EP1320681B1 - Vane pump - Google Patents

Vane pump Download PDF

Info

Publication number
EP1320681B1
EP1320681B1 EP01975550A EP01975550A EP1320681B1 EP 1320681 B1 EP1320681 B1 EP 1320681B1 EP 01975550 A EP01975550 A EP 01975550A EP 01975550 A EP01975550 A EP 01975550A EP 1320681 B1 EP1320681 B1 EP 1320681B1
Authority
EP
European Patent Office
Prior art keywords
vane
arc segment
pump
pumping cavity
rotor member
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.)
Expired - Lifetime
Application number
EP01975550A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1320681A2 (en
Inventor
William Dalton
Kurt G. Grochowski
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.)
Goodrich Pump and Engine Control Systems Inc
Original Assignee
Goodrich Pump and Engine Control Systems 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
Application filed by Goodrich Pump and Engine Control Systems Inc filed Critical Goodrich Pump and Engine Control Systems Inc
Publication of EP1320681A2 publication Critical patent/EP1320681A2/en
Application granted granted Critical
Publication of EP1320681B1 publication Critical patent/EP1320681B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • F04C14/28—Safety arrangements; Monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • 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

Definitions

  • the subject invention relates to fuel pumps for gas turbine engines, and more particularly, to variable displacement vane pumps which are used in applications that require high reliability and a predicted failure mode.
  • variable displacement vane pumps are being developed within the aerospace industry as an alternative to traditional fixed displacement gear pumps.
  • An example of a variable displacement vane pump is disclosed in U.S. Patent No. 5,545,014 to Sundberg et al., the disclosure of which is herein incorporated by reference in its entirety to the extent that it does not conflict with the present disclosure.
  • Vane pumps traditionally include, among other things, a housing, a cam member and a rotor supported within the housing by axially opposed journal bearings.
  • the housing defines an interior chamber, a fluid inlet and a fluid outlet and the cam member and rotor are disposed within the interior chamber.
  • the cam member has a central bore which defines the circumferential boundary of the internal pumping chamber.
  • Mounted for rotational movement within the central bore of the cam member is a rotor supported by axial opposed journal bearings.
  • the rotor element has circumferentially spaced apart slots machined therein which support corresponding radially movable vane elements.
  • Variable displacement vane pumps differ from other vane pumps, such as fixed displacement vane pumps, in that the cam member pivots about a fulcrum aligned with the vertical centerline of the pump, thereby adjusting its position with respect to the rotor. This adjustment allows the relative volumes of the inlet and discharge buckets to be changed and thereby vary the displacement capacity of the pump.
  • the vanes of the rotor element of the pump traverse at least four distinct arcuate regions which make up the 360 degree revolution.
  • the first region is the inlet arc segment in which fluid is received into the pumping chamber and over this region the bucket volume increases.
  • the second region is the discharge arc segment in which pressurized fluid is discharged from the pumping chamber and over this region the bucket volume decrease.
  • seal arc segments separate the inlet and discharge arc segments and represent the regions through which the bucket volume remains substantially constant.
  • fluid at a first pressure is fed into the pumping chamber through the housing inlet, and into the space defined between adj acent vane elements, known as the bucket.
  • the configuration of the cam member causes the vanes to retract within the corresponding slots. This causes the volume defined by the bucket to decrease. Since the amount of fluid received into an inlet bucket is greater than that contained within the corresponding discharge bucket, a fluid volume equivalent in size to the volumetric difference is discharged or displaced through the outlet port at a pressure equal to the downstream pressure which must be overcome.
  • pumping pressures and velocities are so high within the pump housing that the use of heavy, high wear resistant materials such as tungsten carbide for the cam member and the vane elements becomes necessary to handle the wear which is caused by these high levels of pressure and velocity.
  • U.S. Patent No. 5,545,014 to Sundberg et al. and U.S. Patent No. 5,833,438 to Sundberg discloses a durable, single action, variable displacement vane pump capable of undervane pumping and a pressure balancing method.
