EP1436509B1 - Variable-delivery vane pump - Google Patents

Variable-delivery vane pump Download PDF

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Publication number
EP1436509B1
EP1436509B1 EP20020777077 EP02777077A EP1436509B1 EP 1436509 B1 EP1436509 B1 EP 1436509B1 EP 20020777077 EP20020777077 EP 20020777077 EP 02777077 A EP02777077 A EP 02777077A EP 1436509 B1 EP1436509 B1 EP 1436509B1
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EP
European Patent Office
Prior art keywords
movable ring
zone
projection
ring
guide
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.)
Active
Application number
EP20020777077
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German (de)
French (fr)
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EP1436509A1 (en
Inventor
Clément Kiefer
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 France SARL
Original Assignee
Pierburg Pump Technology France SARL
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 to FR0111825A priority Critical patent/FR2829535B1/en
Priority to FR0111825 priority
Application filed by Pierburg Pump Technology France SARL filed Critical Pierburg Pump Technology France SARL
Priority to PCT/EP2002/010237 priority patent/WO2003023228A1/en
Publication of EP1436509A1 publication Critical patent/EP1436509A1/en
Application granted granted Critical
Publication of EP1436509B1 publication Critical patent/EP1436509B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/18Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
    • F04C14/22Control 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
    • F04C14/223Control 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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00Rotary-piston machines or pumps
    • F04C2/30Rotary-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
    • F04C2/34Rotary-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
    • F04C2/344Rotary-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
    • F04C2/3441Rotary-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

