US20090238707A1 - Vane pump - Google Patents

Vane pump Download PDF

Info

Publication number
US20090238707A1
US20090238707A1 US11/721,349 US72134905A US2009238707A1 US 20090238707 A1 US20090238707 A1 US 20090238707A1 US 72134905 A US72134905 A US 72134905A US 2009238707 A1 US2009238707 A1 US 2009238707A1
Authority
US
United States
Prior art keywords
rotor
annular groove
region
rotation axis
eccentricity
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
US11/721,349
Other languages
English (en)
Inventor
Christian Langenbach
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.)
Robert Bosch GmbH
Original Assignee
Individual
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 Individual filed Critical Individual
Assigned to ROBERT BOSCH GMBH reassignment ROBERT BOSCH GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LANGENBACH, CHRISTIAN
Publication of US20090238707A1 publication Critical patent/US20090238707A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • 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
    • 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
    • F04C2270/70—Safety, emergency conditions or requirements
    • F04C2270/701—Cold start

Definitions

  • the invention relates to a vane pump as generically defined by the preamble to claim 1 .
  • a vane pump of this kind is known from DE 199 52 167 A1.
  • This vane pump has a pump housing that contains a rotor, which is driven to rotate via a drive shaft.
  • the rotor has a number of grooves distributed over its circumference that extend in an at least essentially radial direction in relation to the rotation axis of the rotor, each of which has a respective vane-shaped delivery element guided in it in sliding fashion.
  • the pump housing has a circumference wall encompassing the rotor and extending eccentrically in relation to its rotation axis, against which the radially outer ends of the vanes rest.
  • the pump housing has housing end walls situated adjacent to the rotor in the direction of the rotation axis of the rotor.
  • the vanes form chambers, which expand and contract during rotation of the rotor and between which the medium to be supplied is conveyed with an increase in pressure from a suction region to a pressure region that is offset from it in the circumference direction. Centrifugal forces when the rotor is turning hold the vanes in contact with the circumference wall, but at low speeds, particularly when vane pump rotation is just starting, only slight centrifugal forces are exerted so that the vane pump only delivers a small amount.
  • another delivery pump that forms a combined pump unit with the vane pump supplies the inner regions, which are delimited in the grooves by the vanes, with compressed medium, which presses the vanes outward toward the circumference wall in addition to the centrifugal force.
  • at least one housing end wall is provided with an annular groove extending over part of the circumference of the rotor, which is supplied with compressed medium by the additional delivery pump.
  • the annular groove is separated from the drive shaft by a sealing region in which the rotor and the adjoining housing end wall are situated spaced slightly apart from each other in the axial direction.
  • the annular groove is situated concentric to the rotation axis of the rotor so that the sealing region has a constant radial span.
  • the disadvantage in this known vane pump is that the annular groove extending over only part of the circumference of the rotor only exerts pressure on the inner regions of the grooves of the rotor over a corresponding part of a rotation of the rotor, as a result of which under some circumstances, there is only a slight pressing force of the vane against the circumference wall. Moreover, the sealing region can permit leakage of pressurized medium from the annular groove toward the drive shaft.
  • the vane pump according to the invention has the advantage of the prior art that the exertion of pressure on the inner regions of the grooves of the rotor is intensified by means of the annular groove extending over the entire circumference of the rotor.
  • the sealing region between the annular groove and the drive shaft it is possible to intentionally enlarge the radial span of the sealing region in a circumference region of the rotor, which can be used to reduce the leakage from the annular groove.
  • FIG. 1 shows a simplified view of a vane pump in a cross section along the line I-I in FIG. 3 ,
  • FIG. 2 shows the vane pump in a cross section along the line II-II in FIG. 3 .
  • FIG. 3 shows the vane pump in a longitudinal section along the line III-III in FIG. 1 .
  • FIGS. 1 through 3 show a vane pump that is preferably provided for delivery of fuel, in particular diesel fuel.
  • the vane pump delivers fuel from a tank to a high-pressure pump.
  • the vane pump can be separate from the high-pressure pump, built onto the high-pressure pump, or integrated into the high-pressure pump.
  • the vane pump has a pump housing 10 that is comprised of multiple parts and a drive shaft 12 that protrudes into the pump housing 10 .
  • the pump housing 10 has two housing end walls 14 , 16 that delimit a pump chamber in the axial direction, i.e. in the direction of the rotation axis 13 of the drive shaft 12 .
  • the pump chamber is delimited by a circumference wall 18 that is integrally joined to the housing end walls 14 , 16 or can be embodied as a component separate from them.
  • the pump chamber contains a rotor 20 that is attached in a torsionally fixed manner to the drive shaft 12 , for example by means of a groove/spring connection 22 .
  • the rotor 20 has a plurality of grooves 24 distributed over its circumference, extending at least essentially radially to the rotation axis 13 of the rotor 20 .
  • the grooves 24 extend into the rotor 20 from the outer circumference of the rotor 20 toward the rotation axis 13 .
  • four grooves 24 are provided; it is also possible for fewer or more than four grooves 44 to be provided.
  • a plate-shaped delivery element 26 is situated in sliding fashion, which will be referred to below as a vane and whose radially outer end region protrudes out from the groove 24 .
  • Each vane 26 delimits an inner region 25 situated toward the radial inside in the respective groove 24 .
  • the inside of the circumference wall 18 of the pump housing 10 is situated eccentrically to the rotation axis 13 of the rotor 20 , for example in the form of a circle or some other shape.
  • a suction region is provided, which communicates with at least one suction opening 28 .
  • the suction opening 28 connects to the suction groove 30 , preferably in its end region oriented opposite the rotation direction 21 of the rotor 20 .
  • the suction opening 28 is connected to an inlet leading from the tank.
  • At least one housing end wall 14 , 16 is also provided with high-pressure region, which communicates with at least one pressure opening 32 .
