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US20080038117A1 - Pumping System Employing a Variable-Displacement Vane Pump - Google Patents

Pumping System Employing a Variable-Displacement Vane Pump Download PDF

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Publication number
US20080038117A1
US20080038117A1 US10/571,704 US57170404A US2008038117A1 US 20080038117 A1 US20080038117 A1 US 20080038117A1 US 57170404 A US57170404 A US 57170404A US 2008038117 A1 US2008038117 A1 US 2008038117A1
Authority
US
United States
Prior art keywords
pump
pressure
chamber
oil
delivery
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US10/571,704
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English (en)
Inventor
Giacomo Armenio
Clement Kiefer
Massimo Rundo
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Pierburg Pump Technology Italy SpA
Original Assignee
Pierburg SpA
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 Pierburg SpA filed Critical Pierburg SpA
Assigned to PIERBURG S.P.A. reassignment PIERBURG S.P.A. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ARMENIO, GIACOMO, KIEFER, CLEMENT, RUNDO, MASSIMO
Publication of US20080038117A1 publication Critical patent/US20080038117A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/18—Pressure

Definitions

  • the present invention relates to a variable-displacement vane pump comprising a main body having a cavity, in which is movable a ring containing a rotor rotating about a fixed axis.
  • the rotor has a number of vanes, one end of each of which rests on the inner surface of the ring during rotation.
  • Means are also provided which, depending on a control pressure, move the ring between a centred position with respect to the rotation axis of the rotor, in which no pumping action takes place, and a predetermined eccentric position with respect to the rotation axis of the rotor.
  • Vane pumps of the above type are currently used to pump various fluids, such as oil in an internal combustion engine.
  • a pumping system employing a variable-displacement vane pump, as claimed in claim 1 .
  • FIG. 1 shows a first embodiment of the present invention
  • FIG. 2 shows a first configuration of a second embodiment
  • FIG. 3 shows a second configuration of the second embodiment in FIG. 2 ;
  • FIG. 4 shows a first configuration of a detail of the second embodiment in FIGS. 2 and 3 ;
  • FIG. 5 shows a second configuration of the FIG. 4 detail
  • FIG. 6 shows a third embodiment of the present invention.
  • Number 10 in FIG. 1 indicates a variable-delivery vane pump forming part of a pumping system 100 in accordance with the present invention.
  • Pump 10 comprises, in known manner, a main body 11 having a cavity 12 in which a ring 13 translates as described in detail later on.
  • Ring 13 houses a rotor 14 having a number of vanes 15 , which move radially inside respective radial slits 16 formed in rotor 14 , which is rotated in the direction indicated by arrow W (see below).
  • Main body 11 is closed by a cover not shown in the drawings.
  • rotor 14 houses a shaft 17 connected mechanically to rotor 14 ; and a floating ring 18 surrounding shaft 17 , and on which the other ends of vanes 15 rest.
  • Shaft 17 therefore has a centre P 1 which is fixed at all times; and ring 13 has a centre P 2 .
  • the distance P 1 P 2 represents the eccentricity E of pump 10 .
  • eccentricity E the delivery of pump 10 can be varied as required by a user device UT downstream from pump 10 (see below).
  • User device UT may be defined, for example, by an internal combustion engine (not shown).
  • ring 13 has a projection 19 housed partly in a chamber 20 ; and a projection 21 housed partly in a chamber 22 .
  • Projections 19 and 21 are located on opposite sides of centre P 2 of ring 13 , and have respective front surfaces A 1 and A 2 facing chambers 20 and 22 respectively.
  • surface A 2 is larger than surface A 1 . More specifically, tests and calculations have shown surface A 2 must be 1.4 to 1.7 times larger than surface A 1 .
  • a spring 22 a inside chamber 22 exerts a small force on surface A 2 to restore the system to a condition of maximum eccentricity E when system 100 is idle.
  • chambers 20 and 22 are formed in main body 11 of pump 10 .
  • Main body 11 also comprises an intake port 23 for drawing oil from a tank 24 ; and a delivery port 25 for feeding oil to user device UT.
  • a delivery conduit 26 extends from delivery port 25 to feed user device UT.
  • a first portion of the oil supplied to user device UT is diverted to chamber 20 by a conduit 27 , and a second portion of the oil is fed to chamber 22 by a conduit 28 .
  • the second portion of the oil in conduit 28 is almost all fed to chamber 22 by a conduit 28 a via a dissipating device 29 , in which a calibrated pressure loss occurs as the oil actually flows through it.
  • Conduit 28 is connected to a valve 30 by a conduit 28 b.
  • Valve 30 comprises a cylinder 31 housing a piston 32 .
