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WO2005026553A1 - Systeme de pompage utilisant une pompe a palettes a cylindree variable - Google Patents

Systeme de pompage utilisant une pompe a palettes a cylindree variable Download PDF

Info

Publication number
WO2005026553A1
WO2005026553A1 PCT/EP2004/052140 EP2004052140W WO2005026553A1 WO 2005026553 A1 WO2005026553 A1 WO 2005026553A1 EP 2004052140 W EP2004052140 W EP 2004052140W WO 2005026553 A1 WO2005026553 A1 WO 2005026553A1
Authority
WO
WIPO (PCT)
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.)
Ceased
Application number
PCT/EP2004/052140
Other languages
English (en)
Inventor
Giacomo Armenio
Clément 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
Priority to US10/571,704 priority Critical patent/US20080038117A1/en
Priority to EP04787130.6A priority patent/EP1680602B1/fr
Publication of WO2005026553A1 publication Critical patent/WO2005026553A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • 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.
  • various fluids such as oil in an internal combustion engine.
  • the gaps between adjacent vanes on the pump fail to fill completely, thus resulting in forces impairing operation of the pump.
  • counteracting springs are traditionally used, but are extremely rigid and therefore do not deform easily.
  • DISCLOSURE OF INVENTION It is therefore an object of the present invention to provide for hydraulic control of a variable-delivery vane pump, particularly at high speed. According to the present invention, there is provided a pumping system employing a variable- displacement vane pump, as claimed in Claim 1.
  • Figure 1 shows a first embodiment of the present invention
  • Figure 2 shows a first configuration of a second embodiment
  • Figure 3 shows a second configuration of the second embodiment in Figure 2
  • Figure 4 shows a first configuration of a detail of the second embodiment in Figures 2 and 3
  • Figure 5 shows a second configuration of the Figure 4 detail
  • Figure 6 shows a third embodiment of the present invention.
  • BEST MODE FOR CARRYING OUT THE INVENTION Number 10 in Figure 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 (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 PI which is fixed at all times; and ring 13 has a centre P2.
  • the distance P1P2 represents the eccentricity E of pump 10.
  • 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 P2 of ring 13, and have respective front surfaces Al and A2 facing chambers 20 and 22 respectively. For reasons explained in detail later on, surface A2 is larger than surface Al . More specifically, tests and calculations have shown surface A2 must be 1.4 to 1.7 times larger than surface Al .
  • a spring 22a inside chamber 22 exerts a small force on surface A2 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. As shown in Figure 1, 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.
  • valve 30 comprises a cylinder 31 housing a piston 32. More specifically, as shown in Figure 1, piston 32 comprises a first portion 32a and a second portion 32b connected to each other by a rod 32c. Portions 32a and 32b are equal in cross section to cylinder 31, whereas rod 32c is smaller in cross section than cylinder 31. Cylinder 31 has a port 33 connected hydraulically to chamber 22 by a conduit 34.
  • Conduit 28b substantially provides for picking up a delivery pressure signal in conduit 28, so as to act on the front surface A3 of portion 32a of piston 32.
  • the dash line in Figure 1 shows the situation in which port 33 is closed by second portion 32b.
  • the delivery pressure (pi) increases alongside an increase in the operating speed of pump 10
  • greater force is exerted on surface A3 and, on reaching the preload value of a spring 36, moves piston 32 to allow oil flow from conduit 34 through port 33 and along a conduit 35 into tank 24.
  • 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 (pi) on surface A3 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.
  • piston 32 moves into the configuration shown by the continuous line in Figure 1, in which rod 32c 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 28a and through dissipating device 29, so that, as opposed to the delivery pressure (pi) , a lower pressure (p2) is present in chamber 22.
  • the pressure (p2) in chamber 22 is lower than the pressure (pi) in chamber 20, thus disassociating the two pressures to enable ring 13 to move in the direction indicated by arrow FI to establish a balanced eccentricity E value producing the desired oil flow to user deice UT.
  • piston 32 begins moving so that part of the oil leaks through port 33.
  • valve 30 also acts as a pressure dissipating device to assist in creating the desired pressure (p2) in chamber 22.
  • (pi) and (p*) are equal at the end of the transient state The system has also proved stable. That is, adjustment continues for as long as permitted by piston 32, i.e.
  • valve 30 is regulated solely by delivery pressure (pi) and totally unaffected by undesired internal forces.
  • delivery pressure (pi) increases, it remains constant for a while, and then decreases.
  • pressure (pi) remains constant, even at extremely high rotation speeds of rotor 14.
  • pressure value (p*) substantially determined by the characteristics of spring 36, generation of pressure (p2) commences, and ring 13 begins moving in the direction of arrow FI to reduce eccentricity E and therefore the displacement of pump 10.
  • valve 30 opens, and oil flows along conduit 34, through port 33, and along conduit 35 to tank 24, so that the pressure (p2) in chamber 22 is lower than (pi) , and ring 13 moves in the direction of arrow Fl 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 52a, a second portion 52b, and a third portion 52c.
  • Portions 52a and 52b are connected by a rod 52d
  • portions 52b and 52c are connected by a rod 52e.
  • 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 (pi) .
  • the value of ⁇ l which represents the size of port 56, must be greater than ⁇ 2, i.e. the size of the closed area covered by portion 52b of slide 52 .
  • delivery pressure pi
  • FIG. 6 shows a third embodiment of the present invention. Unlike the two embodiments described above, in this case, 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 (pO) . As shown in Figure 6, oil is diverted from delivery conduit 26 to a valve 70 which, as before, opens as soon as delivery pressure (pi) exceeds the calibration value (p*) of valve 70 defined by the resistance of a calibration spring 72a.
  • Valve 70 comprises a cylinder 71 housing a piston 72 stressed elastically by spring 72a.
  • delivery pressure (pi) exceeds value (p*) (defined by spring 72a)
  • 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 (p2) of the oil in chamber 20 is therefore lower than delivery pressure (pi) , so that a force is produced which is opposed by the reaction force produced by spring 60 in chamber 22.
  • the mechanism by which equilibrium is established in vane pump 10 is the same as described for the other two embodiments .