  • U.S. Patent No. 5,833,438 to Sundberg teaches a variable displacement vane pump having a durable rotor member with journal ends at each side of a large diameter central vane section and a mechanism for confining the high pressure within the cam member and thereby preventing axial pressure leakage along the length of the rotor member.
  • the disclosure contained within these patent is hereby incorporated by reference in their entirety to the extent it does not conflict with the present disclosure.
  • a vane pump according to the preamble of claim 1 is known from US-A-5 545 014.
  • variable displacement pumps over conventional vane pumps, namely fixed displacement gear pumps, is that they solve the problem where excess heat generation becomes a crucial impediment to pump performance. Also, a variable displacement vane pump can be used to eliminate certain fuel flow metering components by utilizing the pump as the metering device.
  • variable displacement vane pump One of the disadvantages associated with variable displacement vane pump technology is the inability to predict the failure mode. As a result, there is a reluctance to implement this technology in applications, such as high performance aircraft, that require high reliability and a predicted failure mode.
  • the failure mechanism With a conventional fixed displacement gear pump, the failure mechanism is well known. Typically as the pump degrades, the performance drops off far enough so that one cannot start the engine, thus a safe failure occurs.
  • variable displacement vane pump With a variable displacement vane pump, however, as the vanes wear away due to contact with the cam surface, the cantilevered load that the pressure puts on each vane can become so high that a catastrophic failure of a vane can occur during pump operation and effectively destroys the whole pumping system without warning. In an applications such as helicopter fuel systems, this type of failure can cause damage to the control system and engine and result in the loss of life. In order to prevent such an occurrence, the variable displacement vane pump must be inspected and maintained frequently.
  • variable displacement vane pumps for use with gas turbine engines which include a mechanism for predicting the failure mode of the pump thereby preventing an operational failure.
  • the vane pump includes a pump housing, a cam member, a rotor member and a mechanism for communicating a high pressure fluid from the discharge arc region to the inlet arc region so as to prevent pump start-up when a predetermined wear state has been reached.
  • the pump housing typically includes a cylindrical interior chamber which defines a central axis through which a vertical centerline and a horizontal centerline extend.
  • the cam member is mounted for pivotable movement within the interior chamber of the pump housing about a fulcrum aligned with the vertical centerline of the interior chamber.
  • the cam member has a bore extending therethrough which defines a circumferential surface of a pumping cavity.
  • the circumferential surface of the pumping cavity includes a discharge arc segment, an inlet arc segment and seal arc segments separating the inlet arc segment and the discharge arc segments from one another.
  • the cylindrical rotor member is mounted for rotational movement within the bore of the cam member about the central axis of the interior chamber.
  • the rotor member has a central body portion with first and second axially opposed end surfaces and a plurality of circumferentially spaced apart radially extending vane slots formed therein.
  • Each vane slot supports a corresponding vane element mounted for radial movement therein.
  • Each of the vane elements have a radially outer tip surface which is adapted for slideably engaging the circumferential surface of the pumping cavity and a radially inner undervane portion which is positioned within each vane slot.
  • the mechanism for communicating a high pressure fluid from the discharge arc region to the inlet arc region so as to prevent pump start-up activates when the tip surface of each vane element has worn a predetermined amounted with respect to the undervane portion of each vane element.
  • the mechanism for communicating a high pressure fluid from the discharge arc region to the inlet arc region when the tip surface of each vane element has worn a predetermined amount includes arcuate channels formed in the first end surface of the body portion of the rotor member.
  • the arcuate channels each extend between each vane slot. It is envisioned that the arcuate channels are spaced from the central axis by a radial distance and the radial distance defines the predetermined amount of wear.
  • the means for communicating a high pressure fluid from the discharge arc region to the inlet arc region when the tip surface of each vane element has worn a predetermined amount includes arcuate channels formed in the second end surface of the body portion of the rotor member