  • piston 32 comprises a first portion 32 a and a second portion 32 b connected to each other by a rod 32 c.
  • Portions 32 a and 32 b are equal in cross section to cylinder 31 , whereas rod 32 c is smaller in cross section than cylinder 31 .
  • Cylinder 31 has a port 33 connected hydraulically to chamber 22 by a conduit 34 .
  • Conduit 28 b substantially provides for picking up a delivery pressure signal in conduit 28 , so as to act on the front surface A 3 of portion 32 a of piston 32 .
  • the dash line in FIG. 1 shows the situation in which port 33 is closed by second portion 32 b.
  • the oil is at atmospheric pressure (po).
  • Piston 32 is stressed elastically by a suitably sized spring 36 designed to generate a force which only permits movement of piston 32 when the delivery pressure (p 1 ) on surface A 3 reaches a given value.
  • a return conduit 37 from user device UT to tank 24 completes pumping system 100 .
  • eccentricity E is normally regulated by diverting a portion of the oil supply into a chamber, in which the delivery pressure acts directly on the ring; and an elastic counteracting force, generated by a spring, acts on the opposite side of the ring, so that the pump is set to an eccentricity E value ensuring the oil pressure and flow requested by the user device.
  • Incomplete fill has the side effect of generating a force acting in the direction indicated by arrow F 1 in FIG. 1 .
  • the user device fails to obtain the required delivery pressure, on account of this undesired force which, as stated, is substantially caused by incomplete oil fill of the gaps between the vanes.
  • piston 32 moves into the configuration shown by the continuous line in FIG. 1 , in which rod 32 c of piston 32 is located at port 33 , and so permits oil flow from chamber 22 to conduit 34 , and along conduit 35 into tank 24 .
  • Oil therefore also flows along conduit 28 a and through dissipating device 29 , so that, as opposed to the delivery pressure (p 1 ), a lower pressure (p 2 ) is present in chamber 22 .
  • the pressure (p 2 ) in chamber 22 is lower than the pressure (p 1 ) in chamber 20 , thus disassociating the two pressures to enable ring 13 to move in the direction indicated by arrow F 1 to establish a balanced eccentricity E value producing the desired oil flow to user deice UT.
  • valve 30 also acts as a pressure dissipating device to assist in creating the desired pressure (p 2 ) in chamber 22 .
  • the system has also proved stable.
  • valve 30 which is regulated solely by delivery pressure (p 1 ) and totally unaffected by undesired internal forces.
  • valve 30 opens, and oil flows along conduit 34 , through port 33 , and along conduit 35 to tank 24 , so that the pressure (p 2 ) in chamber 22 is lower than (p 1 ), and ring 13 moves in the direction of arrow F 1 to reduce displacement and therefore oil flow to user device UT.
  • dissipating device 29 and valve 30 are replaced by a three-way slide valve 50 .
  • Valve 50 comprises a cylinder 51 housing a slide 52 stressed by a spring 53 .
  • slide 52 comprises a first portion 52 a, a second portion 52 b, and a third portion 52 c. Portions 52 a and 52 b are connected by a rod 52 d, and portions 52 b and 52 c are connected by a rod 52 e.
  • Cylinder 51 comprises four ports 54 , 55 , 56 , 57 . More specifically, port 54 defines the first way of three-way valve 50 , ports 56 and 57 together define the second way, and port 55 defines the third way.
  • Slide 52 is controlled by delivery pressure (p 1 ).
  • the value of ⁇ 1, which represents the size of port 56 must be greater than ⁇ 2, i.e. the size of the closed area covered by portion 52 b of slide 52 .
  • slide 52 begins moving in the direction of arrow F 3 , so that oil flows from port 54 to port 56 , and from port 57 to port 55 and into tank 24 maintained at atmospheric pressure (p 0 ) ( FIGS. 3 , 5 ).
  • FIG. 6 shows a third embodiment of the present invention.
  • pressure is regulated in chamber 20 as opposed to chamber 22 .
  • Chamber 22 in fact houses a spring 60 for opposing the force produced in chamber 20 , and is at atmospheric pressure (p 0 ).
  • valve 70 As shown in FIG. 6 , oil is diverted from delivery conduit 26 to a valve 70 which, as before, opens as soon as delivery pressure (p 1 ) exceeds the calibration value (p*) of valve 70 defined by the resistance of a calibration spring 72 a.
  • Valve 70 comprises a cylinder 71 housing a piston 72 stressed elastically by spring 72 a.
  • delivery pressure (p 1 ) exceeds value (p*) (defined by spring 72 a )
  • piston 72 moves to uncover a port 73 in cylinder 71 .
  • Oil therefore flows into a conduit 74 fitted with a dissipating device 75 connected to tank 24 by a conduit 76 .
  • the pressure (p 2 ) of the oil in chamber 20 is therefore lower than delivery pressure (p 1 ), so that a force is produced which is opposed by the reaction force produced by spring 60 in chamber 22 .

