EP0910746B1 - Pompe a cellules semi-rotative - Google Patents

Pompe a cellules semi-rotative Download PDF

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Publication number
EP0910746B1
EP0910746B1 EP98920506A EP98920506A EP0910746B1 EP 0910746 B1 EP0910746 B1 EP 0910746B1 EP 98920506 A EP98920506 A EP 98920506A EP 98920506 A EP98920506 A EP 98920506A EP 0910746 B1 EP0910746 B1 EP 0910746B1
Authority
EP
European Patent Office
Prior art keywords
pressure
vane
rotor
cell pump
pressure plate
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
EP98920506A
Other languages
German (de)
English (en)
Other versions
EP0910746A1 (fr
Inventor
Hans-Jürgen Lauth
Thomas Nied-Menninger
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.)
LuK Fahrzeug Hydraulik GmbH and Co KG
Original Assignee
LuK Fahrzeug Hydraulik GmbH and Co KG
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 LuK Fahrzeug Hydraulik GmbH and Co KG filed Critical LuK Fahrzeug Hydraulik GmbH and Co KG
Publication of EP0910746A1 publication Critical patent/EP0910746A1/fr
Application granted granted Critical
Publication of EP0910746B1 publication Critical patent/EP0910746B1/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
    • 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
    • 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

Definitions

  • the invention relates to a vane pump according to Preamble of claim 1.
  • Vane pumps of the type mentioned here are known. They serve, for example, a fluid to provide for a power steering system in a vehicle. They have a pump unit that a cam ring and one rotatably mounted in this Includes rotor. This is radial to Provide axes of rotation in which Wing movably supported in the radial direction are. When the rotor rotates inside the The wings are larger and smaller from the wings being formed subspaces, so that at least ever a suction and a pressure area are created. At least on one side of the pump unit is a pressure plate provided a side boundary surface for the suction and pressure areas. in the Operation of the pump will counter the pressure plate Pump unit pressed, causing wear greatly increased. To counteract this, at the installation of the pump a corresponding game between The cam ring and rotor are provided, making the volumetric Efficiency is often not sufficient is.
  • a vane pump is known from US Pat. No. 3,695,791 known in which an arched, from a bimetal manufactured printing plate is used.
  • the pressure plate is installed so that a predetermined Distance between the pressure plate and the Rotor remains and that the pressure plate is planar between the housing and the rotor is clamped. Due to the bimetallic function of the sealing washer should be achieved that this in operation of the pump Distance remains. Should the pressure plate under a pressure given during the operation of the pump are bent, so the deflection at heating of the fluid to be pumped is canceled, since the bimetal is heated accordingly and counteracts the deflection caused by the pressure forces, by snapping the pressure plate back. It has been shown that in the known pump not a sufficient volumetric in all cases Efficiency can be guaranteed.
  • a vane pump is used to solve this task proposed that mentioned in claim 1 Features. This distinguishes the pump from that the surface facing the pump unit the pressure plate, i.e. the side of the pressure plate, the rotor, the wings, the cam ring and is facing the suction and pressure areas, in depressurized state of the pump is concave is. In the unloaded state of the pressure plate, that is at low pressure (for example when driving straight ahead, if there is no steering), this is sufficient Given the distance to the rotor and the blades, so that at low pressure the oil friction in Gap and thus the mechanical losses low are.
  • An embodiment of the pump is preferred, which is characterized in that on each side the rotor or the pump unit each a pressure plate is provided, which accordingly are concave, the concave side is facing the pressure plate of the pump unit.
