EP1230486B1 - Pompe pour milieu liquide ou gazeux - Google Patents

Pompe pour milieu liquide ou gazeux Download PDF

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Publication number
EP1230486B1
EP1230486B1 EP00975951A EP00975951A EP1230486B1 EP 1230486 B1 EP1230486 B1 EP 1230486B1 EP 00975951 A EP00975951 A EP 00975951A EP 00975951 A EP00975951 A EP 00975951A EP 1230486 B1 EP1230486 B1 EP 1230486B1
Authority
EP
European Patent Office
Prior art keywords
coupling element
pump
pressure plate
pump according
seal
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
EP00975951A
Other languages
German (de)
English (en)
Other versions
EP1230486A1 (fr
Inventor
Thomas Nied-Menninger
Hans-Jürgen Lauth
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.)
ixetic Bad Homburg GmbH
Original Assignee
ixetic Bad Homburg GmbH
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 ixetic Bad Homburg GmbH filed Critical ixetic Bad Homburg GmbH
Publication of EP1230486A1 publication Critical patent/EP1230486A1/fr
Application granted granted Critical
Publication of EP1230486B1 publication Critical patent/EP1230486B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • 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
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for rotary-piston machines or pumps

Definitions

  • the invention relates to a pump, in particular vane pump, for a liquid or gaseous medium, according to the preamble of claims 1 and 4.
  • Pumps of the type discussed here are known, see for example JP-A-07 279 871 , They are used for example for power steering systems in a motor vehicle and comprise a working space which is closed in the axial direction by means of at least one pressure plate.
  • a rotor In the working space, a rotor is arranged, which can be coupled to the drive shaft of an electric motor.
  • a separate bearing for the rotor is not provided, which is supported exclusively by the drive shaft. Due to this configuration, however, there are large outer diameter for the at least one bearing of the drive shaft and a shaft seal, which seals the electric motor in the region of the drive shaft relative to the pump.
  • the pressure plate is on its side facing away from the rotor surface with a pressure chamber in communication, which is sealed relative to the motor with a cooperating with at least one seal, surrounding part of the drive shaft coupling element.
  • the coupling element engages over an annular flange provided on the side facing away from the rotor on the pressure plate, which has a large outside diameter. This is between the Flange and the coupling element formed a radially inner, the pressure chamber of the pump unit separating sealing surface whose distance from the axis of rotation of the drive shaft is large.
  • the arrangement of the inner sealing surface also determines the distance of the pressure chamber to the axis of rotation of the drive shaft, which is accordingly very large, whereby the outer diameter of the rotation group must be made correspondingly large.
  • a pump with the features of claim 1 or 4 is proposed.
  • the distance between a radially inner sealing surface of the pressure chamber to the axis of rotation of the drive shaft between the coupling element and the through hole in the pressure plate is therefore very small, so that a pressure plate and the rotor having pump unit with a small outer diameter can be realized.
  • This can create a pump with a compact, space-saving design. Since the shaft seal is not allowed to communicate with the pressure chamber, a radially outer sealing surface of the pressure chamber is arranged at a large distance from the drive shaft due to the large outer diameter of the shaft seal.
  • the area located between the radially inner and the outer sealing surface is advantageously covered in a sealing manner by means of the coupling element.
  • the coupling element for this purpose has a collar receiving the shaft sealing ring cross-section, wherein for sealing a gap between the collar and the housing portion preferably at least a second seal, for example an O-ring is provided.
  • the coupling element cooperates with an end face of the shaft sealing ring receiving housing portion, thus has no collar for sealing, but abuts with a side facing away from the rotor surface on the end face of the housing portion.
  • at least one third seal for example an O-ring, which can be arranged in a groove in the end face, or a sealing washer is provided.
  • the coupling element engages with its collar in a recess in the housing portion in which the shaft seal is arranged, wherein the gap between the outer peripheral surface of the collar and the wall of the recess preferably by means at least a third seal is sealable.
  • a preferred embodiment is located between the coupling element and the pressure plate connected to the pressure chamber clearance. Due to this configuration, it is possible that the entire projected, the coupling element facing side surface of the pressure plate with the pressurized medium, for example oil, can be acted upon, whereby the pressure plate is preferably pressed against a surrounding the working space contour ring. By pressurizing the entire side surface of the pressure plate deformation of the pressure plate in the manner of a plate spring, which could lead to a short circuit between a suction zone and a pressure zone of the pump can be prevented.