  • the predetermined amount of wear is reached when the undervane portion of each vane element at a point in the pumping cavity is positioned radially outward of the arcuate channels formed in the body portion of the rotor. As a result of this relative positioning, fluid is allowed to communicate from the discharge arc segment to the inlet arc segment of the pumping cavity.
  • the circumferential surface of the pump cavity includes a discharge arc segment of about 150 degrees, a first seal arc segment of about 30 degrees, an inlet arc segment of about 150 degrees and a second seal arc segment of about 30 degrees.
  • first and second axially spaced apart end plates are disposed within the interior chamber of the pump housing.
  • Each end plate has a first surface which is adjacent to the rotor member and forms an axial end portion of the pumping cavity.
  • Each end plate is spaced from the rotor member so as to allow frictionless rotation of the rotor member within the pumping cavity.
  • the end plates include a mechanism associated with the first surface of each end plate for communicating fluid from the discharge arc segment of the pumping cavity to the undervane portion of each vane element when each vane element passes through the discharge and seal arc segments.
  • each end plate includes a mechanism for communicating fluid from the inlet arc region of the pumping cavity to the undervane portion of each vane element when each vane element passes through the inlet arc segment as the rotor member rotates about the central axis.
  • the rotor member further includes a plurality of substantially axial fluid passages formed in the central body portion of the rotor. Each passage is positioned between the plurality of circumferentially spaced apart radial vane slots and provides a path through the rotor body portion for fluid to communicate axially from the pumping cavity to the first and second end plate.
  • the subject application is also directed to a vane pump which includes, among other things, a pump housing a cam member, a rotor member.
  • the rotor member being substantially cylindrical and mounted for rotational movement within the bore of the cam member about the central axis of the interior chamber.
  • the rotor member includes a central body portion with first and second axially opposed end surfaces and a plurality of circumferentially spaced apart radially extending vane slots formed therein.
  • each vane slot supports a corresponding vane element mounted for radial movement therein.
  • Each vane element has a radially outer tip surface adapted for slideably engaging the circumferential surface of the pumping cavity and a radially inner undervane portion within each vane slot.
  • the first end surface of the body portion has arcuate channels formed therein which extend between each vane slot. The arcuate channels providing a path for high pressure fluid to leak from the discharge arc segment to the inlet arc segment of the pumping cavity when each vane tip surface has worn such that the undervane portion is positioned radially outward of the arcuate channels.
  • the arcuate channels are spaced from the central axis by a radial distance whereby the radial distance defines an amount of allowable vane tip surface wear which can occur before high pressure fluid can leak from the discharge arc segment to the inlet arc segment of the pumping cavity.
  • the present application concerns a variable displacement vane pump which includes a pump housing, a cam member, a rotor member, a leak path, first and second axially spaced apart end plates.
  • the leak path communicates fluid from the discharge arc region to the inlet arc region when the cam member is in a start-up position and each undervane portion is positioned radially outward of the leak path.
  • the leak path includes arcuate channels formed in the first end surface of the body portion of the rotor member which extend between each vane slot.
  • Vane pump 10 includes a pump housing 12 defining an interior chamber which supports a cam member 14 and a rotor member 16.
  • Rotor member 16 includes a plurality of radially extending slots 17. Each slot is configured to support a corresponding vane element 18.
  • Cam member 14 is mounted for pivotal movement within pump housing 12 about a pivot pin 20 that defines a fulcrum, so as to vary the displacement of vane pump 10.
  • Cam member 14 includes a one-piece body that defines a bore 22 forming a cam chamber.
  • the circular bore 22 defines a smooth continuous circumferential surface 24 of the pumping cavity, making continuous contact with the outer tip surfaces 21 of each vane element 18.
  • a lever 25 extends from the body of cam member 14 and is pivotably connected to actuation piston assembly 15, for varying the position of the cam member 14 relative to the rotor member 16.
