EP1026401A2 - Pompe hydrostatique - Google Patents

Pompe hydrostatique Download PDF

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Publication number
EP1026401A2
EP1026401A2 EP00101946A EP00101946A EP1026401A2 EP 1026401 A2 EP1026401 A2 EP 1026401A2 EP 00101946 A EP00101946 A EP 00101946A EP 00101946 A EP00101946 A EP 00101946A EP 1026401 A2 EP1026401 A2 EP 1026401A2
Authority
EP
European Patent Office
Prior art keywords
side window
pump
pump according
pump housing
hydrostatic
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.)
Granted
Application number
EP00101946A
Other languages
German (de)
English (en)
Other versions
EP1026401A3 (fr
EP1026401B1 (fr
Inventor
Bernhard Arnold
Franz Pawellek
Franz Wirzberger
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP1026401A2 publication Critical patent/EP1026401A2/fr
Publication of EP1026401A3 publication Critical patent/EP1026401A3/fr
Application granted granted Critical
Publication of EP1026401B1 publication Critical patent/EP1026401B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • 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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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 invention relates to a hydrostatic pump according to the preamble of claim 1.
  • Such hydrostatic pumps can, for example be designed as a cellular pump, as they are in DE 32 12 363 A1.
  • the well-known construction has a pump housing in which a drive shaft is rotatably mounted is. At the end section dipping into the pump housing A rotor is attached to the drive shaft Radially displaceable wing carries. The one from the rotor wings protruding in the radial direction lie on the Inner circumferential wall of a cam ring, which is eccentrically in the Pump housing is mounted. Two adjacent wings each limit a cell, the volume of which is dependent changes from the rotational angle position of the drive shaft. Face the cells are on the one hand from a pump cover and on the other hand limited by a side window.
  • the at the known solution used side window is a Spring biased into its bearing position, on a Housing cover is supported over which the pump housing is sealed at the end.
  • the spring space for those The spring tensioning the side window is filled with pressure medium, so that when pressure builds up in the cells of the vane pump the side window essentially by the fluid pressure is biased into its sealing position. That is, the spring is only required to the sealing system the side window when starting the pump.
  • the invention is based on the object to create a pump that is characterized by a minimal device technology Distinctive effort and at which the Leakage is minimal when the pump is started.
  • the front of the pump housing to seal the side window and in via a spring element The pump can preload towards the displacement chamber constructed much simpler than in the known solution in addition to the side window there is also a housing cover was required.
  • prestressing the side window into its sealing position only via the spring element so that no channels, pressure relief valve devices etc. formed in the pump housing to the spring space - as in the prior art - to be filled with pressure medium. Because of the missing housing cover the pump in the axial direction can be essential shorter than in the previously described prior art become.
  • the construction of the invention can be particularly advantageous to use in vane pumps where the cells formed between two wings on each end limited by the pump housing and the side window are, the latter against the spring element the cam ring is biased.
  • Tilting of the side window can be prevented in the spring element at a radial distance from the drive shaft, i.e. attacks on the edge area of the side window.
  • the overall length can be further reduced if the disc spring immersed in an annular recess in the side window.
  • the depth of this ring recess is that Axial length of the disc spring adjusted.
  • a ring channel can open in the area of the ring recess, over the pressure medium into a flushing channel of the pump housing is feedable. This pressure medium flow can then be used for cooling / lubrication. In this embodiment it is preferred if the disc spring with Breakthroughs are provided through which the flushing flow pass can.
  • the construction described above with a minimal axial length can be used particularly advantageously for pumps, where the vane pump is a high pressure pump is assigned, whose suction connection with the pressure connection the vane pump is connected.
  • the high pressure pump is preferably designed as a radial piston pump, the Displacer (piston) through an eccentric of the drive shaft be operated.
  • the front seal of the eccentric space is preferably carried out in this embodiment through the side window. In such an embodiment the flushing channel described above opens into the eccentric space, so that cooling / lubrication of the high pressure pump can be done.
  • the hydrostatic pump is designed as a vane pump 1.
  • the structure according to the invention can be also with other hydrostatic pumps, for example use with a gear pump etc., where the Pressure medium pressurized up to about 10 bar shall be.
  • the vane pump 1 shown in Figure 1 has a Pump housing 2, in which a drive shaft 4 rotatably mounted is. This is rotatably connected to a rotor 6, which has a plurality of radial slots in which Wing 8 are guided radially.
  • the wings 8 are hydraulic with their protruding beyond the rotor 6 End sections in contact position against the inner peripheral wall a cam ring 10 pressed.
  • This cam ring 10 is stored in the pump housing 2 and has an eccentric Inner bore in which the rotor 6 is guided, so that in the Representation according to Figure 1 between the rotor 6, the cam ring 10 and 2 adjacent wings 8 a sickle-shaped Cell 12 is limited, the volume of which is dependent changed by the angle of rotation of the drive shaft 4.