  • the pressurized medium for example oil
  • a pressing device may be provided which, for example, comprises at least one plate spring.
  • the pressing device is particularly advantageous when the coupling element is designed such that it cooperates with the end face of the shaft sealing ring receiving housing portion.
  • an embodiment of the pump is preferred in which the coupling element in the region between the larger diameter collar and the smaller diameter, in the passage opening in the pressure plate engaging portion located region has an annular bead, which for stiffening the coupling element is used. This makes it possible to form the coupling element thin-walled.
  • an embodiment of the pump is preferred, which is characterized in that the coupling element consists of sheet metal and is preferably formed in one piece.
  • the trained as a sheet metal part coupling element is therefore inexpensive to produce.
  • the coupling element is practically made of any material that can be corrosion resistant, for example, and whose strength properties are sufficient to withstand the pressure in the pressure chamber. Since the coupling element is located in the pressure chamber or adjacent to this, in the promotion of ⁇ 1 serving vane pump, the coupling element also consist of a rusting metal, since the coupling element is protected by ⁇ 1 against corrosion.
  • FIG. 1 shows a section of an embodiment of a pump 1, here as a vane pump is trained.
  • the pump 1 is arranged in the interior 3 of a housing 5 which is closed by a cover 7.
  • the pump 1 comprises a pump unit 9, which comprises a substantially elliptical working space 11 surrounding cam ring 13 and a rotor arranged in the working space 11 15, are introduced into the radially extending to a longitudinal center axis 17 slots in which radially movable wings 19 are used.
  • a medium for example a hydraulic oil, is conveyed from tank connections 21 into a pressure chamber 23. From the pressure chamber 23, the medium passes through a connection path 24 to a consumer, as indicated by arrows.
  • the pressure plate 25 is on its side facing away from the rotor 15 side surface 27 with the pressure chamber 23 in conjunction or is arranged in this embodiment in the pressure chamber 23.
  • the rotor 15 is rotatably coupled to the end of a drive shaft 29 by means of a toothed connection 31 with this.
  • the drive shaft 29 is part of a motor, not shown, preferably electric motor.
  • a bearing 33 arranged in the housing 5 is provided in this embodiment, which is designed here as a rolling bearing. It can be seen that for the cantilevered rotor 15 no own storage is provided. This results in a correspondingly large outer diameter for the bearing 33rd
  • the drive shaft 29 reaches through a passage opening 35 in the middle of the pressure plate 25.
  • the passage opening 35 is of stepped design, that is to say it has a plurality of longitudinal sections with different diameters.
  • the passage opening 35 is preferably circular in cross section.
  • the diameter of the passage opening 35 in its central region is essentially the same size as the diameter of the drive shaft 29 in the region of the bearing 33.
  • the diameter of the passage opening 35 is smaller than that of the drive shaft 29 in FIG Area of their arranged in the camp longitudinal section.
  • the diameter the arranged in the through hole 35 longitudinal portion of the drive shaft 29 is significantly smaller than the diameter of the passage opening 35. This results in a formed between the peripheral surface of the through hole 35 and the outer surface of the drive shaft 29 annulus 37th
  • a well-known shaft sealing ring 39 and a centrifugal disk 41 arranged in the region between the shaft sealing ring 39 and the bearing 33 and having a sleeve-shaped base body are provided in the embodiment shown in FIG.
  • the shaft sealing ring 39 is arranged in the region of a housing section 46, which extends like a dome in the direction of the interior 3 of the pump 1.
  • centrifugal disk 41 The function of the centrifugal disk 41 is to allow small amounts of the pumped by the pump 1 medium, which may possibly pass through the gaps between the shaft seal 39 and the drive shaft 29 and the shaft seal 39 and the housing 5, radially outwardly against the wall 43rd a recess 45 to receive the slinger 41 and the shaft sealing ring 39, where it can be removed in a suitable manner, for example by means of a discharge channel to the outside, so that it does not reach the engine.
  • a coupling element 47 is provided, which is arranged in the region between the pressure plate 25 and the shaft seal 39.
  • the coupling element 47 is here formed in one piece and as a sheet metal part and has a sleeve-shaped portion 49 which engages on the side facing away from the rotor 15 of the pressure plate 25 in the passage opening 35.