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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)
US10/571,704 2003-09-12 2004-09-10 Pumping System Employing a Variable-Displacement Vane Pump Abandoned US20080038117A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
ITBO2003A000528 2003-09-12
IT000528A ITBO20030528A1 (it) 2003-09-12 2003-09-12 Impianto di pompaggio utilizzante una pompa a palette
PCT/EP2004/052140 WO2005026553A1 (fr) 2003-09-12 2004-09-10 Systeme de pompage utilisant une pompe a palettes a cylindree variable

Publications (1)

Publication Number Publication Date
US20080038117A1 true US20080038117A1 (en) 2008-02-14

Family

ID=34308075

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/571,704 Abandoned US20080038117A1 (en) 2003-09-12 2004-09-10 Pumping System Employing a Variable-Displacement Vane Pump

Country Status (4)

Country Link
US (1) US20080038117A1 (fr)
EP (1) EP1680602B1 (fr)
IT (1) ITBO20030528A1 (fr)
WO (1) WO2005026553A1 (fr)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100129239A1 (en) * 2008-11-07 2010-05-27 Gil Hadar Fully submerged integrated electric oil pump
US20100290934A1 (en) * 2009-05-14 2010-11-18 Gil Hadar Integrated Electrical Auxiliary Oil Pump
US20120143470A1 (en) * 2010-12-06 2012-06-07 GM Global Technology Operations LLC Method for operating a variable displacement oil pump
ITTO20111188A1 (it) * 2011-12-22 2013-06-23 Vhit Spa Pompa a cilindrata variabile e metodo di regolazione della sua cilindrata
US20130263815A1 (en) * 2010-11-24 2013-10-10 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US9017041B2 (en) 2010-03-05 2015-04-28 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US9097251B2 (en) 2009-06-16 2015-08-04 Pierburg Pump Technology Gmbh Variable-displacement lubricant pump
US20160047280A1 (en) * 2013-03-18 2016-02-18 Pierburg Pump Technology Gmbh Lubricant vane pump
US20160115832A1 (en) * 2013-05-24 2016-04-28 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US9394891B2 (en) 2011-02-21 2016-07-19 Pierburg Pump Technology Gmbh Variable displacement lubricant pump with a pressure control valve having a preload control arrangement
CN105960531A (zh) * 2013-11-21 2016-09-21 皮尔伯格泵技术有限责任公司 可变排量润滑剂泵
US9726173B2 (en) 2012-11-08 2017-08-08 Pierburg Pump Technology Gmbh Variable displacement lubricant pump for an internal combustion engine with a temperature control valve
US9920757B2 (en) 2013-02-21 2018-03-20 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
JP2018044523A (ja) * 2016-09-16 2018-03-22 日立オートモティブシステムズ株式会社 可変容量ポンプ及び内燃機関の作動油供給システム
US20190338771A1 (en) * 2018-05-02 2019-11-07 GM Global Technology Operations LLC Variable displacement pump
US11268509B2 (en) * 2017-08-03 2022-03-08 Pierburg Pump Technology Gmbh Variable displacement lubricant vane pump
US11415128B2 (en) * 2017-06-22 2022-08-16 Hitachi Astemo, Ltd. Variable displacement pump and control method therefor