  • each vane element 18 fits snugly within a corresponding slot 17 and functions like a piston as it is depressed radially inwardly during movement of the rotor member 16 through the high pressure discharge arc region 62 (Fig. 3) of the pumping chamber.
  • Each slot 17 has a radially inner undervane cavity 19 defining an area that is open to low inlet pressure when the vane element 18 is in the inlet arc region 60 ( Fig. 3) of the pumping chamber, and to high discharge pressure when the vane element 18 is in the discharge arc region 62 of the pumping chamber and the seal arc regions 64a and 64b (Fig. 3) of the pumping chamber.
  • the manner in which pressurized fluid is communicated to the undervane cavity will be described in more detail herein below with respect to Fig. 3.
  • vane pump 10 further includes an inlet region 50 for admitting low pressure fluid into the pumping chamber and a discharge region 52 for discharging high pressure fluid from the pumping chamber.
  • a main drive shaft 32 extends through the interior chamber of pump housing 12 along the longitudinal axis thereof for driving a central shaft member 34.
  • Shaft member 34 is supported for rotation by opposed journal bearings 36a and 36b, and is keyed to rotor member 16 for imparting rotational motion thereto.
  • Opposed sideplates 40 and 42 which are disposed within the interior chamber, form a sealed cavity between cam member 14 and rotor member 16, and provide inlet and discharge ports for the cavity.
  • Axial spacer 30 is supported within the housing 12, between sideplates 40 and 42, and has a thickness that is slightly greater than the thickness of cam member 14. This allows the sideplates 40 and 42 to be tightly clamped against the spacer 30 by a plurality of threaded fasteners (not shown) while allowing small gaps to remain between the cam member 14 and the sideplates to reduce or eliminate friction therebetween.
  • the 360 degree pumping chamber includes an inlet arc region 60, a discharge arc region 62 and sealing arc regions 64a and 64b positioned between the inlet and discharge arc regions 60 and 62.
  • the inlet arc region 60 represents the portion of the pumping chamber in which the volume contained between adjacent vane elements (i.e., within the buckets) increases and low pressure fluid is received into the pumping chamber.
  • the discharge arc region 62 is the portion of the pumping chamber in which the volume contained between adjacent vane elements decreases. In the seal arc regions 64a and 64b, the volume remains substantially constant.
  • each vane element 18 When the rotor 16 rotates within the pumping chamber, the centrifugal force created thereby imparts a radially outward force on each vane elements 18. In addition, the pressurized fluid contained within adjacent buckets imparts a radially inward force on each adjacent vane element 18. Often, the opposed forces which are applied to each vane element 18 are not balanced. As a result, the vane tip 21 of each vane 18 is either subjected to excessive wear due to a net radially outward force or fluid leaks from within the bucket due to a net radially inward force. This reduces pumping efficiency.
  • An ideal pump operating condition occurs when the pressure applied to the vane elements is balanced and the vane elements "float" within the slots defined in the rotor. This condition results in minimum wear to the vane tips and minimizes the pressure losses caused by the lack of contact between the vane tips and the cam member.
  • Pump 10 is adapted and configured to correct the unbalanced vane condition by applying pressure to the undervane portion 23 of each vane element 18. More specifically, low pressure from within each bucket traversing the inlet region 60 is supplied to the undervane portion 23 of vane elements 18 within the inlet arc region 60. Similarly, the undervane portion 23 of the vanes traversing the discharge arc region 62 and the seal arc regions 64a and 64b are supplied with high pressure from the buckets located in the discharge arc region 62.
  • the pressure in the form of pressurized fluid, is supplied from the inlet arc region 60 and discharge arc region 62 to the undervane portion 23 of each vane element 18 by way of flow ports machined in the rotor body portion and by providing end plates which have flow channels formed therein.
  • the body portion 19 of rotor 16 includes a plurality of flow ports 84 formed therein.
  • Each flow port 84 is positioned between the plurality of circumferentially spaced apart radial vane slots 17 and provides a path for fluid to flow from the pumping cavity to channels 66i and 66d ( seeFig 3) formed in end plate 40, or in both end plate 40 and 42.
  • Each flow port 84 is substantially T-shaped and includes a radial conduit 85 and an axial conduit 86.