  • Vane pumps of the type mentioned here are basically known, so that on their structure and Function is not discussed in detail. It is exemplified here by a pump for a Power steering system out.
  • the partial section shown in Figure 1 through the Vane pump 1 shows a pump unit 3 that a rotor 5 and a cam ring 7 surrounding it includes.
  • a rotor 5 In the rotor 5 are in the radial direction running slots 9 introduced into the radial Movable wing 11 are used.
  • the inner contour of the lifting ring 7 is not circular, but approximately elliptical, so that when the rotor rotates, the blades 11 on and off be extended. It becomes subspaces trained which during one revolution of the Enlarge and reduce the rotor so that at least a suction and a pressure area are created.
  • a first Pressure plate 13 On the one side of the pump unit 3 is a first Pressure plate 13 is provided.
  • the pump unit On the other hand can the pump unit on a flat housing surface issue.
  • second pressure plate 15 is provided. That of the pump unit 3 facing surface of the first Pressure plate 13 is concave, as is the Surface 19 of the second pressure plate 15, which the Pump unit 3 is facing.
  • the pressure plates 13 and 15 practically only with their outer edges on the lateral boundary surfaces of the Hubrings 7 on.
  • the one facing away from the rotor 5 Sides of the pressure plates 13, 15 is given pressure low (for example "circulation pressure") or zero, see above that the load on the outer edges of the pressure plates is low.
  • the vane pump 1 acts on the Outer surfaces 21 and 23 of the pressure plates 13 and 15 a high pressure force, such as when the Steering is given. This is shown in FIG Arrows indicated.
  • the width of the cam ring 7 corresponds approximately to that Width of the rotor 5.
  • the wings 11 are slightly narrower than the rotor 5 and Hubring 7. Due to the fact that the pressure plates 13 and 15 under pressure on the pump unit 3 are in the wing 11 given only extremely narrow gaps, so that under high pressure a very good volumetric efficiency results. That is, from the wings subdivided subspaces are optimally opposed to each other sealed, so that from the vane pump conveyed medium only to an extremely low Flow part back from the pressure area to the suction area can. At a low pressure, as shown in Figure 1 was assumed, for example in the case of circulation printing, there is a relatively poor volumetric Efficiency.
  • the deflection of the pressure plates 13, 15 takes place continuously, i.e. evenly with increasing, on the surface facing away from the rotor 5 the pressure applied to the printing plates. As a result of that the pressure plates 13, 15 move freely and without pretension installed, will be jerky Deflection avoided. It is particularly advantageous also that the pressure plates 13, 15 at a high Pressure of the fluid to be pumped with a surface pressure and at a low pressure of the fluid be loaded with an edge pressure. In both Cases are those that act on the printing plates Forces relatively low.
  • the printing plates can remain unencumbered during manufacture a concave surface is worked out, or can be pre-bent to then under defined Preload forces a flat surface to work out the one in the unloaded state concave curvature.
  • Deformation of the pressure plates under operating pressure 13 and 15 can be chosen by the choice of material for the printing plates and by specifying a certain plate thickness can be defined. It is thus possible, a defined behavior of the printing plates to specify in the operating state.
  • the curvature of the surfaces 17 and 19 can be chosen in this way be the deepest in the unloaded state Point of the pressure plates 13 and 15 opposite one imaginary level around 10 ⁇ m to 40 ⁇ m, preferably jumps back by 15 ⁇ m to 30 ⁇ m.

Landscapes

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

Claims (5)