Description

  • The present invention relates to a variable displacement vane pump according to the preamble of the main claim. Such a stern is known from the document US-A-3 771921 .
  • Pallet pumps are commonly used to move various fluids, including water, oil or air for vacuum pumps. These pumps consist mainly of a pump body closed by a cover, forming the stator, and a rotor provided with radial slots in which can slide pallets. Two successive pallets, with the inner wall of the body and the outer wall of the rotor as well as the bottom of the pump body and the cover, form a cell. The suction and discharge of the fluid are through the lower and upper walls formed by the bottom of the pump body and the cover. Near the suction channel, the cells are still small. During rotation of the rotor, the cell grows and fills with fluid. When the cell has reached its maximum size, it is separated from the suction channel and comes into contact with the discharge channel. The volume of the cell begins to decrease to reach its minimum volume thus repressing the fluid it contained.
  • Variation in flow rate or outlet pressure can be achieved in different ways. In a first embodiment, the cavity which is made in the pump body has a doubly eccentric internal section, the rotor rotating in the center of this section. With this embodiment, it is not possible to change the volume so that at a given speed the same pressure or flow rate is obtained.
  • Document is known US 3,771,921A a device that can be used as a pump or generator. This device comprises a housing in which a movable ring can take three positions: a central position, corresponding to a neutral point, and two eccentric positions with respect to the axis of the rotor, on either side of the neutral point. of the means for moving the ring, constituted on the one hand by a spring and on the other hand by a cavity in which one end of the mobile ring penetrates, make it possible to place the mobile ring in the desired position. The cavity is connected to the compressed air line of an external pump. When the external pump is started, the ring is pushed into a first position eccentric by the compressed air contained in the cavity against the effect of the compression spring, and the compressed air passes through the pump which starts to rotate acting then as a generator. If the external pump is stopped, the movable ring is moved by the spring towards the central position where it is blocked if a bar stops the recoil movement of the ring, or to a second eccentric position, symmetrical to the first relative at the neutral point. The axis of the rotor is then coupled to a motor and the pump acts as a simple vane pump without it being possible to act on its displacement. The displacement of the ring makes it possible to modify the function of the device without affecting its displacement.
  • There are vane pumps designed in such a way that it is possible to regulate their displacement to allow an adjustment of the volume of the cells and thus a regulation of the flow and the pressure.
  • These variable displacement pumps operate on the same principle, but a movable ring is interposed between the cavity and the rotor. The movable ring can move in the cavity between a position where it is concentric to the axis of rotation of the rotor (neutral point) and an extreme eccentric position. The further the axes are, the larger the volume of the cells. The ring is held in eccentric position by a return spring whose voltage is adjustable. A piston is placed opposite the spring and tends to push the ring to the neutral position. The piston is fed with the fluid exiting the pump so that the higher the pressure, the more the piston pushes the ring to the neutral position. When the pressure drops, the return spring tends to push the ring towards its eccentric position.
  • Such pumps are known for example from EP 0 398 377 A .
  • These pumps therefore allow self-regulation of the flow rate as a function of the pressure. However, the piston system is a major disadvantage because it requires a corresponding bore, which is expensive.
  • Moreover, the movement of the mobile ring in the housing is not guided, or is done by lateral surfaces located on the edges of the cavity, parallel to the plane of displacement of the mobile ring, on which slide corresponding surfaces of the ring. In addition, the ring is sometimes unbalanced because of the lateral pressure exerted on it in the discharge zone, which can lead to premature wear of the various parts and to a malfunction of the system.
  • Finally, the suction and discharge areas are not isolated, so that it is not possible to achieve the equilibrium of the ring.
  • Document is known GB-A-661,596 a pump in which the oil enters through the inlet centered on the axis of rotation of the hub. The outer face of the ring is therefore subject exclusively to the discharge pressure in the left side of the pump, which tends to unbalance the movable ring.
  • Of the document FR-A-2,764,336 a pump is known in which the part of the outer surface of the ring subjected to the discharge pressure and the part subjected to the suction pressure are identical and particularly reduced. Here too, the ring is unbalanced.
  • The object of the invention is to develop a variable displacement vane pump according to the preamble which allows a better balance of the ring. In addition, the invention also aims to improve the sealing of the suction and discharge areas to ensure a better stability of the ring and achieve equilibrium of the ring.
  • The vane pump according to the invention is defined in claim 1 of
  • In a preferred embodiment of the invention, the control chamber formed by the recess and the projection communicates with the pressure zone of the pressure pump. Thus, the same pressure prevails in the pressure zone of the pump and in the pilot chamber.
  • It is also possible that the pilot pressure applied in the pilot chamber formed by the recess and the projection depends on the pressure prevailing in the area of use of the fluid pumped by the vane pump. This solution makes it possible to take account of the pressure drops between the delivery zone of the pump and the location of the engine where the pumped fluid is actually used.
  • This simple embodiment allows inexpensive industrial implementation. It is thus possible to give up the lateral guide surfaces made on the one hand in the walls of the cavity and on the lateral edges of the ring.
  • In a preferred embodiment, means are provided for connecting the chamber formed by the guide recess and the guide member with the suction zone or the pressure zone of the pump. In the latter case, it will be necessary to size the guide member so that the force exerted on it by the fluid under pressure is less than the force exerted by the piloting pressure on the projection.
  • In order to ensure a better balance of the movable ring in the cavity, the casing and the movable ring are dimensioned so that the component perpendicular to the displacement of the ring of the resultant forces acting on said mobile ring is the weakest possible, without necessarily being zero. The different forces that are exerted on the ring are on the one hand the force of the pressure of the fluid inside the ring and the force of the pressure of the fluid on the outside of the ring and on the other hand the force of the piloting pressure in the pilot chamber and the force of the vanes on the ring as well as the force of the return spring. This balance of the ring is achieved by moving more or less the portion of the projection located on the side of the discharge zone and the corresponding part of its recess and / or the guide wall located on the side of the discharge zone and the corresponding portion of the guide recess towards the discharge zone so that the section of the ring in contact with the discharge zone is more or less important. The section of the ring which is in contact with the discharge zone can thus be more or less reduced depending on the nominal pressure of the pump. Thus, for pumps with high nominal pressure in which the pressure likely to prevail in the discharge zone is very large, the section of the mobile ring subjected to this pressure is lower than for pumps with lower nominal pressure. The mobile ring is thus better balanced and is subjected to less significant efforts.
