EP0068035B1 - Pompe à palettes en particulier pour direction assistée - Google Patents

Pompe à palettes en particulier pour direction assistée Download PDF

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Publication number
EP0068035B1
EP0068035B1 EP19810104981 EP81104981A EP0068035B1 EP 0068035 B1 EP0068035 B1 EP 0068035B1 EP 19810104981 EP19810104981 EP 19810104981 EP 81104981 A EP81104981 A EP 81104981A EP 0068035 B1 EP0068035 B1 EP 0068035B1
Authority
EP
European Patent Office
Prior art keywords
flow
rotor
cam ring
inlet
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
Application number
EP19810104981
Other languages
German (de)
English (en)
Other versions
EP0068035A1 (fr
Inventor
Erwin Konz
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.)
Cessione luk Fahrzeug - Hidraulik & Co KG GmbH
Original Assignee
Vickers Systems 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 Vickers Systems GmbH filed Critical Vickers Systems GmbH
Priority to DE8181104981T priority Critical patent/DE3174238D1/de
Priority to EP19810104981 priority patent/EP0068035B1/fr
Publication of EP0068035A1 publication Critical patent/EP0068035A1/fr
Application granted granted Critical
Publication of EP0068035B1 publication Critical patent/EP0068035B1/fr
Expired 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
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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