Landscapes

  • 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 concerne un système de pompage (100) comprenant une pompe à palettes à débit variable (10). Cette pompe (10) comprend des dispositifs de régulation et de dissipation de la pression hydraulique (29 et 30) permettant de conférer à l'huile contenue dans une chambre de régulation (22) une pression (p2) inférieure à la pression de refoulement (p1).
PCT/EP2004/052140 2003-09-12 2004-09-10 Systeme de pompage utilisant une pompe a palettes a cylindree variable Ceased WO2005026553A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US10/571,704 US20080038117A1 (en) 2003-09-12 2004-09-10 Pumping System Employing a Variable-Displacement Vane Pump
EP04787130.6A EP1680602B1 (fr) 2003-09-12 2004-09-10 Système de pompage utilisant une pompe à palettes à cylindrée variable

Applications Claiming Priority (2)

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

Publications (1)

Publication Number Publication Date
WO2005026553A1 true WO2005026553A1 (fr) 2005-03-24

Family

ID=34308075

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/052140 Ceased WO2005026553A1 (fr) 2003-09-12 2004-09-10 Systeme de pompage utilisant une pompe a palettes a cylindree variable

Country Status (4)

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

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007122463A3 (fr) * 2006-03-23 2008-02-07 Pierburg Spa Dispositif dissipateur de pression pour circuit hydraulique
EP2253847A1 (fr) 2009-05-18 2010-11-24 Pierburg Pump Technology GmbH Pompe à ailettes à lubrifiant à capacité variable
EP2264318A1 (fr) 2009-06-16 2010-12-22 Pierburg Pump Technology GmbH Pompe lubrifiante à déplacement variable
WO2011107156A1 (fr) 2010-03-05 2011-09-09 Pierburg Pump Technology Gmbh Pompe à lubrifiant à débit variable
WO2012069083A1 (fr) 2010-11-24 2012-05-31 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable
US8202061B2 (en) 2006-09-26 2012-06-19 Magna Powertrain Inc. Control system and method for pump output pressure control
WO2012113437A1 (fr) 2011-02-21 2012-08-30 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable avec soupape de régulation de pression munie d'un dispositif de commande de précharge
WO2014071976A1 (fr) 2012-11-08 2014-05-15 Pierburg Pump Technology Gmbh Pompe à lubrifiant à déplacement variable
EP2318715A4 (fr) * 2008-07-10 2014-06-11 Windfuel Mills Pty Ltd Génération et utilisation d'air à haute pression
EP2770209A1 (fr) 2013-02-21 2014-08-27 Pierburg Pump Technology GmbH Pompe lubrifiante à cylindrée variable
WO2015074700A1 (fr) * 2013-11-21 2015-05-28 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable
US20150330388A1 (en) * 2012-12-20 2015-11-19 Pierburg Pump Technology Gmbh Lubricant vane pump
CN105264230A (zh) * 2013-05-24 2016-01-20 皮尔伯格泵技术有限责任公司 可变排量润滑油泵
WO2016059490A1 (fr) * 2014-10-15 2016-04-21 Vhit S.P.A. Système et procédé de commande pour commander une pompe volumétrique