  • It is preferable that the section of the outer surface of the movable ring that is subjected to the outlet pressure prevailing in the discharge zone is smaller than the section of the outer surface of the movable ring that is subjected to pressure. entering the suction zone. Specifically, it is preferable that the section of the outer surface of the movable ring located in the discharge zone between the side wall of the projection located in the discharge zone and the guide wall located in the discharge zone is less than the section of the outer surface of the movable ring located in the suction zone between the side wall of the projection located in the suction zone and the guide wall located in the suction zone.
  • In a variant of the invention, means are provided to isolate the suction zone and the pressure zone. By isolating the suction and discharge areas, the equilibrium of the ring can be better achieved. This sealing can be provided in particular by the projection and the guide member. By leaving the component perpendicular to the displacement of the ring of the resultant forces acting on the latter slightly greater than zero, it ensures a good seal by pressing the projection and one of the guide walls in their respective recess on the side from the suction or discharge zone. The clearance necessary for the smooth sliding of the protrusion and the guide walls in their respective recess is thus not a cause of leakage. The sealing means may further comprise sealing washers placed between the upper and lower faces of the body cavity and the corresponding upper and lower faces of the hub.
  • The invention will be described in more detail below with the aid of the following figures:
  • Figure 1 :
    Top view of the body of a vane pump according to a first embodiment of the invention;
    Figure 2:
    Cross section according to VV of the vane pump of the figure 1 ;
    Figure 3:
    Perspective view of a movable ring according to the first embodiment;
    Figure 4:
    Top view of the body of a vane pump according to a second embodiment of the invention.
  • The two examples of realization presented below have the same elements which are therefore numbered in the same way.
  • The vane pump consists of a body (1) having a cavity (2) in which a movable ring (3) can move. In the center of the cavity (2) and inside the movable ring (3) is a hub (4) provided with vanes (5) which move in radial slots (6). A lid (7) closes the cavity (2).
  • The volume defined by the inner wall of the movable ring (3) is a circular base cylinder in the examples presented to the figures 1 and 4 . However, the base can also be elliptical for example. This volume is characterized by its center (A). When the center of the ring (A) coincides with the axis of rotation (R) of the hub (4), the pump is in neutral.
  • A return spring (8), whose tension can be adjusted by usual adjusting means, tends to move the ring (3) eccentrically relative to the axis of rotation (R) of the hub (4). A protrusion (9) is formed on the circumference of the ring (3) on the other side with respect to the return spring (8). This projection (9) penetrates into a corresponding recess (10) made in the wall of the cavity (2).
  • The suction channel (11) and the discharge channel (12) may be located either in the bottom of the cavity (2) of the body (1) or in the lid. A supply duct connects the discharge zone (12) and the pilot chamber formed by the recess (10) and the projection (9) so that the same pressure prevails in this chamber as in the discharge zone. .
  • It is also possible to connect the control chamber not with the discharge zone of the pump, but with the engine zone fed by the pump in which the pressure of the fluid to be controlled is prevailing. Thus, the pressure drops between the pump outlet and the motor zone (or any other device powered by the pump) where the fluid must be present at a given pressure are taken into account.
  • The pressure exerted by the fluid in the control chamber and the force of the spring act against each other and define the position of the ring (3) with respect to the axis of rotation of the hub (4) in function the pressure in the discharge zone (12) or the fluid utilization zone. The center of the ring (A) therefore moves in a plane parallel to the axis of rotation (R) of the hub (4).
  • The solution thus retained does not require a bore or corresponding piston, which makes this embodiment much more economical.
  • Furthermore, a guide member is formed on the periphery of the ring (3) on the side of the return spring (8). This guide member is formed mainly of two walls (14, 15) placed on the outer face of the ring (3). These walls are parallel to each other and parallel to the lateral edges of the projection (9), and therefore to the plane of movement of the center (A) of the movable ring (3). These guide walls (14, 15) penetrate inside a corresponding guide recess (16) formed in the cavity (2) of the body (1). The return spring (8) bears on the ring (3) preferably between these two walls (14, 15).
  • These guide walls (14, 15), in cooperation with the guide recess (16) in which they can slide, and the pilot projection (9), in cooperation with the pilot recess (10), constitute guiding elements which ensure a good displacement of the ring during use
  • Adjusting the dimensions of the projection (9) and the pilot recess (10) on the one hand and the guide walls (14, 15) and the guide recess (16) on the other hand ensures a good seal between the suction zone and the discharge zone. In some cases, it may be necessary to complete this isolation by two sealing washers (not shown) placed between the upper face of the hub and the cover for one and between the bottom face of the hub and the bottom of the cavity ( 2) of the body (1) for the second.
  • To ensure a balance of pressures in the guide chamber formed by the walls (14, 15), the periphery of the ring (3) and the recess (16), one of the walls (14, 15), in the example of figures 1 and 3 the wall (14) has a communication opening between the guide chamber and either the suction zone or the discharge zone. It is also possible to provide a channel in the lid or in the bottom of the cavity, a solution retained in the example presented in the figure 4 .
  • It is possible to dig a recess in the projection (9) formed on the circumference of the ring (3) to allow weight and material gain in the ring, as shown in FIG. figure 1 .
  • In order to balance the movable ring (3) and to prevent it being subjected to excessive forces, it is preferable that the section (17) of the outer surface of the movable ring (3) which is subjected to the outlet pressure prevailing in the discharge zone is more or less important depending on the rated power of the pump.
  • For this, it is possible for example, as shown in figure 4 , shifting more or less the portion of the projection (9) located on the discharge zone side and the corresponding part of its recess (10) and / or the guide wall (15) located on the discharge zone side and the corresponding portion of the guide recess (16) to the discharge zone. The point of support of the spring (8) on the movable ring (3) can also be shifted towards the discharge zone. The displacement towards the discharge region of the projection (9) / recess (10) of a part and / or of the guide wall (15) / of the recess (16) is calculated so that the perpendicular component to the displacement of the ring of the resultant of the forces exerted on the latter is as weak as possible. It is possible to leave this component non-zero, to ensure a good seal between the suction zone and the discharge zone. Thus balanced, the ring undergoes less effort and less likely to wear or deform during use at the risk of seeing leakage between the two areas of suction and discharge or see the ring get stuck.
  • The vane pump according to the invention is simpler to achieve than the pump of the state of the art. Moreover, it does not require a piston. It is therefore more economical. Its guide members allow easy movement of the ring. These sealing means make it possible to achieve the equilibrium of the ring. Thanks to the good balance of the mobile ring, the different elements wear out less quickly and the risk of malfunction is reduced.
  • List of references:
  • 1.
    pump body
    2.
    cavity
    3.
    ring
    4.
    hub
    5.
    pallets
    6.
    radial slots
    7.
    lid
    8.
    spring
    9.
    projection
    10.
    driving recess
    11.
    suction area
    12.
    discharge area
    14.
    guide wall
    15.
    guide wall
    16.
    guide recess
    17.
    section of the outer surface of the movable ring in contact with the discharge zone
    AT
    center of the ring
    R
    axis of rotation of the hub

