EP0125328B1 - Pompe à palettes, en particulier pour servo-assistance - Google Patents

Pompe à palettes, en particulier pour servo-assistance Download PDF

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Publication number
EP0125328B1
EP0125328B1 EP83104769A EP83104769A EP0125328B1 EP 0125328 B1 EP0125328 B1 EP 0125328B1 EP 83104769 A EP83104769 A EP 83104769A EP 83104769 A EP83104769 A EP 83104769A EP 0125328 B1 EP0125328 B1 EP 0125328B1
Authority
EP
European Patent Office
Prior art keywords
insert
duct
valve
vane pump
pump
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
EP83104769A
Other languages
German (de)
English (en)
Other versions
EP0125328A1 (fr
Inventor
Heinz Teubler
Heinz Krüger
René Dr. Dipl.-Ing. Schulz
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 DE8383104769T priority Critical patent/DE3370058D1/de
Priority to EP83104769A priority patent/EP0125328B1/fr
Priority to US06/609,290 priority patent/US4575314A/en
Priority to CA000454154A priority patent/CA1217387A/fr
Priority to JP59096296A priority patent/JPH0689748B2/ja
Publication of EP0125328A1 publication Critical patent/EP0125328A1/fr
Application granted granted Critical
Publication of EP0125328B1 publication Critical patent/EP0125328B1/fr
Priority to JP5086627A priority patent/JPH0658267A/ja
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
    • F04C15/062—Arrangements for supercharging the working space
    • 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 of the preamble of claim 1.
  • channels are provided which extend from an oil storage room to the work rooms and each have a sloping section and a curved, normally horizontally arranged section. These curved sections extend in the axial plane of the rotor and open with their axial legs in current distribution spaces to the work spaces and with their radial legs in a pressurized valve space, from which an outflow jet arises when the associated valve responds.
  • the channels described are essentially symmetrical and arranged. In the illustrated embodiment, the curved sections of the channels have been produced using the casting process.
  • the invention is therefore based on the object of designing a vane pump of the type specified at the outset in such a way that the hydraulic fluid is deflected well in the region of the deflection section, the risk of erosion being avoided.
  • the erosion is avoided in that the plug-shaped insert is thicker than the feed channel in the region of the deflection section and to a certain extent lines the feed channel. If the housing is made of die-cast aluminum, brass or another, less eroding material is used for the plug-shaped use. The transition between the feed channel section, formed by the wall of the die-cast aluminum, and the deflection section, formed by the plug-shaped insert, has been moved to a position which is not hit by the outflow jet.
  • the stopper-shaped insert expediently extends to the inflow channel coming from the tank, in which suction prevails when the valve responds.
  • the first or front step of the stepped bore intersects the suction inflow channel.
  • the front end of the plug-shaped insert is accessible for a special, adapted processing, so that the flow conditions at the transition of the discharge channel of the valve to the suction-inflow channel and further into the curved feed channel can be adapted to a wide range of operating conditions.
  • the vane pump has a main housing part and a housing cover 2, which consist of die-cast aluminum and enclose an interior 1 a pressure-tight.
  • 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 cylindrical in shape, 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 there are two crescent-shaped working areas which are divided by the vanes 8 into a number of cell spaces.
  • the cell spaces increase on the suction side of the system and decrease on the pressure side.
  • the supply of hydraulic fluid takes place from a tank, not shown, into a distribution space 16, from which two approximately vertical bores emerge as inflow channels 17a, 17b and tangentially meet curved feed channels 18a, 18b, the feed channels 18a, 18b in the normally horizontal axis plane of the pump and arranged symmetrically to each other are.
  • the curved feed channels 18a, 18b each have a radial leg which opens into an unloading channel 19a or 19b, while the axial legs encounter inlet openings 20 which penetrate the pressure plate 4 and lead into the respective working spaces of the pump.
  • the hydraulic fluid is discharged via outlet openings 33 through the pressure plate 4 on its rear side into a pressure chamber 35 and from there via a delivery channel 36 to an outer pump outlet 37.
  • a throttle body 38 with a measuring orifice 38a and an auxiliary throttle 38b is located in the delivery channel 36.