  • a first seal 51 is provided, which is formed here by an O-ring and arranged in a larger diameter portion of the through hole 35.
  • the sleeve-shaped portion 49 is followed by a substantially perpendicular to the section 49 extending wall portion 53 which has on its pressure plate 25 side facing an annular bead 55 which serves to stiffen the optionally very thin-walled coupling element 47.
  • the bead 55 is formed by a groove-shaped depression on the side facing away from the pressure plate 25.
  • a collar 57 which engages over the housing portion 46 and preferably completely surrounds on its circumference.
  • a further, second seal 59 is provided, which is here formed by an O-ring, which is arranged on an attached to the outside of the housing portion 46 annular shoulder.
  • the distance between the radially inner sealing surface between coupling element 47 and wall of the through hole 35 is significantly smaller than the distance of the radially outer Sealing surface between the coupling element 47 and the housing portion 46. Due to this configuration, a pump 1 or pump unit 9 are formed whose lying between successive wings 19 delivery spaces have only a small distance from the axis of rotation of the drive shaft 29, whereby a compact, in particular a small outer diameter having Pump unit 9 can be realized.
  • the plugged-on on the housing portion 46 collar 57 has on the inside of its free end a rounding, preferably a radius R1 on.
  • the rounding serves to facilitate the attachment of the collar 57 on the housing portion 46 and to avoid damaging the second seal 59.
  • the portion 49 of the coupling element 47 is provided at its free end on the outside with a rounding, preferably a radius R2. This rounding is to facilitate the insertion of the portion 49 in the through hole 35 of the pressure plate 25 and prevent damage to the first seal 51.
  • the coupling element 47 is formed in the region of its vertical wall portion 53 or adapted to the side surface 27 of the pressure plate 25 that a substantially annular space 61 between the coupling element 47 and an annular end wall portion 60 of the pressure plate 25 is formed, which is connected to the pressure chamber 23 is or a part of the pressure chamber 23 forms.
  • a contact pressure 63 is arranged in the pressure chamber 23, which has a compression spring 65 which is supported on the coupling element 47 on the housing 5 and the pressure plate 25 on its side surface 27 with a directed in the direction of the axis of rotation of the drive shaft 29 Force applied.
  • the pressing device 63 supports during operation of the pump 1, the contact pressure of the pressure plate 25 to the cam ring 13. In the pressureless state, the pressing of the pressure plate 25 to the cam ring 13 exclusively by the contact pressure 63, so that even before starting the pump 1 is a lateral Seal the delivery spaces between the wings 19 is given.
  • the motor and the pump 1, not shown in the figures form in the embodiment shown in Figure 1 in the assembled state, a unit which is also the subject of the invention, wherein the assembly of the centrifugal disc 41 and in particular the shaft seal 39 only after the installation of the engine the pump side takes place.
  • the bearing 33 for the drive shaft 29 is introduced from the motor side into the housing 5.
  • the bearing 33 is mounted for the drive shaft 29 from the pump side, as well as the shaft seal 29, which brings advantages in assembly and coupling of the pump and the engine together.
  • the shaft seal 39 has a very large outer diameter.
  • the coupling element 47 is disposed between the pressure chamber 23 of the pump 1 and the motor, the radially inner sealing surface of the pressure chamber can still be arranged very close to the passage of the drive shaft 29 through the pressure plate 25, so that a small outer diameter of the pressure plate 25 can be realized ,
  • FIG 2 shows a coupling element K 47 ', which is not the subject of the invention, wherein like parts are given the same reference numerals, so that reference is made to the description of Figure 1.
  • the coupling element 47 ' differs from the coupling element 47 shown in FIG. 1 only in that it has no collar 57.
  • the wall portion 53 of the coupling element 47 ' is pressed with its side surface 67 facing away from the rotor to the end face of the housing portion 46.
  • the radially outer sealing surface of the pressure chamber 23 is thus no longer located on the outside of the housing section 46 and thus closer to the drive shaft 29.
  • a third seal is provided in an advantageous embodiment.
  • the coupling element 47 ' which is easier to manufacture compared with the coupling element 47 shown in FIG.
  • the coupling element 47, 47 ' may be made of metal or plastic and is preferably formed in one piece. In a preferred embodiment that is Coupling element 47, 47 '-as shown in Figures 1 and 2- axisymmetric design.
  • the motor preferably electric motor, driven pump 1 in a motor vehicle in which only little space is available and a low weight are required, particularly advantageous.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (9)