Definitions

  • the invention relates to a vane pump with the features a) to d) of claim 1.
  • the cam ring also forms an outer part of the housing and has two through bores beyond the diameter range of the pressure plate.
  • Each through-hole is flanked by two pockets, each of which extends radially inward in one housing half and whose respective front end forms the first and second inlet opening to the working areas of the pump.
  • the front pocket in the direction of flow forms a current distribution space in its radially outer region, while the radially inner region forms a continuation and deflection channel, at the end of which the first inlet opening lies.
  • the current distribution space thus does not open directly into the first inlet opening.
  • the continuation and deflection channel touches the pressure plate in an edge recess.
  • a supply channel from the oil reservoir to branching supply channels is provided, which open at their ends in inlet kidneys, in which one Current distribution takes place in such a way that a partial flow passes through a cam ring channel and a blind bore in the pressure plate to the side of the rotor opposite the inlet kidney and can contribute to filling the respective working area.
  • a disadvantage of the known design is the asymmetrical supply of the hydraulic fluid to the two inlet kidneys, one of which favors the inertia of the inlet flow, while the other is disadvantaged. As a result, the speed of the pump cannot be very high in order to avoid the risk of cavitation and excessive noise.
  • the feed channels favor one working area and leave the other working area in the flow shadow, so that when the number of revolutions increases, there is a risk of cavitation and excessive noise.
  • the invention solves the problem of providing a vane pump of the type specified at the outset with a smaller overall volume, with an even more uniform filling of the two working areas being achieved.
  • a power steering pump built according to the invention for pressures in the range from 65 to 82 bar had a total weight that was 400 to 450 g lower than a power steering pump of the same power available on the market.
  • the vane pump has a main housing part 1 and a housing cover 2, which enclose an interior 1a in a pressure-tight manner.
  • an interior 1a sit - arranged fixed to the housing - a pressure plate 4 and a cam ring 5, which are secured against rotation by pins 6.
  • a rotor 7 is arranged within the cam ring 5 and between the housing cover 2 and the pressure plate 4 and has a number of radial guide slots. Wings 8 are radially displaceably mounted within these guide slots.
  • the rotor 7 can be driven via a shaft 9 which is mounted in a bearing bore in the housing cover 2.
  • the rotor 7 is cylindrically shaped, while the cam ring 5 has an approximately oval inner contour, the small axis of which corresponds approximately to the diameter of the rotor 7, while the large axis determines the extension length of the vanes 8.
  • the cam ring 5 and the rotor 7 are two crescent-shaped work areas 11 and 12, which are divided into a number of cell spaces by the vanes 8. The cell spaces increase on the suction side of the system and decrease on the pressure side.
  • the supply of hydraulic fluid to the respective suction side is as follows: Recirculated hydraulic Liquid is passed below a reservoir 14 into a filter chamber 15, from where the liquid enters an oil reservoir 16, which surrounds the cam ring 5, the rotor 7, the pressure plate 4 and their housing support walls in a semicircular shape.
  • Two feed channels 17a, 18a and 17b, 18b each comprise a vertical section, formed by bores 17a and 17b, and a horizontal, knee-shaped section 18a and 18b, respectively. With their knee-shaped sections 18a, 18b, the feed channels lie essentially in the horizontal axis plane (FIG. 2) and are arranged symmetrically to one another.
  • the radial legs of the feed channels 18a, 18b open into a valve chamber 19 aligned with the shaft 9, while the axial legs each meet through openings 20 of the pressure plate 4.
  • Circumferential seals 21 seal the gap between the back of the pressure plate 4 and the housing wall 1.
  • the through openings 20 expand towards the front of the pressure plate 4 and form a curved, elongated current distribution space 22 which extends in the circumferential direction and in which current is divided.
  • a radially inner branch stream 23 passes through the radially inner part of the through opening 20 and the current distribution space 22 directly via a first inlet 27 into the working area 11 or 12 between the cam ring 5 and the rotor 7, while a radially outer branch stream 24 passes through the radially outer part of the through opening 20 and the current distribution space 22 flows.
  • Three bores 25 in the cam ring form a cam ring channel which runs in the axial direction and meets a housing groove 26 which directs the branch flow 24 radially inwards.
  • the housing groove 26 is widened at its radially inner end in the circumferential direction and there forms a second inlet 28 into the working area of the pump.
  • Arc-shaped grooves 31, 32 are provided in the housing cover 2 and in the pressure plate 4 on both sides of the wings 8.
  • the grooves 31 are each connected via holes 33 (FIG. 4) through the cam ring 5 to the grooves 32 (FIG. 1).
  • the grooves 32 each include a bore through the pressure plate 4.
  • a throttle body 38 with a measuring orifice 38a and an auxiliary throttle 38b is located in the delivery line 36.
  • the auxiliary throttle 38b is connected to a flow control valve 40 via a channel 39.
  • the flow control valve 40 has a slide piston 41, which is pushed by the force of a spring 42 in the direction of the back of the pressure plate 4.
  • the slide piston has two sealing areas 43, 44, between which there is an annular groove 45, into which the feed channels 17a, 18a and 17b, 18b normally open.
  • a partially radially and partially axially extending channel 46 leads from the annular groove 45 through the slide piston 41 into a valve chamber 47, into which the channel 39 opens and in which the spring 42 lies.
  • a spring 48 and a valve cone 49 are arranged within the channel 46.
  • the operation of the power steering pump proceeds as follows: by driving the shaft 9, the rotor 7 is rotated and the vanes 8 are thus guided through the sickle-shaped working areas 11, 12. Hydraulic fluid is drawn in, which can enter both flanks of the wings 8, as shown by the branch flows 23 and 24 in FIG. 3. The feed takes place in the same way for both work areas 11, 12 via the essentially symmetrical feed channels 17a, 18a and 17b, 18b. As a result of this “parallel feeding”, an equal distribution of the filling pressure in both working areas 11, 17 is achieved. This has a noise-reducing effect due to the avoidance of cavitation.
  • the suctioned hydraulic fluid is displaced into the pressure area by the vanes 8 and reaches the pressure chamber 35 via the outlet channels 31, 32 and from there via the delivery channel 36 and the throttle body 38 to the outer pump outlet 37. If more hydraulic fluid is conveyed than the measuring orifice 38a coped with, the pressure in the pressure chamber 35 rises, and the slide piston 41 is pushed against the force of the spring 42 until the sealing surface 43 partially reaches beyond the mouth of the feed channels 17a, 18a, 17b, 18b. With this current control, a direct connection between the pressure chamber 35 and the feed channels is created, which is extremely short, so that the regulated hydraulic fluid is circulated with little energy loss.
  • valve cone 49 lifts off, so that the pressure in the valve chamber 47 drops and the slide piston 41 is displaced to the right in the drawing. This in turn creates the direct connection between the pressure chamber 35 and the supply channels 17a, 18a, 17b, 18b (function as a pressure relief valve).
  • the surrounding wall parts Due to the arrangement of the pressure chamber 35 centrally in the housing 1, the surrounding wall parts have a good sound-insulating effect, in particular because the flow control valve 40 is also aligned with the axis of the rotor 7 and the pressure plate 4.
  • the housing cover 2 is made of aluminum, on the one hand to save weight and on the other hand to offer a good running surface.
  • a stiffening rib 3 is used to receive a leak oil hole 3a, which leads the leak oil creeping along the shaft 9 back into the reservoir 16. Due to the existence of the storage space 16, the size of the storage container 14 can be reduced accordingly, whereby the size and weight of the overall pump can also be saved.

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 (4)

1. Pompe à palettes pour liquide hydraulique, en particulier pour direction assistée, présentant les caractéristiques suivantes;
a) un carter (1, 2) avec une came annulaire (5) qui y est fixée entoure une plaque de pression (4) et un rotor (7) qui définit l'axe de la pompe, en laissant libres deux zones de travail (11, 12) partagées par des palettes (8) en cellules qui, du fait de l'entrainement du rotor (7) par un arbre (9), se déplacent entre une première ouverture d'entrée et une seconde ouverture d'entrée (27, 28) disposées sur des côtés différents du rotor et entre une première ouverture de sortie et une seconde ouverture de sortie (31,32) également disposées sur des côtés différents du rotor, pour chacune des zones de travail (11, 12);
b) à chaque zone de travail (11, 12) conduit un canal d'entrée qui, par l'intermédiaire d'une chambre de répartition de débit (22), bifurque vers la première ouverture d'entrée (27) et la seconde ouverture d'entrée (28), étant précisé que chaque chambre de répartition du débit présente une zone radialement extérieure et une zone radialement intérieure et que la zone radialement extérieure conduit, en passant par un canal (25) dans la came annulaire et un canal de changement de direction (26), à la seconde ouverture d'entrée (28);
c) depuis les zones de travail (11, 12), les ouvertures de sortie (31, 32) conduisent sur la face arrière, côté opposé au rotor, de la plaque de pression (4) dans une chambre sous pression (35), étant précisé que la face avant, côté du rotor, de la plaque sous pression (4) s'appuie de façon étanche contre le rotor (7) et contre la came annulaire (5);
d) les canaux d'entrée sont disposés essentiellement symmétriquement l'un par rapport à l'autre, étant précisé que chaque canal d'entrée présente un premier tronçon de canal d'arrivée (17a, 17b) et un secon tronçon de canal d'arrivée (18a, 18b) coudé et comportant une aile axiale et une aile radiale; que les premiers tronçons de canal d'arrivée (17a, 17b) sont dans un plan qui court à-peu-près perpendiculairement à l'axe de la pompe et que les seconds tronçons de canal d'arrivée (18a, 18b) s'étendent dans un plan passant par l'axe de la pompe et débouchent, par leur aile axiale, dans les chambres de répartition de débit (22) ainsi que, par leur aile radiale, dans une chambre (19) d'où, lorsque réagit un robinet à soupape (40), se produit une évacuation du liquide hydraulique;

