may be designed to be unequal if a permanent contribution from the pump outlet pressure is desired. As such, outlet passage 550 may function as a third control chamber. For example, it may be beneficial to provide a pressure regulation at a vehicle cold start condition.
  • control ring 526 At cold start, it may be desirable to urge control ring 526 toward a position of minimum displacement as shown in Figure 1 1 . This may be accomplished by having moment arm R be longer than moment arm R 2 . Alternatively, it may be desirable to compensate for forces acting internally within pump 500 and acting on pump control ring 526. To address this concern, it may be desirable to construct moment arm Ri at a length less than the length of moment arm R 2 to urge pump control ring 526 toward the maximum displacement position.
  • Figure 9 represents control ring 526 at a position of maximum eccentricity, thereby providing maximum pump displacement.
  • first seal assembly 528 is circumferentially spaced apart from fourth seal assembly 534 an angle greater than 80 degrees.
  • first control chamber 520 is always active and may be in receipt of pressurized fluid from any source, such as the pump output.
  • Second control chamber 524 is switched on and off via solenoid 522.
  • the supply of pressurized fluid may be from any source.
  • Outlet passage 550, or third control chamber 550 may or may not contribute to the pressure controlling function as described in relation to the relative lengths of moment arms Ri and R 2 .
  • Pump 500 need only be associated with an on/off type solenoid valve 522 due to the provision of three control chambers.
  • Third control chamber 550 provides for a very low restriction outlet flow path.
  • First control chamber 520 and second control chamber 524 allow two equilibrium pressures that are determined by sources other than the pump outlet pressure.

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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

L'invention porte sur une pompe à palettes à capacité variable, qui comprend une première chambre de commande entre un carter de pompe et une première partie d'un anneau de commande de pompe. La première partie de l'anneau de commande s'étend de façon circonférentielle de part et d'autre d'un axe de pivotement. Une seconde chambre de commande est formée entre le carter de pompe et une seconde partie de l'anneau de commande de pompe. Les première et seconde chambres de commande peuvent recevoir un fluide mis sous pression pour créer une force servant à déplacer l'anneau de commande de pompe pour réduire la capacité volumétrique de la pompe. Un ressort de rappel sollicite l'anneau de pompe vers une position de capacité volumétrique maximale.
PCT/IB2014/059506 2013-03-13 2014-03-06 Pompe à palettes ayant de multiples chambres de commande WO2014141013A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
CN201480013705.5A CN105074217B (zh) 2013-03-13 2014-03-06 具有多控制室的叶片泵
KR1020157027875A KR101789899B1 (ko) 2013-03-13 2014-03-06 다중 제어 챔버를 구비한 베인 펌프
MX2015012591A MX365215B (es) 2013-03-13 2014-03-06 Bomba de paletas con multiples camaras de control.
JP2015562455A JP6130525B2 (ja) 2013-03-13 2014-03-06 複数の制御チャンバを備えるベーンポンプ
CA2902472A CA2902472C (fr) 2013-03-13 2014-03-06 Pompe a palettes ayant de multiples chambres de commande
EP14763782.1A EP2971779B1 (fr) 2013-03-13 2014-03-06 Pompe à palettes ayant de multiples chambres de commande

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US13/800,227 2013-03-13
US13/800,227 US9181803B2 (en) 2004-12-22 2013-03-13 Vane pump with multiple control chambers

Publications (1)

Publication Number Publication Date
WO2014141013A1 true WO2014141013A1 (fr) 2014-09-18

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Application Number Title Priority Date Filing Date
PCT/IB2014/059506 WO2014141013A1 (fr) 2013-03-13 2014-03-06 Pompe à palettes ayant de multiples chambres de commande

Country Status (7)

Country Link
EP (1) EP2971779B1 (fr)
JP (1) JP6130525B2 (fr)
KR (1) KR101789899B1 (fr)
CN (1) CN105074217B (fr)
CA (2) CA2902472C (fr)
MX (1) MX365215B (fr)
WO (1) WO2014141013A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3428450A4 (fr) * 2016-03-07 2019-01-16 Hitachi Automotive Systems, Ltd. Pompe à cylindrée variable
WO2022096134A1 (fr) 2020-11-09 2022-05-12 Pierburg Pump Technology Gmbh Pompe de graissage à cylindrée variable
CN114776582A (zh) * 2021-01-22 2022-07-22 Slpt国际泵业集团 具有改进的压力控制和范围的可变排量叶片泵

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Publication number Priority date Publication date Assignee Title
DE102016124104A1 (de) * 2016-12-12 2018-06-14 Schwäbische Hüttenwerke Automotive GmbH Hydraulikvorrichtung mit Dichtelement
CN106969249A (zh) * 2017-04-26 2017-07-21 奇瑞汽车股份有限公司 一种叶片式机油泵
CN107605720B (zh) * 2017-10-27 2019-06-28 湖南机油泵股份有限公司 一种基于双开关电磁阀的三级或四级可变排量机油泵
CN108894982B (zh) * 2018-08-21 2023-12-05 湖南机油泵股份有限公司 一种具有密封补偿功能的可变排量叶片泵
KR20210149179A (ko) * 2019-04-23 2021-12-08 스택폴 인터내셔널 엔지니어드 프로덕츠, 엘티디. 제어 챔버를 위한 개선된 시일 조립체를 지닌 베인 펌프
CN117052957B (zh) * 2023-10-10 2024-01-26 山东振宇厨业有限公司 一种燃气灶具联动安全调节阀

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006045190A1 (fr) * 2004-10-25 2006-05-04 Magna Powertrain Inc. Pompe a palettes a cylindree variable comprenant une chambre reductrice de force sur la bague de reglage de cylindree
CA2588817A1 (fr) * 2004-12-22 2006-06-29 Magna Powertrain Inc. Pompe a palettes de capacite variable comprenant des chambres de commande doubles
EP2253847A1 (fr) * 2009-05-18 2010-11-24 Pierburg Pump Technology GmbH Pompe à ailettes à lubrifiant à capacité variable

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US11168684B2 (en) 2016-03-07 2021-11-09 Hitachi Astemo, Ltd. Variable displacement pump
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CN114776582B (zh) * 2021-01-22 2024-05-24 Slpt国际泵业集团 具有改进的压力控制和范围的可变排量叶片泵

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JP2016510102A (ja) 2016-04-04
CA2902472C (fr) 2018-10-02
KR20150128866A (ko) 2015-11-18
KR101789899B1 (ko) 2017-10-25
EP2971779A1 (fr) 2016-01-20
CN105074217B (zh) 2017-03-15
MX365215B (es) 2019-05-27
JP6130525B2 (ja) 2017-05-17
CA3014939A1 (fr) 2014-09-18
EP2971779B1 (fr) 2020-08-05
CA2902472A1 (fr) 2014-09-18
EP2971779A4 (fr) 2016-12-07
CA3014939C (fr) 2020-07-14
CN105074217A (zh) 2015-11-18
MX2015012591A (es) 2016-01-20

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