  • This feature is advantageous because fluid must travel radially inward from the bucket into each flow port 84, against the centrifugal force created by the rotation, so that the fluid is effectively filtered prior to entering each flow port 84. Moreover, particulate contained within the fluid in the pumping chamber is forced radially outward by the centrifugal motion, leaving particulate free fluid on the radially inner portion of the bucket.
  • arcuate outer channels 66i and 66d are formed in face 44 of endplate 40 and are in fluid communication with the inlet and discharge arc regions, 60 and 62, respectively by way of flow ports 84 of rotor member 16.
  • Low pressure fluid from the inlet arc region 60 is received into arcuate outer channel 66i and then flows radially inward through passages 68a-e to arcuate inner channel 69i.
  • the passages 68a-e and the inner channel 69i are also formed in face 44 of side plate 40.
  • Inner channel 69i communicates with the undervane portion of each vane element 18 positioned within the inlet arc region 60.
  • variable displacement vane pump technology is the inability to predict the failure mode. Unlike conventional fixed displacement vane pumps, which will not start up when the pumping elements have experienced a pre-determined amount of wear, traditional variable displacement vane pumps fail without warning and often catastrophically during pump operation.
  • Fuel pump 10 is adapted and configured to change the failure mode normally associated with variable displacement vane pump technology to one which is substantially similar to that of fixed displacement vane pumps.
  • a series of leak paths 87a and 87b are formed in ends 92a and 92b of body portion 19 of rotor member 16. These leak paths 92a and 92b allow high pressure which is contained with arcuate outer channel 66d, arcuate inner channel 69d and passages 67a-d to flow into the low pressure inlet arc region 60 when the vane elements 18 have worn such that the undervane portion 23 is positioned radially outward of leak paths 87a and 87b.
  • maximum vane protrusion from within the corresponding slot occurs when cam member 14 is disposed in the position corresponding to pump start-up, as illustrated in Fig. 1.
  • the vane elements 18 located in sealing arc region 64a are subj ected to the maximum protrusion from within the vane slots 17.
  • the undervane portion 23 of each vane element 18 prevents fluid from flowing into leak paths 87a and 87b.
  • the radial position of the undervane portion 23 of each vane element 18 with respect to leak paths 87a and 87b is altered.
  • the vane elements 18 wear to the extent that the undervane portion 23 is positioned radially outward of the leak paths 87a and 87b, and can no longer prevent fuel from leak paths 87a and 87b. Consequently, the leak paths 87a and 87b formed in rotor 16 begin to slowly communicate high pressure fuel to the low pressure inlet side of the sealing arc 64a.
  • vane elements 18 of vane pump 10 are shown in a worn condition. As the vane elements 18 wear, it is through the channels or recesses formed in the end plates, that the high pressure communicates to the low pressure side of the pump. As wear continues further, this communication becomes more pronounced and substantial. Eventually, a certain level of leakage through this path is achieved such that the ability of the pump to provide sufficient flow to start the engine becomes diminished and start-up cannot occur. Thus, it will be necessary to remove the pump for overhaul prior to attaining a point where failure due to an overloaded vane is imminent and a major failure can be avoided.
  • the failure mode only affects the engine's ability to start. Higher leakage during operation is not critical to the survival of a mission and therefore there is no danger that the additional leakage will interfere with engine operation. This operational scenario is identical to that of a fixed displacement pump.
  • the radial position of the leak paths 87a and 87b are established based on the configuration and size of the pumping components and the material properties of the vane elements.
  • the leak path location is selected so that the above-described failure mode is ensured and catastrophic operational failures are avoided.
  • porting connections of the pump can be achieved through a variety of methods.
  • Pump configurations can use various cuts in cams, sideplates and rotors to communicate different pressures for different reasons including, but not limited to, bearing lubrication, pressure balancing and the like.
  • the invention utilizes porting cuts in the rotor to provide for a controlled and predictable failure mode thus providing the vane pump with reliability similar to that of a fixed displacement pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Fuel-Injection Apparatus (AREA)
EP01975550A 2000-09-28 2001-09-28 Vane pump Expired - Lifetime EP1320681B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US23629300P 2000-09-28 2000-09-28
US236293P 2000-09-28
PCT/US2001/030427 WO2002027187A2 (en) 2000-09-28 2001-09-28 Vane pump