  1. Pompe, en particulier pompe à palettes pour un milieu liquide ou gazeux, laquelle peut être entraînée à l'aide d'un moteur, en particulier d'un moteur électrique, laquelle comprend un rotor (15) disposé dans une chambre de travail pouvant être accouplé à un arbre d'entraînement (29) du moteur et au moins une plaque de pression (25) fermant la chambre de travail (11) en direction axiale, laquelle est en liaison avec une chambre de pression (23) par sa surface latérale (27) opposée au rotor (15), ainsi qu'un élément de couplage (47) entourant une partie de l'arbre d'entraînement (29), interagissant avec au moins un joint, contribuant à l'étanchéité de la chambre de pression (23) par rapport au moteur, l'arbre d'entraînement (29) traversant une ouverture de passage (35) dans la plaque de pression (25), l'élément de couplage (47) présentant une section en forme de manchon (49), laquelle pénètre dans l'ouverture de passage (35) dans la plaque de pression (25), et le diamètre de l'ouverture de passage étant plus petit, de préférence beaucoup plus petit que le diamètre extérieur d'une bague d'étanchéité d'arbre (39) entourant une partie de l'arbre d'entraînement (29), caractérisée en ce que l'élément de couplage (47) forme une surface d'étanchéité conjointement avec une partie de boîtier (46) accueillant la bague d'étanchéité d'arbre (39), l'élément de couplage (47) présentant une collerette (57) dépassant au moins partiellement une section de boîtier (46) accueillant la bague d'étanchéité d'arbre (39) et la collerette (57) et la section de boîtier (46) produisant la surface d'étanchéité.
  2. Pompe selon la revendication 1, caractérisée en ce qu'entre la section en forme de manchon (49) et l'ouverture de passage (35), au moins un premier joint (51) est prévu.
  3. Pompe selon l'une des revendications précédentes, caractérisée en ce qu'entre la collerette (57) et la section de boîtier (46), au moins un deuxième joint (59) est prévu.
  4. Pompe selon le préambule de la revendication 1, caractérisée en ce que l'élément de couplage (47) forme une surface d'étanchéité conjointement avec une section de boîtier (46) accueillant la bague d'étanchéité d'arbre (39), l'élément de couplage (47) interagissant avec une surface frontale d'une section de boîtier (46) accueillant la bague d'étanchéité d'arbre et réalisant une surface d'étanchéité.
  5. Pompe selon la revendication 4, caractérisée en ce qu'entre l'élément de couplage (47) et la surface frontale, au moins un troisième joint est prévu.
  6. Pompe selon l'une des revendications précédentes, caractérisée en ce qu'entre l'élément de couplage (47) et la plaque de pression (25) se trouve un espace libre (61) relié à la chambre de pression (23).
  7. Pompe selon l'une des revendications précédentes, caractérisée en ce qu'un dispositif de pression (63) est prévu, lequel alimente la plaque de pression (25) avec une force dirigée en direction du rotor (15).
  8. Pompe selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage (47) présente une section de paroi (53) reliée avec la section (49) en forme de manchon, laquelle section de paroi s'étend essentiellement verticalement relativement à la section (49) et dans laquelle un bourrelet (55) en forme d'anneau est placé.
  9. Pompe selon l'une des revendications précédentes, caractérisée en ce que l'élément de couplage (47) se compose de tôle et est formé de préférence d'une pièce.
EP00975951A 1999-11-02 2000-10-28 Pompe pour milieu liquide ou gazeux Expired - Lifetime EP1230486B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19952605 1999-11-02
DE19952605A DE19952605A1 (de) 1999-11-02 1999-11-02 Pumpe für ein flüssiges oder gasförmiges Medium
PCT/EP2000/010639 WO2001033081A1 (fr) 1999-11-02 2000-10-28 Pompe pour milieu liquide ou gazeux