  • the auxiliary throttle 38b is connected via a control channel 39 to the spring chamber 47 of a flow control valve 40.
  • This 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 41 has two collar-shaped sealing areas 43 and 44, between which an annular groove 45 extends. When the valve 40 is closed, the discharge channels 19a, 19b meet the annular groove 45.
  • a channel 46 which extends partially radially and partially axially, leads from the annular groove 45 through the slide piston 41 into the valve chamber 47, and the channel 46 is dominated by a cone valve. which responds when a certain permissible pressure in the valve chamber 47 is exceeded and relieves pressure in this chamber, so that the spool 41 acts as a controlled pressure relief valve, as is known. Whether as a flow control valve or as a pressure limiting valve, when activated, the valve 40 assumes the position shown in FIG. 2.
  • a gap is released between the piston collar 43 and the edge of the channel 19a or 19b, through which a powerful outflow jet 50 (FIGS. 3 to 5) shoots, depending on the pressure of the hydraulic fluid in the pressure chamber 35.
  • the outflow jet 50 normally passes obliquely at the mouth of the inlet channel 17a or 17b, so that a suction is created at this junction, through which hydraulic fluid is sucked in from the tank.
  • the outflow jet 50 also has the unpleasant property of scouring out the wall material at the point of impact.
  • the usual aluminum die-cast material for bearing housings is particularly sensitive to cavitation erosion. In the invention, therefore, the impact point is lined with erosion-resistant material, for example made of brass (in particular material no. 20550), bronze or steel.
  • a plug-shaped insert 51 (FIG. 3), 52 (FIG. 4) or 53 (FIG. 5) is provided, which is to be fastened in an associated stepped bore 61 or 62 or 63.
  • Each step bore 61, 62, 63 has a front step 64, a middle step 65 or 66 and a rear step 67 from which an outer bore section 68 extends which, as seen from the valve 40, radially outside the knee-shaped feed channels 18a or 18b is arranged.
  • the inserts 51, 52, 53 each have a press collar 54 with a conical taper 55 in order to insert the bore section 68 and hold it by means of a press fit.
  • a toroidal deflection section 56 is provided along a quarter circle, on which the flow deflection takes place between the radial and axial legs of the curved feed channel 18a or 18b.
  • the front steps 64, 65 are arranged near the center of the inflow channel 17a or 17b, i. H.
  • the plug-shaped insert 51 has a front end 57 which is drawn very far inward and which is cut out in the region of the inflow channel 17a, 17b in order not to hinder the inflow of hydraulic fluid.
  • the deflection channel is designed as a lateral, open groove which extends at the valve-side end 57 in the axial direction of the insert 51 and is designed as a torus at the pump-side end 58. Such a groove can easily be made with a ball mill.
  • the diameter of the unloading channel 19a, 19b is smaller than the groove depth of the insert 51, i. H.
  • FIG. 4 also shows an insert 52 which extends far inwards, the front end 57 of which is designed similarly to that of FIG . This is possible because the pump-side end 58 of the deflection channel is quite easily accessible and a ball mill can be guided along a curve when immersed in the insert 52 to be produced.
  • the ridge 57g can be rounded off comfortably in order to reduce the risk of eddy formation.
  • the rounded degree 57g lies approximately in the radial central plane of the inflow channel 17a or 17b.
  • the insert 53 according to FIG. 5 is somewhat shorter and has a drilled deflection channel, which is produced similarly to the case in FIG. 4.
  • the transition point between insert 53 and the die cast material of the pump housing at step 66 is particularly at risk of erosion; for this reason it is ensured that the outflow jet 50 does not occasionally strike this point.
  • the collar 43 has an undercut 43a which is designed in the shape of a flute in order to effect beam guidance in cooperation with the edge 61.
  • the outflow jet 50 becomes much more parallel to the local axial direction of the Channel 19a or 19b aligned, as is the case in the embodiment of Fig. 3 or 4.
  • the outflow jet 50 therefore hits the wall of the insert 53 much later, practically in the region of curvature of the deflection channel.
  • the preparation of the 'insert 51 is preferably performed by extrusion, while the inserts 52 and 53 are drilled and milled preferably combined, as far as it concerns the manufacture of the deflection channel.
  • the housing 1, which is preferably made of aluminum, can also be produced by die casting in addition to die casting.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (7)