  • FIG 2 shows a section along the line A-A in Figure 1. Accordingly, the cells 12 are front of one Limited pump cover 14 and a side plate 16, which rest on the cam ring 10.
  • the pump housing 2 is provided with a receiving bore 18 provided on the peripheral walls of the cam ring 10 and Side window 16 are supported or guided.
  • the wings dive 8 in radial slots being between the bottom of the radial slot and the adjacent face of each Wing 8 a pressure chamber 20 for receiving pressure medium is provided, via which the wings 8 in their contact position be biased against the cam ring 10.
  • the inner bore 22 penetrated by the drive shaft 4 is widened towards the end faces of the rotor 6, so that the position positioning of the rotor 6 is facilitated.
  • the non-rotatable connection between drive shaft 4 and rotor 6 takes place via a suitable connecting element 24, for example a key that fits into an axial groove 26 of the rotor 6 immersed and in a pocket of the drive shaft 4 is recorded in sections.
  • a suitable connecting element 24 for example a key that fits into an axial groove 26 of the rotor 6 immersed and in a pocket of the drive shaft 4 is recorded in sections.
  • a sliding bush 28 for guiding the drive shaft 4.
  • the side window 16 via a spring element, in the present case a disc spring 30 biased into their bearing position against the cam ring 10.
  • the plate spring 30 is supported on a radial shoulder 32 of the pump housing 2.
  • the outside diameter the plate spring 30 is only slightly smaller than the inside diameter the receiving bore 18 so that the plate spring 30 applied to the side window 16 with a maximum span.
  • This broad support means that the Side window 16 reliably prevented, so that even higher drive shaft speeds a reliable system of the side part 16 on the cam ring 10 is guaranteed.
  • the plate spring 30 dips into an annular recess 34 a whose axial depth is slightly less than the axial length of the Disc spring 30 is formed.
  • An opening opens into the end face of the ring recess 34 Ring channel 36 through which a pressure medium flow through the Side window into a flushing channel 38 of the pump housing 2 can be done. Via this flushing channel 38 Pressure medium for cooling / lubricating highly stressed components the pump 1 are branched off. This optional Formation of a coolant / lubricant flow is, for example then used when the drive shaft 4 also to drive a high pressure pump, for example a radial piston pump is used that on the flushing-lubrication circuit connected.
  • the plate spring 30 is at least in the area of the flushing channel 38 provided with at least one opening 40, via the in the pressure medium through the plate spring 30 can enter the rinsing channel 38.
  • the supply and discharge of the pressure medium to and from the Cells 12 take place via a suction kidney 42 or a pressure kidney 44, which are formed in the housing cover 14 and in corresponding recesses 46, 48 in the adjacent End face of the side window 16 open.
  • the sealing of the side window 16 with respect to the housing 2 takes place via an O-ring 50 which is in an annular groove is inserted on the outer circumference of the side window 16.
  • Such a vane pump 1 is installed very easy.
  • the drive shaft 4 becomes the high pressure pump, if necessary inserted into the pump housing 2 and then the Disc spring 30 inserted so that this on the radial shoulder 32 rests. Then the side window 16 with the sliding bush 28 pushed onto the drive shaft 4, until it comes into contact position with the plate spring 30.
  • the housing cover 14 with the Pump housing 2 screwed.
  • the Housing cover 14 with the Pump housing 2 screwed.
  • the Side window 16 is by the force of Belleville washer 30 against the one against the housing cover 14 Hubring 10 biased without further attachment or Prestressing means required.
  • the tension of the plate spring 30 is designed so that the side window 16 in the over Vane pump 1 sealing maximum pressure to be applied rests on the cam ring as well as on the vanes 12 and the rotor 6, so that the leakage is minimal in this pressure range.
  • the side part 16 can also the Frontal limitation of the pump housing for the radial piston pump form. That is, in this case the side window forms 16 at least part of an end boundary of the eccentric chamber of the radial piston pump 1.
  • a hydrostatic pump is disclosed, in particular a vane pump, in which the displacement space on the front limited by a housing cover and a side window is. The latter is in its contact position via a spring element biased and forms the frontal portion of the Pump housing for the vane pump.
  • the side surface of the side plate 16, which is the rotor 6 and is assigned to the cam ring 10 is a metallic sealing surface educated.
  • the side surfaces of the rotor 6 and the cam ring 10, the side window 16 or the pump cover 14 are assigned, designed as metallic sealing surfaces.
  • the cells 12 are sealed by means of the dense one Pressure of the sealing surface of the side window 16 against the sealing surfaces of the rotor 6 and the cam ring 10.
  • the contact pressure is generated only by the plate spring 30.
  • the side window 16 has in addition to the implementation of the drive shaft 4th no through channels, so no hydraulic Connection between the two areas of the pump housing 2 is present, which is formed on both sides of the side window 16 are separated by the side window 16.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
EP00101946A 1999-02-03 2000-02-01 Pompe hydrostatique Expired - Lifetime EP1026401B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19904339A DE19904339A1 (de) 1999-02-03 1999-02-03 Hydrostatische Pumpe
DE19904339 1999-02-03