Claims (9)

  1. Variable-volume vane pump, comprising:
    • a body (1) having a cavity (2) in which there can move
    • a movable ring (3) inside which there is situated
    • a hub (4) able to turn about a fixed axis (R) and provide with vanes (5) which, during rotation, bear against the internal face of the movable ring (3),
    • movement means for moving the movable ring (3), according to a control pressure, between a position centred on the rotation axis of the hub (4) and a predefined extreme position off-centre with respect to the rotation axis of the hub (4), said means of moving the movable ring (3) comprising a recess (10) formed in the wall of the cavity (2) of the body (1), and a projection (9) formed on the external face of the movable ring (3) and intended to slide in the recess (10) of the cavity (2) of the body (1) so as to form a control chamber in which the control pressure is applied,
    • a return spring (8) tending to move the movable ring (3) into its off-centre extreme position, said return spring (8) preferably being places on the other side with respect to the recess (10) and the projection (9),
    • a guide member (14, 15, 16) for guiding the movable ring (3) in the cavity (2) of the body (1),
    characterised in that the guide member is formed by two walls (14, 15) placed on the external surface of the movable ring (3) on the other side with respect to the projection (9), parallel to each other and parallel to the lateral edges of the projection (9), these walls (14, 15) being intended to slide in a corresponding recess (16) formed in the wall of the cavity (2) of the body (1), and in that the housing (1) and the movable ring (3) are sized so that the component perpendicular to the movement of the ring (3) of the resultant of the forces exerted on said movable ring (3) is as low as possible, without necessarily being zero, the equilibrium of forces being achieved by shifting, to a greater or lesser extent, the part of the projection (9) situated on the same side as the discharge zone and the corresponding part of its recess (10) and/or the guide wall (15) situated on the same side as the discharge zone and the corresponding part of the guide recess (16) towards the discharge zone, so that the section (17) of the ring in contact with the discharge zone is greater or lesser.
  2. Vane pump according to claim 1, characterised in that the section (17) of the external surface of the movable ring (3) that is subjected to the output pressure prevailing in the discharge zone is smaller than the section of the external surface of the movable ring (3) that is subjected to the inlet pressure prevailing in the suction zone.
  3. Vane pump according to the preceding claim, characterised in that the section (17) of the external surface of the movable ring (3) situated in the discharge zone (12) between the lateral wall of the projection (9) situated in the discharge zone and the guide wall (15) situated in the discharge zone is less than the section of the external surface of the movable ring (3) situated in the suction zone (11) between the lateral wall of the projection (9) situated in the suction zone and the guide wall (14) situated in the suction zone.
  4. Vane pump according to the one of the preceding claims, characterised in that the control chamber formed by the recess (10) and the projection (9) communicates with the pressure zone of the pump.
  5. Vane pump according to one of claims 1 to 3, characterised in that the control pressure applied in the control chamber formed by the recess (10) and the projection (9) depends on the pressure prevailing in the zone where the fluid pumped by the vane pump is used.
  6. Vane pump according to one of the preceding claims, characterised in that means are provided for connecting the chamber formed by the guide recess (16) and the guide member (14, 15) with the suction zone or the pressure zone of the pump.
  7. Vane pump according to one of the preceding claims, characterised in that means are provided for isolating the suction zone and the pressure zone.
  8. Vane pump according to the preceding claim, characterised in that the sealing means comprise the projection (9) and the guide member (14, 125).
  9. Vane pump according to claim 7 or 8, characterised in that the sealing means comprise sealing washers placed between the top and bottom faces of the cavity (2) of the body (1) and the corresponding to and bottom of the hub (4).
EP20020777077 2001-09-12 2002-09-12 Variable-delivery vane pump Active EP1436509B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
FR0111825A FR2829535B1 (en) 2001-09-12 2001-09-12 Variable cylindree pallet pump
FR0111825 2001-09-12
PCT/EP2002/010237 WO2003023228A1 (en) 2001-09-12 2002-09-12 Variable-delivery vane pump