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO20060206A1 (it) * 2006-03-23 2007-09-24 Piersburg S P A Dispositivo dissipatore di pressione per un circuito idraulico.
EP2066904B1 (fr) 2006-09-26 2017-03-22 Magna Powertrain Inc. Système et procédé de régulation pour réguler la pression de sortie d'une pompe
WO2010003187A1 (fr) 2008-07-10 2010-01-14 Windfuel Mills Pty Ltd Génération et utilisation d'air à haute pression
EP2253847B1 (fr) 2009-05-18 2019-07-03 Pierburg Pump Technology GmbH Pompe à paillettes à lubrifiant à capacité variable
WO2014094860A1 (fr) * 2012-12-20 2014-06-26 Pierburg Pump Technology Gmbh Pompe à palettes à lubrifiant
EP3207254B1 (fr) * 2014-10-15 2021-04-21 VHIT S.p.A. Système et procédé de commande pour commander une pompe volumétrique

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US4035105A (en) * 1975-04-16 1977-07-12 G. L. Rexroth Gmbh Variable-output pump control arrangement
US4325215A (en) * 1977-03-10 1982-04-20 Teijin Seiki Company Limited Hydraulic apparatus
US4468173A (en) * 1981-05-11 1984-08-28 Mannesmann Rexroth Gmbh Control device for a variable displacement pump
US4496288A (en) * 1981-12-22 1985-01-29 Toyoda Koki Kabushiki Kaisha Vane type pump with a variable capacity for power steering devices
US4509902A (en) * 1982-04-10 1985-04-09 Robert Bosch Gmbh Power regulating device for a hydrostatic pump
US4531898A (en) * 1983-12-13 1985-07-30 Nissan Motor Co., Ltd. Control system for a vane type variable displacement pump
US4780069A (en) * 1984-08-14 1988-10-25 Mannesmann Rexroth Gmbh Directlly actuated vane-type pump
US4702083A (en) * 1984-10-30 1987-10-27 Toyota Jidosha Kabushiki Kaisha Control system and method for controllable output type hydraulic fluid pump of automatic transmission providing decreased pump output in association with the engine starting condition
US4710106A (en) * 1984-11-26 1987-12-01 Nippondenso Co., Ltd. Volume controlling device for variable volume pump
US4711616A (en) * 1984-12-13 1987-12-08 Nippondenso Co., Ltd. Control apparatus for a variable displacement pump
US4737078A (en) * 1985-02-01 1988-04-12 Mannesmann Rexroth Gmbh Control valve for a pump with variable displacement volume
US4697996A (en) * 1985-05-20 1987-10-06 Mannesmann Rexroth Gmbh Rotary pump with adjustable cam ring
US4950137A (en) * 1987-07-30 1990-08-21 Mannesmann Rexroth Gmbh Radial piston machine having pivoted control means engaging cam ring
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US5141418A (en) * 1990-07-25 1992-08-25 Atsugi Unisia Corporation Variable capacity type vane pump with a variable restriction orifice
US5326230A (en) * 1991-10-25 1994-07-05 Mannesmann Rexroth Gmbh Closed loop control circuit for variable hydraulic pump
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Cited By (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8632321B2 (en) 2008-11-07 2014-01-21 Magna Powertrain Inc. Fully submerged integrated electric oil pump
US20100129239A1 (en) * 2008-11-07 2010-05-27 Gil Hadar Fully submerged integrated electric oil pump