caractérisée par les mesures suivantes:
e) chaque tronçon de canal d'arrivée coudé (18a, 18b) débouche respectivement, par son aile axiale, dans une ouverture de passage (20) correspondante, qui traverse la plaque de pression (4), qui est étanche sur la face arrière de la plaque de pression (4), vis-à-vis de la chambre sous pression (35), au moyen de garnitures périphériques (21) et qui abrite respectivement l'une des chambres (22) de répartition du débit,
f) chaque chambre de répartition du débit (22) débouche, par sa zone radialement intérieure, directement dans la première ouverture d'entrée (27).
2. Pompe à palettes selon la revendication 1, caractérisée en ce que chaque canal dans la came annulaire (25) est formé par des alésages dans la came annulaire (5), disposés l'un à côté de l'autre et s'étendant en direction axiale.
3. Pompe à palettes selon la revendication 1 ou la revendication 2, caractérisée en ce que les seconds tronçons de canal d'arrivé coudés (18a, 18b) ont une forme telle que l'on obtient une répartition égale de la pression de remplissage dans les deux zones de travail (11, 12).
4. Pompe à palettes selon l'une des revendications 1 à 3, caractérisée en ce que les ouvertures de sortie (31, 32) d'une zone de travail (11 ou 12) sont reliées l'une à l'autre par l'intermédiaire d'un alésage (33) dans la came annulaire (5), l'une des ouvertures de sortie (32) étant conçue comme chambre de confluence des débits.
EP19810104981 1981-06-26 1981-06-26 Pompe à palettes en particulier pour direction assistée Expired EP0068035B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8181104981T DE3174238D1 (en) 1981-06-26 1981-06-26 Vane pump, especially for power steering
EP19810104981 EP0068035B1 (fr) 1981-06-26 1981-06-26 Pompe à palettes en particulier pour direction assistée

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19810104981 EP0068035B1 (fr) 1981-06-26 1981-06-26 Pompe à palettes en particulier pour direction assistée

Publications (2)

Publication Number Publication Date
EP0068035A1 EP0068035A1 (fr) 1983-01-05
EP0068035B1 true EP0068035B1 (fr) 1986-04-02

Family

ID=8187788

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19810104981 Expired EP0068035B1 (fr) 1981-06-26 1981-06-26 Pompe à palettes en particulier pour direction assistée

Country Status (2)

Country Link
EP (1) EP0068035B1 (fr)
DE (1) DE3174238D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007039172A1 (de) 2007-06-05 2008-12-11 Robert Bosch Gmbh Flügelzellenpumpe

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3623421A1 (de) * 1986-07-11 1988-01-14 Vickers Systems Gmbh Lenkhilfpumpe
US6149409A (en) * 1999-08-02 2000-11-21 Ford Global Technologies, Inc. Cartridge vane pump with dual side fluid feed and single side inlet
DE102014106427A1 (de) * 2014-05-08 2015-11-12 Technische Universität Dresden Verfahren und Vorrichtung zur Herstellung von Formteilen aus einer Faserwerkstoffbahn

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2800083A (en) * 1951-11-07 1957-07-23 Vickers Inc Power transmission
US2880674A (en) * 1953-09-11 1959-04-07 Vickers Inc Power transmission
DE1553020A1 (de) * 1964-01-02 1970-10-22 Breinlich Dr Richard Drehfluegelmaschine mit einer verbesserten Steuerung der Zufuehrung und Abfuehrung des Fluidums
FR1536836A (fr) * 1967-09-15 1968-08-16 Hobourn Eaton Mfg Co Ltd Pompe rotative
US3632238A (en) * 1969-09-05 1972-01-04 Eaton Yale & Towne Pump assembly

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007039172A1 (de) 2007-06-05 2008-12-11 Robert Bosch Gmbh Flügelzellenpumpe

Also Published As

Publication number Publication date
EP0068035A1 (fr) 1983-01-05
DE3174238D1 (en) 1986-05-07

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