Publications (2)

Publication Number Publication Date
EP1436509A1 EP1436509A1 (en) 2004-07-14
EP1436509B1 true EP1436509B1 (en) 2008-11-26

Family

ID=8867231

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020777077 Active EP1436509B1 (en) 2001-09-12 2002-09-12 Variable-delivery vane pump

Country Status (8)

Country Link
US (1) US7344361B2 (en)
EP (1) EP1436509B1 (en)
JP (1) JP2005502815A (en)
KR (1) KR20040029171A (en)
DE (1) DE60230053D1 (en)
ES (1) ES2318048T3 (en)
FR (1) FR2829535B1 (en)
WO (1) WO2003023228A1 (en)

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DE102014201575A1 (en) 2014-01-29 2015-07-30 Zf Friedrichshafen Ag expander
DE102014201572A1 (en) 2014-01-29 2015-07-30 Robert Bosch Automotive Steering Gmbh expander

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US7491037B2 (en) * 2005-08-05 2009-02-17 Edwards Thomas C Reversible valving system for use in pumps and compressing devices
ITBO20060811A1 (en) 2006-11-29 2008-05-30 Pierburg Spa Oil pump with variable displacement vane.
KR100974592B1 (en) 2008-07-24 2010-08-06 현대자동차주식회사 Variable oil pump
CA2679776A1 (en) * 2008-10-08 2010-04-08 Magna Powertrain Inc. Direct control variable displacement vane pump
US8632321B2 (en) * 2008-11-07 2014-01-21 Magna Powertrain Inc. Fully submerged integrated electric oil pump
EP2404062A4 (en) * 2009-03-05 2014-01-15 Stt Technologies Inc A Joint Venture Of Magna Powertrain Inc And Shw Gmbh Direct control linear variable displacement vane pump
US8696326B2 (en) * 2009-05-14 2014-04-15 Magna Powertrain Inc. Integrated electrical auxiliary oil pump
EP2351934A1 (en) 2010-01-11 2011-08-03 Pierburg Pump Technology GmbH Variable-displacement lubricant pump
DE102012204424A1 (en) * 2012-03-20 2013-09-26 Robert Bosch Gmbh A vane pump with a housing, a sliding stator, and a rotatable within the stator rotor
US10253772B2 (en) 2016-05-12 2019-04-09 Stackpole International Engineered Products, Ltd. Pump with control system including a control system for directing delivery of pressurized lubricant
KR20180000740U (en) 2016-09-05 2018-03-14 유효상 CASEMENT hinge
US20190293069A1 (en) * 2016-10-12 2019-09-26 Pierburg Pump Technology Gmbh Automotive variable mechanical lubricant pump
US10167752B2 (en) 2017-02-10 2019-01-01 GM Global Technology Operations LLC Engine oil pump with electronic oil pressure control

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014201575A1 (en) 2014-01-29 2015-07-30 Zf Friedrichshafen Ag expander
DE102014201572A1 (en) 2014-01-29 2015-07-30 Robert Bosch Automotive Steering Gmbh expander
WO2015113691A1 (en) 2014-01-29 2015-08-06 Zf Friedrichshafen Ag Expansion machine

Also Published As

Publication number Publication date
EP1436509A1 (en) 2004-07-14
DE60230053D1 (en) 2009-01-08
WO2003023228A1 (en) 2003-03-20
FR2829535B1 (en) 2005-08-12
ES2318048T3 (en) 2009-05-01
JP2005502815A (en) 2005-01-27
US7344361B2 (en) 2008-03-18
US20040247463A1 (en) 2004-12-09
KR20040029171A (en) 2004-04-03
FR2829535A1 (en) 2003-03-14

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