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JP5615826B2 (ja) * 2008-11-07 2014-10-29 エスティーティー テクノロジーズ インコーポレイテッド ア ジョイント ヴェンチャー オブ マグナ パワートレイン インコーポレイテッド アンド エスエイチダブリュ ゲゼルシャフト ミット ベシュレンクテル ハフツング 完全サブマージド一体形電気オイルポンプ
US8696326B2 (en) * 2009-05-14 2014-04-15 Magna Powertrain Inc. Integrated electrical auxiliary oil pump
GB2486195A (en) * 2010-12-06 2012-06-13 Gm Global Tech Operations Inc Method of Operating an I.C. Engine Variable Displacement Oil Pump by Measurement of Metal Temperature
ITTO20111188A1 (it) 2011-12-22 2013-06-23 Vhit Spa Pompa a cilindrata variabile e metodo di regolazione della sua cilindrata
WO2014146675A1 (fr) * 2013-03-18 2014-09-25 Pierburg Pump Technology Gmbh Pompe de graissage à palettes
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
JP6715216B2 (ja) * 2017-06-22 2020-07-01 日立オートモティブシステムズ株式会社 可変容量形ポンプ及びその制御方法
WO2019024997A1 (fr) * 2017-08-03 2019-02-07 Pierburg Pump Technology Gmbh Pompe à palettes et à débit variable de lubrification
US20190338771A1 (en) * 2018-05-02 2019-11-07 GM Global Technology Operations LLC Variable displacement pump

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EP1043504A2 (fr) * 1999-04-08 2000-10-11 Bayerische Motoren Werke Aktiengesellschaft Pompe à palettes à déplacement variable
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WO2002052155A1 (fr) * 2000-12-04 2002-07-04 Toyoda Koki Kabushiki Kaisha Pompe volumetrique a palettes

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FR2195271A1 (fr) * 1972-08-04 1974-03-01 Peugeot & Renault
DE3214212A1 (de) * 1982-04-17 1983-10-20 Alfred Teves Gmbh, 6000 Frankfurt Druckregelvorrichtung fuer pumpen, insbesondere fluegelzellenpumpen
GB2151705A (en) * 1983-12-24 1985-07-24 Teves Gmbh Alfred Variable-delivery sliding-vane rotary 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
EP1043504A2 (fr) * 1999-04-08 2000-10-11 Bayerische Motoren Werke Aktiengesellschaft Pompe à palettes à déplacement variable
WO2002052155A1 (fr) * 2000-12-04 2002-07-04 Toyoda Koki Kabushiki Kaisha Pompe volumetrique a palettes
US20020085923A1 (en) * 2000-12-15 2002-07-04 Unisia Jkc Steering Systems Co, Ltd. Variable displacement pump