Publications (2)

Publication Number Publication Date
EP1320681A2 EP1320681A2 (en) 2003-06-25
EP1320681B1 true EP1320681B1 (en) 2004-11-24

Family

ID=22888922

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01975550A Expired - Lifetime EP1320681B1 (en) 2000-09-28 2001-09-28 Vane pump

Country Status (4)

Country Link
EP (1) EP1320681B1 (ja)
JP (1) JP2004536246A (ja)
DE (1) DE60107454T2 (ja)
WO (1) WO2002027187A2 (ja)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7207785B2 (en) * 2000-09-28 2007-04-24 Goodrich Pump & Engine Control Systems, Inc. Vane pump wear sensor for predicted failure mode
US8402811B2 (en) * 2010-06-26 2013-03-26 Yining Nie Cyclic impact-sliding fatigue wear testing instrument
CN102536801B (zh) * 2011-12-12 2015-04-22 马燕翔 无定子磨损的滑片泵

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2641195A (en) * 1947-11-28 1953-06-09 Oilgear Co Sliding vave type hydrodynamic machine
US2962972A (en) * 1958-07-23 1960-12-06 Vickers Inc Power transmission
JPS5031643B1 (ja) * 1969-02-27 1975-10-14
JPS60192892A (ja) * 1984-03-14 1985-10-01 Nippon Soken Inc ベ−ン型圧縮機
EP0399387B1 (en) * 1989-05-24 1992-09-30 Vickers Incorporated Rotary vane machine
US5545014A (en) * 1993-08-30 1996-08-13 Coltec Industries Inc. Variable displacement vane pump, component parts and method
JPH1047261A (ja) * 1996-07-30 1998-02-17 Toyoda Mach Works Ltd ベーンポンプ
DE19703113C2 (de) * 1997-01-29 1998-10-29 Danfoss As Hydraulische Flügelzellenmaschine

Also Published As

Publication number Publication date
EP1320681A2 (en) 2003-06-25
WO2002027187A3 (en) 2002-06-20
DE60107454D1 (de) 2004-12-30
DE60107454T2 (de) 2005-04-14
JP2004536246A (ja) 2004-12-02
WO2002027187A2 (en) 2002-04-04
WO2002027187A9 (en) 2003-05-30

Similar Documents

Publication Publication Date Title
EP1320682B1 (en) Vane pump
EP0623768B1 (en) Labyrinth gas-seal
EP3227577B1 (en) Hydrodynamic bearing features
EP1531270B1 (en) Vane pump with safety mechanism against wear
US5716201A (en) Variable displacement vane pump with vane tip relief
US5733109A (en) Variable displacement vane pump with regulated vane loading
US5545018A (en) Variable displacement vane pump having floating ring seal
US7637724B2 (en) Variable displacement vane pump with pressure balanced vane
US20060099100A1 (en) Cam ring bearing for fuel delivery system
NZ200819A (en) Vane type fluid motor or pump with positively pressure-controlled vane/cam contact
EP1208302B1 (en) Dual lobe, split ring, variable roller vane pump
US5833438A (en) Variable displacement vane pump having cam seal with seal land
US5738500A (en) Variable displacement vane pump having low actuation friction cam seal
EP1320681B1 (en) Vane pump
US6663357B2 (en) Vane pump wear sensor for predicted failure mode
KR880002419B1 (ko) 베인형 압축기
US6503071B2 (en) High speed UniVane fluid-handling device
US6375435B2 (en) Static cam seal for variable displacement vane pump
US7192264B2 (en) Hyrdraulic motor
EP1163449B1 (en) Variable displacement vane pump
RU2338884C1 (ru) Роторно-вихревая машина с керамическими рабочими элементами
RU2118711C1 (ru) Коловратный гидронасос переменной производительности

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20030328

AK Designated contracting states

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

17Q First examination report despatched

Effective date: 20030801

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: GOODRICH PUMP AND ENGINE CONTROL SYSTEMS, INC.

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: GOODRICH PUMP & ENGINE CONTROL SYSTEMS, INC.

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RBV Designated contracting states (corrected)

Designated state(s): DE FR GB

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 60107454

Country of ref document: DE

Date of ref document: 20041230

Kind code of ref document: P

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20050825

ET Fr: translation filed
REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 60107454

Country of ref document: DE

Representative=s name: VOSSIUS & PARTNER PATENTANWAELTE RECHTSANWAELT, DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 16

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20161130

Year of fee payment: 16

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 17

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 60107454

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20180404

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 18

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20200929

Year of fee payment: 20

Ref country code: FR

Payment date: 20200928

Year of fee payment: 20

REG Reference to a national code

Ref country code: GB

Ref legal event code: PE20

Expiry date: 20210927

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF EXPIRATION OF PROTECTION

Effective date: 20210927