1. Pompe à palettes, en particulier pour direction assistée, présentant les caractéristiques suivantes :
a) dans un carter (1, 2) sont disposés une plaque sous pression (4), une bague formant came (5) et un rotor (7) pour enfermer au moins une zone de travail que des palettes (8) divisent en espaces formant cellule qui, au cours de l'entraînement du rotor (7) par un arbre (9), passent entre des ouvertures d'entrée (20) et des ouvertures de sortie (33) ;
b) des ouvertures de sortie (33) sont reliées à un espace sous pression (35) qui conduit à une soupape (40) qui travaille normalement comme soupape de régulation de débit et fait évacuer dans un canal de décharge (19a, 19b) le liquide hydraulique en excès sous forme d'un jet de décharge (50) ;
c) aux ouvertures d'entrée (20) correspond, par zone de travail de la pompe, un système d'arrivée de liquide hydraulique qui présente un canal d'admission (17a, 17b) présentant une différence de niveau, un canal d'arrivée (18a, 18b) coudé et normalement disposé horizontalement et le canal de décharge (19a, 19b) qui sont reliés l'un à l'autre et se correspondent l'un à l'autre de façon telle que, lors de son impact, le jet de décharge (50) crée un effet de succion dans le canal d'admission (17a, 17b) et vient heurter la paroi du canal d'arrivée (18a, 18b) ; caractérisée
d) en ce qu'un tronçon du canal d'arrivée coudé (18a, 18b) est conçu comme partie d'un alésage à décrochements (61, 62, 63) qui s'étend, depuis la face extérieure du carter, en direction de la soupape (40) et, près du décrochement le plus intérieur (64), se transforme en canal de décharge (19a, 19b) ; et
e) en ce que dans l'alésage à décrochements (61, 62, 63) est fixée une garniture en forme de bouchon (51, 52, 53) dans laquelle est venu de forme un canal de changement de direction qui présente une extrémité côté soupape (57), une extrémité côté pompe (58), ainsi qu'un tronçon de changement de direction (56) disposé entre elles, qui est fabriqué en un matériau résistant à l'érosion et qui habille le point d'impact du jet de décharge (50).
2. Pompe à palettes selon la revendication 1, caractérisée en ce que l'alésage à décrochements (61, 62, 63) présente un tronçon alésé extérieur (68) dans lequel s'étend un collet de la garniture (51, 52, 53) pour ajustement à la presse.
3. Pompe à palettes selon la revendication 1 ou 2, caractérisée en ce que la garniture (51, 52) vient, par son extrémité côté soupape (57), au contact du canal d'admission (17a, 17b).
4. Pompe à palettes selon l'une des revendications 1 à 3, caractérisée en ce que le canal de changement de direction, venu de forme, est conçu sous forme de rainure ouverte latéralement qui s'étend à l'extrémité côté soupape (57) de la garniture (51) dans sa direction axiale et qui présente à son extrémité côté pompe (58) un tore (56) en forme de quart de cercle.
5. Pompe à palettes selon l'une des revendications 1 à 3, caractérisée en ce que le canal de changement de direction, venu de forme, est conçu sous forme d'alésage qui s'étend, à l'extrémité côté soupape (57) de la garniture (52, 53) dans sa direction axiale et qui présente, à son extrémité côté pompe, (58), un tore en forme de quart de cercle (56).
6. Pompe à palettes selon l'une des revendications 1 à 5, caractérisée en ce que l'alésage à décrochements (61, 62, 63) présente trois décrochements et, de façon plus précise, un premier décrochement intérieur (34), un second décrochement, extérieur (67) et un décrochement (65 ou 66) situé entre eux et contre lequel vient s'appliquer l'extrémité côté soupape (57) de la garniture (51, 52, 53).
7. Pompe à palettes selon la revendication 6, caractérisée en ce que la soupape (40) présente un collet (43) avec une contre-dépouille en forme de gorge creuse (43a), de façon qu'à l'ouverture de la soupape (40), en collaboration avec l'arête (61 k) formée entre l'alésage de la soupape et le canal de décharge (19a, 19b) le jet de décharge (50) soit dirigé selon la direction longitudinale de la garniture (53).
EP83104769A 1983-05-14 1983-05-14 Pompe à palettes, en particulier pour servo-assistance Expired EP0125328B1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
DE8383104769T DE3370058D1 (en) 1983-05-14 1983-05-14 Vane pump, especially for power steering
EP83104769A EP0125328B1 (fr) 1983-05-14 1983-05-14 Pompe à palettes, en particulier pour servo-assistance
US06/609,290 US4575314A (en) 1983-05-14 1984-05-11 Deflecting insert for a rotary vane pump
CA000454154A CA1217387A (fr) 1983-05-14 1984-05-11 Pompe centrifuge
JP59096296A JPH0689748B2 (ja) 1983-05-14 1984-05-14 回転羽根ポンプ
JP5086627A JPH0658267A (ja) 1983-05-14 1993-04-14 回転羽根ポンプ