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007122463A3 (fr) * 2006-03-23 2008-02-07 Pierburg Spa Dispositif dissipateur de pression pour circuit hydraulique
US8202061B2 (en) 2006-09-26 2012-06-19 Magna Powertrain Inc. Control system and method for pump output pressure control
US9091269B2 (en) 2008-07-10 2015-07-28 Windfuel Mills Pty Ltd Generation and use of high pressure air
EP2318715A4 (fr) * 2008-07-10 2014-06-11 Windfuel Mills Pty Ltd Génération et utilisation d'air à haute pression
EP2253847A1 (fr) 2009-05-18 2010-11-24 Pierburg Pump Technology GmbH Pompe à ailettes à lubrifiant à capacité variable
EP2264318A1 (fr) 2009-06-16 2010-12-22 Pierburg Pump Technology GmbH Pompe lubrifiante à déplacement variable
WO2010146087A2 (fr) 2009-06-16 2010-12-23 Pierburg Pump Technology Gmbh Pompe à lubrifiant à déplacement variable
WO2010146087A3 (fr) * 2009-06-16 2011-09-15 Pierburg Pump Technology Gmbh Pompe à lubrifiant à déplacement variable
CN102459903A (zh) * 2009-06-16 2012-05-16 皮尔伯格泵技术有限责任公司 可变排量润滑剂泵
US9097251B2 (en) 2009-06-16 2015-08-04 Pierburg Pump Technology Gmbh Variable-displacement lubricant pump
CN102459903B (zh) * 2009-06-16 2015-05-06 皮尔伯格泵技术有限责任公司 可变排量润滑剂泵
CN102844570A (zh) * 2010-03-05 2012-12-26 皮尔伯格泵技术有限责任公司 可变排量的润滑泵
JP2013521436A (ja) * 2010-03-05 2013-06-10 ピールブルグ 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 可変容量形潤滑剤ポンプ
CN102844570B (zh) * 2010-03-05 2016-01-20 皮尔伯格泵技术有限责任公司 可变排量的润滑泵
WO2011107156A1 (fr) 2010-03-05 2011-09-09 Pierburg Pump Technology Gmbh Pompe à lubrifiant à débit variable
US9017041B2 (en) 2010-03-05 2015-04-28 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
CN103228917A (zh) * 2010-11-24 2013-07-31 皮尔伯格泵技术有限责任公司 可变排量的润滑剂泵
CN103228917B (zh) * 2010-11-24 2016-01-13 皮尔伯格泵技术有限责任公司 可变排量的润滑剂泵
US9133738B2 (en) 2010-11-24 2015-09-15 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
WO2012069083A1 (fr) 2010-11-24 2012-05-31 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable
CN103380300B (zh) * 2011-02-21 2016-01-13 皮尔伯格泵技术有限责任公司 包括具有预载控制装置的压力控制阀的可变排量润滑剂泵
JP2014506655A (ja) * 2011-02-21 2014-03-17 ピールブルグ 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 予圧制御装置を有する圧力制御弁を備える可変容量形潤滑油ポンプ
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
WO2012113437A1 (fr) 2011-02-21 2012-08-30 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable avec soupape de régulation de pression munie d'un dispositif de commande de précharge
CN103380300A (zh) * 2011-02-21 2013-10-30 皮尔伯格泵技术有限责任公司 包括具有预载控制装置的压力控制阀的可变排量润滑剂泵
WO2014071976A1 (fr) 2012-11-08 2014-05-15 Pierburg Pump Technology Gmbh Pompe à lubrifiant à déplacement variable
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
US20150330388A1 (en) * 2012-12-20 2015-11-19 Pierburg Pump Technology Gmbh Lubricant vane pump
US9909584B2 (en) * 2012-12-20 2018-03-06 Pierburg Pump Technology Gmbh Lubricant vane pump
EP2770209A1 (fr) 2013-02-21 2014-08-27 Pierburg Pump Technology GmbH Pompe lubrifiante à cylindrée variable
WO2014128006A1 (fr) 2013-02-21 2014-08-28 Pierburg Pump Technology Gmbh Pompe à lubrifiant à déplacement variable
US9920757B2 (en) 2013-02-21 2018-03-20 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
CN105264230A (zh) * 2013-05-24 2016-01-20 皮尔伯格泵技术有限责任公司 可变排量润滑油泵
US10024207B2 (en) 2013-05-24 2018-07-17 Pierburg Pump Technology Gmbh Variable displacement lubricant pump
WO2015074700A1 (fr) * 2013-11-21 2015-05-28 Pierburg Pump Technology Gmbh Pompe à lubrifiant à cylindrée variable
WO2016059490A1 (fr) * 2014-10-15 2016-04-21 Vhit S.P.A. Système et procédé de commande pour commander une pompe volumétrique

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ITBO20030528A1 (it) 2005-03-13
EP1680602B1 (fr) 2015-11-11
US20080038117A1 (en) 2008-02-14
EP1680602A1 (fr) 2006-07-19

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