Publications (2)

Publication Number Publication Date
EP1230486A1 EP1230486A1 (fr) 2002-08-14
EP1230486B1 true EP1230486B1 (fr) 2008-01-23

Family

ID=7927601

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00975951A Expired - Lifetime EP1230486B1 (fr) 1999-11-02 2000-10-28 Pompe pour milieu liquide ou gazeux

Country Status (5)

Country Link
US (1) US6641380B1 (fr)
EP (1) EP1230486B1 (fr)
JP (1) JP4514385B2 (fr)
DE (3) DE19952605A1 (fr)
WO (1) WO2001033081A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1461534B1 (fr) * 2001-12-27 2007-05-16 ixetic Bad Homburg GmbH Pompe
RU2257492C1 (ru) * 2003-12-01 2005-07-27 РУПП "Борисовский завод "Автогидроусилитель" Гидравлический насос
EP1672218B1 (fr) * 2004-12-18 2013-11-06 ixetic Bad Homburg GmbH Pompe
DE102005029446B4 (de) * 2005-06-24 2014-12-18 Robert Bosch Gmbh Pumpe, insbesondere für ein Hydraulikaggregat
RU2383747C2 (ru) * 2008-05-04 2010-03-10 Алексей Александрович Скрипкин Двигатель с самоуплотнением и дополнительным валом отбора мощности
EP2313656B1 (fr) * 2008-08-12 2016-02-17 Magna Powertrain Bad Homburg GmbH Unité de pompe
DE102011008294B4 (de) * 2011-01-11 2015-01-22 Magna Powertrain Ag & Co. Kg Pumpe
DE102015002352A1 (de) * 2014-12-17 2016-06-23 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Elektrische Ölpumpe, insbesondere für ein Kraftfahrzeug
DE102015105933B4 (de) 2015-04-17 2018-04-26 Schwäbische Hüttenwerke Automotive GmbH Pumpe
DE102018133681A1 (de) 2018-12-28 2020-07-02 Schwäbische Hüttenwerke Automotive GmbH Rotationspumpe mit axialer Kompensation, Auslassdichtung für eine Pumpe sowie vormontierte Pumpeneinheit
DE102019215933A1 (de) * 2019-07-26 2021-01-28 Hanon Systems Efp Deutschland Gmbh Flügelzellenpumpe
DE102020133327B4 (de) * 2020-12-14 2023-01-19 KSB SE & Co. KGaA Pumpenanordnung

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4199304A (en) 1978-03-13 1980-04-22 Ford Motor Company Positive displacement compact slipper pump
JPS58133493A (ja) * 1982-02-03 1983-08-09 Diesel Kiki Co Ltd ベ−ン型圧縮機
JPS58187591A (ja) * 1982-04-27 1983-11-01 Toyoda Mach Works Ltd ベ−ンポンプ
US4573890A (en) * 1984-10-22 1986-03-04 Atsugi Motor Parts Co., Ltd. Vane pump with locating pins for cam ring
JPS6261979U (fr) * 1985-10-09 1987-04-17
JPS62129593A (ja) * 1985-11-28 1987-06-11 Diesel Kiki Co Ltd ベ−ン型圧縮機
JPS63173893A (ja) * 1987-01-09 1988-07-18 Seiko Seiki Co Ltd 気体圧縮機
JP2800575B2 (ja) * 1992-08-07 1998-09-21 日産自動車株式会社 ベーンポンプ
JPH07279871A (ja) 1994-04-04 1995-10-27 Showa:Kk オイルポンプの駆動軸枢支構造
DE19725195A1 (de) * 1996-06-29 1998-01-02 Luk Fahrzeug Hydraulik Flügelzellenpumpe
DE19802443C1 (de) * 1998-01-23 1999-05-12 Luk Fahrzeug Hydraulik Pumpe

Also Published As

Publication number Publication date
DE10083436D2 (de) 2002-12-19
DE10083436B4 (de) 2013-04-11
JP2003514175A (ja) 2003-04-15
DE50014936D1 (de) 2008-03-13
WO2001033081A1 (fr) 2001-05-10
JP4514385B2 (ja) 2010-07-28
EP1230486A1 (fr) 2002-08-14
US6641380B1 (en) 2003-11-04
DE19952605A1 (de) 2001-05-10

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