Publications (3)

Publication Number Publication Date
EP1026401A2 true EP1026401A2 (fr) 2000-08-09
EP1026401A3 EP1026401A3 (fr) 2001-09-26
EP1026401B1 EP1026401B1 (fr) 2003-06-11

Family

ID=7896297

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00101946A Expired - Lifetime EP1026401B1 (fr) 1999-02-03 2000-02-01 Pompe hydrostatique

Country Status (2)

Country Link
EP (1) EP1026401B1 (fr)
DE (2) DE19904339A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009135587A2 (fr) * 2008-05-08 2009-11-12 Ixetic Bad Homburg Gmbh Pompe
EP3081741A3 (fr) * 2015-04-17 2017-01-04 Schwäbische Hüttenwerke Automotive GmbH Pompe
US10458406B2 (en) * 2016-03-11 2019-10-29 Magna Powertrain Bad Homburg GmbH Seal arrangement for a switchable vane cell pump of cartridge design

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102251962A (zh) * 2011-08-18 2011-11-23 肖义堃 一种叶片泵
DE102020116748A1 (de) 2020-06-25 2022-02-17 Schwäbische Hüttenwerke Automotive GmbH Pumpe mit axial wirksamer Federdichtung

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3212363A1 (de) 1981-04-23 1983-02-10 General Motors Corp., Detroit, Mich. Selbstanlaufende fluegelkolbenpumpe

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1121395A (fr) * 1954-03-30 1956-08-13 Dispositif de retenue de fluides pour machines rotatives
US3362339A (en) * 1965-10-01 1968-01-09 Leeds & Northrup Co Metering pump
US3549288A (en) * 1969-03-05 1970-12-22 Ford Motor Co Positive displacement slipper pump with flangeless drive shaft
JPS56156489A (en) * 1980-05-06 1981-12-03 Jidosha Kiki Co Ltd Oil pump
DE9201060U1 (de) * 1992-01-29 1992-03-19 Voulgaris, Andres, 8164 Hausham Hydraulischer Motor
DE19531701C1 (de) * 1995-08-14 1997-01-16 Luk Fahrzeug Hydraulik Pumpe
DE19631846A1 (de) * 1995-08-14 1997-02-20 Luk Fahrzeug Hydraulik Pumpe
DE19546329A1 (de) * 1995-12-12 1997-06-19 Zahnradfabrik Friedrichshafen Flügelzellenpumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3212363A1 (de) 1981-04-23 1983-02-10 General Motors Corp., Detroit, Mich. Selbstanlaufende fluegelkolbenpumpe

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009135587A2 (fr) * 2008-05-08 2009-11-12 Ixetic Bad Homburg Gmbh Pompe
WO2009135587A3 (fr) * 2008-05-08 2010-03-18 Ixetic Bad Homburg Gmbh Pompe
EP3081741A3 (fr) * 2015-04-17 2017-01-04 Schwäbische Hüttenwerke Automotive GmbH Pompe
US10082139B2 (en) 2015-04-17 2018-09-25 Schwäbische Hüttenwerke Automotive GmbH Pump comprising a spring
EP3081741B1 (fr) 2015-04-17 2019-11-13 Schwäbische Hüttenwerke Automotive GmbH Pompe
US11143181B2 (en) 2015-04-17 2021-10-12 Schwäbische Hüttenwerke Automotive GmbH Pump comprising a spring
US10458406B2 (en) * 2016-03-11 2019-10-29 Magna Powertrain Bad Homburg GmbH Seal arrangement for a switchable vane cell pump of cartridge design

Also Published As

Publication number Publication date
DE50002506D1 (de) 2003-07-17
DE19904339A1 (de) 2000-08-10
EP1026401A3 (fr) 2001-09-26
EP1026401B1 (fr) 2003-06-11

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