  • an elongated pressure groove 34 is provided, which is curved in an approximately kidney-shaped fashion, extends in the circumference direction of the rotor 20 , and communicates with the pressure opening 32 .
  • the pressure opening 32 connects to the pressure groove 34 , preferably in its end region oriented in the rotation direction 21 of the rotor 20 .
  • the pressure opening 32 is connected to an outlet that leads to the high-pressure pump.
  • the suction opening 28 , the suction groove 30 , the pressure opening 32 , and the pressure groove 34 are situated spaced radially apart from the rotation axis 13 of the rotor 20 , close to the inside of circumference wall 18 .
  • the radially outer ends of the vanes 26 rest against the inside of the circumference wall 18 and slide along it in the rotation direction 21 as the rotor 20 turns. Because of the eccentric design of the inside of the circumference wall 18 in relation to the rotation axis 13 of the rotor 20 , the vanes 26 form chambers 36 with changing volumes.
  • the suction groove 30 and the suction opening are situated in a circumference region in which the rotating motion of the rotor 20 in the rotation direction 21 causes the volume of the chambers 36 to increase so that they are filled with fuel.
  • the compression groove 34 and the pressure opening 32 are situated in a circumference region in which the rotating motion of the rotor 20 in the rotation direction 21 causes the volume of the chambers 36 to decrease so that fuel is displaced from them into the pressure groove 34 and from there into the pressure opening 32 .
  • annular groove 38 is provided, which extends over the entire circumference of the rotor 20 and communicates with the pressure groove 34 via a connecting groove 40 .
  • a connecting groove 40 it is also possible for a connecting bore to be provided.
  • a sealing region 39 is formed in which there is only a slight axial distance between the rotor 20 and the adjoining housing end wall 14 , 16 . In the region around the drive shaft 12 , there is only a slight amount of pressure so that between the annular groove 38 and the region around the drive shaft 12 , there is a pressure difference.
  • the annular groove 38 extends eccentrically in relation to the rotation axis 13 of the rotor 20 so that the radial span s of the sealing region 39 is different over the circumference of the annular groove 38 .
  • the annular groove 38 can, for example, be at least approximately circular, having a center point M, which is situated offset from the rotation axis 13 of the rotor 20 by a distance e that constitutes the eccentricity.
  • the eccentricity e of the annular groove 38 is at least approximately of the same magnitude and oriented in the same direction as the eccentricity of the inside of the circumference wall 18 of the pump housing 10 .
  • the center point M of the annular groove 138 is situated offset from the rotation axis 13 in a direction toward a region of the circumference wall 18 situated between the suction groove 30 and the pressure groove 34 in the rotation direction 21 of the rotor 20 .
  • This eccentric arrangement of the annular groove 38 increases the radial span s 1 of the sealing region 39 inside the annular groove 38 in relation to the drive shaft 12 on the side toward which the center point M is offset in relation to the rotation axis 13 while decreasing the radial span s 2 of the sealing region 39 on the opposite side.
  • annular groove 38 it is also possible for the annular groove 38 to not be circular, but to have an eccentric course in relation to the rotation axis 13 , in which case the radial span s 1 of the sealing region 39 in a region between the suction groove 30 and the pressure groove 34 in the rotation direction 21 of the rotor 20 is greater than the radial span s 2 of the sealing region 39 in the opposite region.
  • the connecting groove 40 can, for example, extend inward from the pressure groove 34 in a radial direction or at an angle to a radius with regard to the rotation axis 13 .
  • the connecting groove 40 can, in particular, extend in such a way that it approaches the annular groove 38 in the rotation direction 21 of the rotor 20 .
  • the connecting groove 40 can extend in a spiral curve.
  • the connecting groove 40 is preferably connected at one end at least approximately tangentially to the pressure groove 34 and/or at the other end, at least approximately tangentially to the annular groove 38 .
  • the connecting groove 40 connects to the end region of the pressure groove 34 oriented opposite from the rotation direction 21 of the rotor 20 .
  • this drag flow achieves a pressure increase in the annular groove 38 even when the vane pump rotation is just starting so that the vane pump delivers a sufficient quantity of fuel even as it is starting to turn.
  • the curved course of the connecting groove 40 also assures that when the rotor 20 is turning, the vanes 26 move across the connecting groove 40 in an approximately tangential fashion, which minimizes the wear on the vanes 26 and the housing end wall 14 , 16 .
  • annular groove 38 and the connecting groove 40 that connects it to the pressure groove 34 can be provided in only one housing end wall 14 or 16 or for an annular groove 38 and a connecting groove 40 to be provided in both housing end walls 14 and 16 , which grooves are then preferably situated in mirror-image fashion in relation to each other in the housing end walls 14 and 16 . It is also possible for a respective annular groove 38 to be provided in each of the two housing end walls 14 and 16 , but for a connecting groove 40 to be provided in only one housing part 14 or 16 .
  • suction groove 30 and/or the pressure groove 34 may be provided in only one housing end wall 14 or 16 , in which case the other housing end wall 16 or 14 is embodied as smooth or for a respective suction groove 30 and/or pressure groove 34 to be provided in each of the two housing end walls 14 and 16 , which grooves are then preferably situated in mirror-image fashion in relation to each other in the housing end walls 14 and 16 .
  • the suction opening 28 and the pressure opening 32 are each provided in only one respective housing end wall 14 or 16 , with the suction opening 28 provided in one housing end wall 14 and the pressure opening 32 provided in the other housing wall 16 .
  • the rotor 20 and the vanes 26 are loaded in at least approximately equal fashion at both ends in the axial direction so that little or no resulting force is exerted on the rotor 20 and the vanes 26 in the direction of the rotation axis 13 .
  • the depth of the annular groove 38 and connecting groove 40 in the housing end wall 14 , 16 is between 0.1 and 2 mm and the width of the grooves 38 , 40 is preferably greater than their depth.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
US11/721,349 2004-12-16 2005-11-21 Vane pump Abandoned US20090238707A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004060551.3 2004-12-16
DE102004060551A DE102004060551A1 (de) 2004-12-16 2004-12-16 Flügelzellenpumpe
PCT/EP2005/056088 WO2006063917A1 (de) 2004-12-16 2005-11-21 Flügelzellenpumpe