  1. Pompe à palettes (1) comprenant un rotor (5) dans lequel sont logées des ailettes (11) mobiles en direction radiale, un anneau de pompe (7) entourant le rotor et formant au moins une zone d'aspiration et une zone de pression, au moins une plaque de pression (13) qui forme une surface délimitant latéralement les zones d'aspiration et de pression et qui, quand la pompe fonctionne est soumise à une pression sur sa face éloignée des zones d'aspiration et de pression, caractérisée en ce que la surface (17 ;19) de la plaque de pression (13 ; 15) en regard du rotor (5) a une forme concave quand la pompe à palettes (1) est sans pression.
  2. Pompe à palettes selon la revendication 1, caractérisée en ce que de chaque côté du rotor (5) et de l'anneau de pompe (7), il est prévu une plaque de pression (13 ; 15) et la face (19) de la seconde plaque (15) qui est en regard du rotor (5), des ailettes (11), de l'anneau de pompe (7) et des zones d'aspiration et de pression a une forme concave quand la pompe (1) est sans pression.
  3. Pompe à palettes selon l'une des revendications 1 ou 2, caractérisée en ce que le bombé des surfaces concaves (17 ; 19) de la (des) plaque(s) de pression (13 ; 15) est choisi de manière que cette surface (17 ; 19) soit sous pression de service, pratiquement planes.
  4. Pompe à palettes selon l'une quelconque des revendications précédentes, caractérisée en ce que les faces latérales de la (des) plaques (13 ;15) sont essentiellement parallèles.
  5. Pompe à palettes selon l'une quelconque des revendications précédentes, caractérisée en ce que l'anneau de pompe (7) et le rotor (3) ont la même largeur.
EP98920506A 1997-04-15 1998-04-09 Pompe a cellules semi-rotative Expired - Lifetime EP0910746B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19715650 1997-04-15
DE19715650 1997-04-15
PCT/EP1998/002082 WO1998046884A1 (fr) 1997-04-15 1998-04-09 Pompe a cellules semi-rotative

Publications (2)

Publication Number Publication Date
EP0910746A1 EP0910746A1 (fr) 1999-04-28
EP0910746B1 true EP0910746B1 (fr) 2003-03-05

Family

ID=7826545

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98920506A Expired - Lifetime EP0910746B1 (fr) 1997-04-15 1998-04-09 Pompe a cellules semi-rotative

Country Status (6)

Country Link
US (1) US6123532A (fr)
EP (1) EP0910746B1 (fr)
JP (1) JP4094682B2 (fr)
DE (1) DE19880474D2 (fr)
GB (1) GB2329678B (fr)
WO (1) WO1998046884A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0513782U (ja) * 1991-08-02 1993-02-23 エバーコート株式会社 葉書等の通信体
JP2006249944A (ja) * 2005-03-08 2006-09-21 Toyota Motor Corp ベーンポンプ
TWI421481B (zh) * 2011-06-24 2014-01-01 Universal Cement Corp 預壓式壓力感測器模組
CN102777379B (zh) * 2012-05-24 2015-09-09 温岭市大众精密机械有限公司 一种叶片泵配油盘
JP6163111B2 (ja) * 2014-01-21 2017-07-12 株式会社ショーワ ベーンポンプユニット

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2544988A (en) * 1949-03-12 1951-03-13 Vickers Inc Power transmission
US3019737A (en) * 1960-02-12 1962-02-06 Thompson Ramo Wooldridge Inc Leaf spring seal for pumps
US3096720A (en) * 1962-01-02 1963-07-09 Gil W Younger Rotary gear pumps
US3695791A (en) 1970-09-18 1972-10-03 Emerson Electric Co Variable sealed hydraulic pump or motor
US3752609A (en) * 1972-02-17 1973-08-14 Sperry Rand Corp Vane pump with fluid-biased end walls
US4050855A (en) * 1975-02-26 1977-09-27 Nippon Piston Ring Kabushiki Kaisha Dry air rotary pump or compressor
JPS5514783Y2 (fr) * 1975-05-01 1980-04-04
JPS5358807A (en) * 1976-11-09 1978-05-27 Nippon Piston Ring Co Ltd Rotary fluid pump
JPS58133493A (ja) * 1982-02-03 1983-08-09 Diesel Kiki Co Ltd ベ−ン型圧縮機

Also Published As

Publication number Publication date
US6123532A (en) 2000-09-26
DE19880474D2 (de) 1999-09-02
JP2000512714A (ja) 2000-09-26
JP4094682B2 (ja) 2008-06-04
GB2329678B (en) 2001-03-14
GB2329678A (en) 1999-03-31
EP0910746A1 (fr) 1999-04-28
GB9827131D0 (en) 1999-02-03
WO1998046884A1 (fr) 1998-10-22

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