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP83104769A EP0125328B1 (fr) 1983-05-14 1983-05-14 Pompe à palettes, en particulier pour servo-assistance

Publications (2)

Publication Number Publication Date
EP0125328A1 EP0125328A1 (fr) 1984-11-21
EP0125328B1 true EP0125328B1 (fr) 1987-03-04

Family

ID=8190465

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83104769A Expired EP0125328B1 (fr) 1983-05-14 1983-05-14 Pompe à palettes, en particulier pour servo-assistance

Country Status (5)

Country Link
US (1) US4575314A (fr)
EP (1) EP0125328B1 (fr)
JP (2) JPH0689748B2 (fr)
CA (1) CA1217387A (fr)
DE (1) DE3370058D1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4237483C2 (de) * 1992-11-06 2000-12-07 Zahnradfabrik Friedrichshafen Hochdruckpumpe, insbesondere für Hilfskraftlenkungen

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3506458C3 (de) * 1984-04-06 1995-02-09 Zahnradfabrik Friedrichshafen Hochdruckpumpe mit Stromregelventil
JPH02139386U (fr) * 1989-04-24 1990-11-21
DE4138516A1 (de) * 1991-11-23 1993-05-27 Luk Fahrzeug Hydraulik Pumpe
US5567125A (en) * 1995-01-06 1996-10-22 Trw Inc. Pump assembly with tubular bypass liner with at least one projection
DE19513079B9 (de) * 1995-04-07 2004-09-09 Zf Friedrichshafen Ag Flügelzellenpumpe mit Stromregelventil
DE19810318B4 (de) * 1997-03-12 2014-01-16 Ixetic Bad Homburg Gmbh Hydraulikmaschine
GB2332482B (en) * 1997-06-24 2001-10-03 Luk Fahrzeug Hydraulik Pump for conveying a medium
DE60327876D1 (de) * 2002-06-13 2009-07-16 Hino Motors Inc Ölpumpe
JP4932670B2 (ja) * 2007-10-25 2012-05-16 カヤバ工業株式会社 可変減衰弁

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2724335A (en) * 1951-12-14 1955-11-22 Eaton Mfg Co Pumping unit with flow director
US2880674A (en) * 1953-09-11 1959-04-07 Vickers Inc Power transmission
US3366065A (en) * 1967-01-03 1968-01-30 Chrysler Corp Supercharging of balanced hydraulic pump
DE2003184B2 (de) * 1970-01-24 1974-01-17 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Selbsttätiges Durchflußmengenregelventil
DE2219588A1 (de) * 1972-04-21 1973-10-25 Teves Gmbh Alfred Verfahren und vorrichtung zur herstellung von druckmittelkanaelen in gussgehaeusen von hydromaschinen
US4168033A (en) * 1977-07-06 1979-09-18 Rain Bird Sprinkler Mfg. Corp. Two-piece wear-resistant spray nozzle construction
DE3018650A1 (de) * 1980-05-16 1981-11-26 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Hochdruckpumpe mit einem stomregelventil
US4470768A (en) * 1983-01-03 1984-09-11 Sperry Vickers Zweigniederlassung Der Sperry Gmbh Rotary vane pump, in particular for assisted steering

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4237483C2 (de) * 1992-11-06 2000-12-07 Zahnradfabrik Friedrichshafen Hochdruckpumpe, insbesondere für Hilfskraftlenkungen

Also Published As

Publication number Publication date
EP0125328A1 (fr) 1984-11-21
US4575314A (en) 1986-03-11
JPS59218379A (ja) 1984-12-08
DE3370058D1 (en) 1987-04-09
CA1217387A (fr) 1987-02-03
JPH0658267A (ja) 1994-03-01
JPH0689748B2 (ja) 1994-11-14

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