Publications (1)

Publication Number Publication Date
US20090238707A1 true US20090238707A1 (en) 2009-09-24

Family

ID=35589620

Family Applications (1)

Application Number Title Priority Date Filing Date
US11/721,349 Abandoned US20090238707A1 (en) 2004-12-16 2005-11-21 Vane pump

Country Status (7)

Country Link
US (1) US20090238707A1 (de)
EP (1) EP1828611B1 (de)
JP (1) JP2008524486A (de)
CN (1) CN101080573A (de)
AT (1) ATE408064T1 (de)
DE (2) DE102004060551A1 (de)
WO (1) WO2006063917A1 (de)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009048479A1 (de) 2009-10-07 2011-04-21 Volkswagen Ag Wärmekraftmaschine in Form eines Flügelzellenexpanders
JP5480730B2 (ja) * 2010-06-24 2014-04-23 宗司 中川 ベーン型内燃機関の気密構造
JP5865631B2 (ja) * 2011-08-23 2016-02-17 株式会社ショーワ ベーンポンプ
DE102011054028A1 (de) * 2011-09-29 2013-04-04 Zf Lenksysteme Gmbh Verdrängerpumpe
WO2013068531A2 (de) 2011-11-11 2013-05-16 Dieter Brox Regelbarer flügelkompressor
JP6023615B2 (ja) * 2013-03-13 2016-11-09 Ｋｙｂ株式会社 可変容量型ベーンポンプ
EP3056737B1 (de) * 2015-02-11 2017-11-15 Danfoss A/S Flügelzellenpumpe
JP2019019673A (ja) * 2017-07-11 2019-02-07 日立オートモティブシステムズ株式会社 ポンプ
CN111683885B (zh) * 2018-02-06 2022-06-03 申克普若赛斯欧洲有限公司 用于将密封件紧固到旋转给料机的转子叶片的系统
JP7243528B2 (ja) * 2019-08-29 2023-03-22 株式会社デンソー ベーンポンプ
DE102019127389A1 (de) * 2019-10-10 2021-04-15 Schwäbische Hüttenwerke Automotive GmbH Flügelzellenpumpe