US9581158B2 (en) 2008-11-07 2017-02-28 Magna Powertrain Inc. Submersible electric pump having a shaft with spaced apart shoulders
US20100290934A1 (en) * 2009-05-14 2010-11-18 Gil Hadar Integrated Electrical Auxiliary Oil Pump
US8696326B2 (en) 2009-05-14 2014-04-15 Magna Powertrain Inc. Integrated electrical auxiliary oil pump
US9097251B2 (en) 2009-06-16 2015-08-04 Pierburg Pump Technology Gmbh Variable-displacement lubricant pump
US9017041B2 (en) 2010-03-05 2015-04-28 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US20130263815A1 (en) * 2010-11-24 2013-10-10 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US9133738B2 (en) * 2010-11-24 2015-09-15 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US20120143470A1 (en) * 2010-12-06 2012-06-07 GM Global Technology Operations LLC Method for operating a variable displacement oil pump
US9394891B2 (en) 2011-02-21 2016-07-19 Pierburg Pump Technology Gmbh Variable displacement lubricant pump with a pressure control valve having a preload control arrangement
WO2013093711A1 (fr) 2011-12-22 2013-06-27 Vhit S.P.A. Pompe volumétrique rotative et méthode de régulation de son débit volumétrique
ITTO20111188A1 (it) * 2011-12-22 2013-06-23 Vhit Spa Pompa a cilindrata variabile e metodo di regolazione della sua cilindrata
US9726173B2 (en) 2012-11-08 2017-08-08 Pierburg Pump Technology Gmbh Variable displacement lubricant pump for an internal combustion engine with a temperature control valve
US9920757B2 (en) 2013-02-21 2018-03-20 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US9759103B2 (en) * 2013-03-18 2017-09-12 Pierburg Pump Technology Gmbh Lubricant vane pump
US20160047280A1 (en) * 2013-03-18 2016-02-18 Pierburg Pump Technology Gmbh Lubricant vane pump
US20160115832A1 (en) * 2013-05-24 2016-04-28 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
US10024207B2 (en) * 2013-05-24 2018-07-17 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
JP2017500471A (ja) * 2013-11-21 2017-01-05 ピアーブルグ パンプ テクノロジー ゲゼルシャフト ミット ベシュレンクテル ハフツングＰｉｅｒｂｕｒｇ Ｐｕｍｐ Ｔｅｃｈｎｏｌｏｇｙ ＧｍｂＨ 可変容量潤滑剤ポンプ
CN105960531A (zh) * 2013-11-21 2016-09-21 皮尔伯格泵技术有限责任公司 可变排量润滑剂泵
JP2018044523A (ja) * 2016-09-16 2018-03-22 日立オートモティブシステムズ株式会社 可変容量ポンプ及び内燃機関の作動油供給システム
WO2018051673A1 (fr) * 2016-09-16 2018-03-22 日立オートモティブシステムズ株式会社 Pompe à débit variable et système d'alimentation en fluide hydraulique pour moteur à combustion interne
CN109690081A (zh) * 2016-09-16 2019-04-26 日立汽车系统株式会社 可变容量泵以及内燃机的工作油供给系统
US11415128B2 (en) * 2017-06-22 2022-08-16 Hitachi Astemo, Ltd. Variable displacement pump and control method therefor
US11268509B2 (en) * 2017-08-03 2022-03-08 Pierburg Pump Technology Gmbh Variable displacement lubricant vane pump
US20190338771A1 (en) * 2018-05-02 2019-11-07 GM Global Technology Operations LLC Variable displacement pump

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ITBO20030528A1 (it) 2005-03-13
EP1680602B1 (fr) 2015-11-11
WO2005026553A1 (fr) 2005-03-24
EP1680602A1 (fr) 2006-07-19

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