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2423271A (en) * 1942-09-11 1947-07-01 Frank A Talbot Rotary motor, pump, and the like
US4854830A (en) * 1987-05-01 1989-08-08 Aisan Kogyo Kabushiki Kaisha Motor-driven fuel pump
US4872806A (en) * 1987-05-15 1989-10-10 Aisan Kogyo Kabushiki Kaisha Centrifugal pump of vortex-flow type
US5033946A (en) * 1986-07-22 1991-07-23 Eagle Industry Co., Ltd. Rotary vane machine with back pressure regulation on vanes
US5490770A (en) * 1993-11-26 1996-02-13 Aisin Seiki Kabushiki Kaisha Vane pump having vane pressurizing grooves
US6244830B1 (en) * 1996-12-23 2001-06-12 Luk, Fahrzeug-Jydraulik Gmbh & Co. Kg Vane-cell pump
US6877969B2 (en) * 2003-04-09 2005-04-12 Toyoda Koki Kabushiki Kaisha Vane pump

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60150496A (ja) * 1984-01-18 1985-08-08 Hitachi Ltd 可動翼形圧縮機
JPS63280883A (ja) * 1987-05-14 1988-11-17 Toyota Autom Loom Works Ltd 可変容量型ベ−ン圧縮機
DE19529806C2 (de) * 1995-08-14 1999-04-01 Luk Fahrzeug Hydraulik Flügelzellenpumpe
DE19710378C1 (de) * 1996-12-23 1998-03-12 Luk Fahrzeug Hydraulik Flügelzellenmaschine, insbesondere Flügelzellenpumpe

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2423271A (en) * 1942-09-11 1947-07-01 Frank A Talbot Rotary motor, pump, and the like
US5033946A (en) * 1986-07-22 1991-07-23 Eagle Industry Co., Ltd. Rotary vane machine with back pressure regulation on vanes
US4854830A (en) * 1987-05-01 1989-08-08 Aisan Kogyo Kabushiki Kaisha Motor-driven fuel pump
US4872806A (en) * 1987-05-15 1989-10-10 Aisan Kogyo Kabushiki Kaisha Centrifugal pump of vortex-flow type
US5490770A (en) * 1993-11-26 1996-02-13 Aisin Seiki Kabushiki Kaisha Vane pump having vane pressurizing grooves
US6244830B1 (en) * 1996-12-23 2001-06-12 Luk, Fahrzeug-Jydraulik Gmbh & Co. Kg Vane-cell pump
US6877969B2 (en) * 2003-04-09 2005-04-12 Toyoda Koki Kabushiki Kaisha Vane pump

Also Published As

Publication number Publication date
CN101080573A (zh) 2007-11-28
ATE408064T1 (de) 2008-09-15
WO2006063917A1 (de) 2006-06-22
EP1828611B1 (de) 2008-09-10
DE102004060551A1 (de) 2006-06-22
DE502005005361D1 (de) 2008-10-23
EP1828611A1 (de) 2007-09-05
JP2008524486A (ja) 2008-07-10

Similar Documents

Publication Publication Date Title
US20090238707A1 (en) Vane pump
US7878779B2 (en) Vane pump with housing end wall having an annular groove and a pressure groove that communicate via a curved connecting groove
US7997882B2 (en) Reduced rotor assembly diameter vane pump
US7845922B2 (en) Vane pump
EP2976531B1 (de) Gleitmittelflügelzellenpumpe
EP0398377B1 (de) Rotationshydraulikmaschine
US4758141A (en) Vane pump with flexible tongue valve
US5407327A (en) Vane cell pump
EP0735271B1 (de) Seitenkanalbrennstoffpumpe für Kraftfahrzeug
US7165932B2 (en) Fuel pump having dual single sided impeller
US8672658B2 (en) Vane pump with improved rotor and vane extension ring
US7008174B2 (en) Fuel pump having single sided impeller
US7300267B2 (en) Unit for delivering fuel to an internal combustion engine
US20010016167A1 (en) Static cam seal for variable displacement vane pump
US5980200A (en) Peripheral pump, in particular for feeding fuel from feed tank to internal combustion engine of motor vehicle
US6719543B2 (en) Selectively adjustable fixed displacement vane pump
US9909584B2 (en) Lubricant vane pump
US7632060B2 (en) Fuel pump having dual flow channel
CN112513464B (zh) 流体输送装置
US6835056B2 (en) Roller vane pump incorporating a bearing bush
US7267524B2 (en) Fuel pump having single sided impeller
US20210270266A1 (en) Rotary vane pump
EP4240973A1 (de) Schmiermittelpumpe mit variabler verdrängung

Legal Events

Date Code Title Description
AS Assignment

Owner name: ROBERT BOSCH GMBH, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:LANGENBACH, CHRISTIAN;REEL/FRAME:022882/0067

Effective date: 20070213

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION