EP0151657A1 - Pompe à palettes, en particulier pour système de puissance assisté - Google Patents

Pompe à palettes, en particulier pour système de puissance assisté Download PDF

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Publication number
EP0151657A1
EP0151657A1 EP84101136A EP84101136A EP0151657A1 EP 0151657 A1 EP0151657 A1 EP 0151657A1 EP 84101136 A EP84101136 A EP 84101136A EP 84101136 A EP84101136 A EP 84101136A EP 0151657 A1 EP0151657 A1 EP 0151657A1
Authority
EP
European Patent Office
Prior art keywords
venturi nozzle
flow
pump
vane pump
hydraulic fluid
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.)
Withdrawn
Application number
EP84101136A
Other languages
German (de)
English (en)
Inventor
Heinz Teubler
René 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.)
Vickers Systems 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 EP84101136A priority Critical patent/EP0151657A1/fr
Priority to CA000472981A priority patent/CA1245100A/fr
Priority to JP60018791A priority patent/JPS60192889A/ja
Publication of EP0151657A1 publication Critical patent/EP0151657A1/fr
Priority to US06/830,254 priority patent/US4637782A/en
Withdrawn legal-status Critical Current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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels

Definitions

  • the invention relates to a vane pump with the features of the preamble of claim 1.
  • the hydraulic fluid discharge system contains a space arranged behind the pressure plate, into which the slide piston of the flow control valve projects, the spring or control chamber of which is connected to the pressure space via a channel including the throttle. If the hydraulic fluid flows through this throttle or outflow bore, depending on the quantity flowing through, a pressure drop arises which is used to control the flow control v & r.tils is used. If the hydraulic flow delivered by the pump is greater than the set quantity of the flow control valve, the differential current is reduced and reaches the pump delivery system. It has been shown, however, that the useful current delivered by the pump is not independent of the drive speed of the pump, namely that the delivered useful current increases with increasing speed.
  • the power steering pump has two working areas, each of which is connected to the liquid drainage system via outlet openings in the pressure plate, a plug-like throttle insert being arranged in front of the one outlet opening, which contains the outflow bore for the regulated flow (useful flow) and depending on the flow through the hydraulic fluid conveys different pressure drop values to the flow control valve, whereby the falling characteristic curve is generated.
  • a certain degree of randomness of the flow around the throttle insert is disadvantageous since the entire pump delivery flow cannot be recorded.
  • the useful power is directed back to the tank via the steering valve.
  • the hydraulic fluid under the so-called dynamic pressure relaxes, which leads to a corresponding loss of performance if the power is not absorbed by the steering.
  • Such a high power consumption does not occur practically in the high speed range because you cannot turn sharply when driving fast.
  • a constant readiness to perform is maintained, the level of which is not required and thus leads to an unnecessary loss of performance.
  • 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 size of the dispensed is reduced N utzstroms in dependence on the speed range of the pump with respect to a desired course can influence, and in particular that at a higher rotational speed of the consideredussie useful current is reduced.
  • the entire pump flow which increases in proportion to the speed of the pump, is passed through the Venturi nozzle and is divided there into the delivered useful flow, which flows through the throttle, and the regulated flow, which reaches the pump feed system.
  • the regulated current at higher speeds is significantly greater than the usable current delivered, the pressure at the narrowest point of the Venturi nozzle drops more and more and thus the pressure in the control chamber of the flow control valve. This opens it relatively more, and the regulated flow increases more than it corresponds to the increase in the pump flow due to the increase in speed.
  • Due to the reduced useful current delivered with increasing speed the dynamic pressure in the steering valve is also reduced, so that the power loss decreases both because of the reduced current and because of the reduced pressure loss compared to previously known pumps.
  • the vane pump has a main housing part 1 and a housing cover 2, which enclose an interior pressure-tight. Sitting in the interior - 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, 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.
  • Hydraulic fluid is supplied from a distribution area (not shown) via two approximately vertical bores 17 (FIGS. 2 and 3), knee-shaped feed channel sections 18 (FIG. 2) and through openings 20 into the respective working areas of the pump.
  • the knee-shaped feed channel sections 18 (FIG. 2) each have a radial leg which opens into an unloading channel 19 (FIGS. 2 and 3).
  • the hydraulic fluid is discharged via channels 33 (FIG. 1) through the pressure plate 4 on its rear side into a pressure chamber 35 and from there into a Venturi nozzle 36.
  • the pump delivery flow is divided into a regulated useful flow to the outer pump outlet 37 and a delivery flow regulated by a flow control valve 40 into the discharge channels 19 (FIG. 3).
  • the regulated N utzstrom passes through an orifice or Throttle 38 in a discharge channel 39 which is connected to the control chamber 47 of the valve 40.
  • the flow control valve 4 0 includes a spool 41 which is urged by the force of a spring 42 in the direction of the venturi 36 and brought to rest there, if appropriate.
  • the slide piston 41 has two collar-shaped sealing areas 43 and 44, between which an annular groove 45 extends.
  • the discharge channels 19 (FIG. 2) meet the annular groove 45.
  • a channel 46 which extends partially radially and partially axially, leads through the slide piston 41 into the control chamber 47, and the channel 46 becomes a cone valve masters, which responds when a certain allowable pressure in the control chamber 47 is exceeded and vented this space, so that the spool 41 acts as a controlled pressure relief valve, as is known.
  • the valve 40 assumes the position shown in FIG.
  • the throttle 38 is arranged at the narrowest point or at least close to this narrowest point of the Venturi nozzle 36.
  • the throttle 38 is designed as a bore and perpendicular to the axis of the venturi 36.
  • the angle a between the axis of the venturi (calculated in the direction of the valve 40) and the axis of the throttle 38 can be changed depending on the desired control characteristic. If a descending characteristic curve (FIG. 4) is desired, an angular range a between 90 and 150 ° can be considered. With increasing angle a, the characteristic curve drops more.
  • the Venturi nozzle 36 can be rotationally symmetrical with respect to its axis; however, one can also choose a shape in which there are as far as possible no dead spots in the flow, ie the Venturi nozzle can be flattened into the plane of the discharge channels 19.
  • the venturi 36 should have a width at its outlet that is almost equal to the diameter of the spool 41. This can be achieved by arranging the Venturi nozzle 36 and the spool 41 in the same bore (here corresponding to the control chamber 47).
  • FIG. 4 shows a diagram of the regulated useful current versus the pump speed, specifically the dot-dash area indicates the control behavior without a Venturi nozzle 36, while the extended region applies to the Venturi nozzle 36.
  • the flow rate initially increases linearly until the response value of the valve 40 is reached at approximately 750 l / min, after which the valve 40 regulates most of the flow rate.
  • the regulated useful current as the rest is offered to the steering valve and leads to a constant loss of performance. With the invention it is possible to safely reduce the regulated useful current with increasing pump speed and thus to achieve a favorable power ratio.
EP84101136A 1984-02-04 1984-02-04 Pompe à palettes, en particulier pour système de puissance assisté Withdrawn EP0151657A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP84101136A EP0151657A1 (fr) 1984-02-04 1984-02-04 Pompe à palettes, en particulier pour système de puissance assisté
CA000472981A CA1245100A (fr) 1984-02-04 1985-01-28 Pompe tournante a aubes
JP60018791A JPS60192889A (ja) 1984-02-04 1985-02-04 回転羽根ポンプ
US06/830,254 US4637782A (en) 1984-02-04 1986-02-18 Rotary vane pump

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP84101136A EP0151657A1 (fr) 1984-02-04 1984-02-04 Pompe à palettes, en particulier pour système de puissance assisté

Publications (1)

Publication Number Publication Date
EP0151657A1 true EP0151657A1 (fr) 1985-08-21

Family

ID=8191751

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84101136A Withdrawn EP0151657A1 (fr) 1984-02-04 1984-02-04 Pompe à palettes, en particulier pour système de puissance assisté

Country Status (4)

Country Link
US (1) US4637782A (fr)
EP (1) EP0151657A1 (fr)
JP (1) JPS60192889A (fr)
CA (1) CA1245100A (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998059172A1 (fr) * 1997-06-24 1998-12-30 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pompe pour refouler une substance
KR101228190B1 (ko) * 2010-05-25 2013-01-30 성균관대학교산학협력단 지능형 최소 침습 수술 도구

Families Citing this family (9)

* 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
US5033265A (en) * 1989-03-08 1991-07-23 Sundstrand Corporation Coaxial hydraulic actuator system
JPH0350587U (fr) * 1989-09-26 1991-05-16
DE4416077A1 (de) * 1994-05-06 1995-11-09 Zahnradfabrik Friedrichshafen Flügelzellenpumpe
JP3771675B2 (ja) * 1997-06-24 2006-04-26 株式会社日立製作所 容積型ポンプの流量制御装置
JP3861594B2 (ja) * 2000-12-15 2006-12-20 ユニシア ジェーケーシー ステアリングシステム株式会社 オイルポンプ
US7793416B2 (en) 2006-05-15 2010-09-14 Viking Pump, Inc. Methods for hardening pump casings
US8333576B2 (en) * 2008-04-12 2012-12-18 Steering Solutions Ip Holding Corporation Power steering pump having intake channels with enhanced flow characteristics and/or a pressure balancing fluid communication channel
CN109555640B (zh) * 2018-11-22 2020-04-03 张薇薇 一种带有文丘里管的液压马达

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2340196A (en) * 1941-06-16 1944-01-25 Houdaille Hershey Corp Rotary hydraulic pump and pressure control valving therefor
US3415194A (en) * 1966-09-16 1968-12-10 Eaton Yale & Towne Pump
DE1528973A1 (de) * 1951-01-28 1969-09-25 Bosch Gmbh Robert Verdraengerpumpe
DE2001614A1 (de) * 1970-01-15 1971-07-22 Zahnradfabrik Friedrichshafen Stromregeleinrichtung fuer eine Hydraulikpumpe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3384020A (en) * 1966-07-29 1968-05-21 Eaton Yale & Towne Pump
US4199304A (en) * 1978-03-13 1980-04-22 Ford Motor Company Positive displacement compact slipper pump
US4470768A (en) * 1983-01-03 1984-09-11 Sperry Vickers Zweigniederlassung Der Sperry Gmbh Rotary vane pump, in particular for assisted steering

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2340196A (en) * 1941-06-16 1944-01-25 Houdaille Hershey Corp Rotary hydraulic pump and pressure control valving therefor
DE1528973A1 (de) * 1951-01-28 1969-09-25 Bosch Gmbh Robert Verdraengerpumpe
US3415194A (en) * 1966-09-16 1968-12-10 Eaton Yale & Towne Pump
DE2001614A1 (de) * 1970-01-15 1971-07-22 Zahnradfabrik Friedrichshafen Stromregeleinrichtung fuer eine Hydraulikpumpe

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998059172A1 (fr) * 1997-06-24 1998-12-30 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Pompe pour refouler une substance
GB2332482A (en) * 1997-06-24 1999-06-23 Luk Fahrzeug Hydraulik Pump for conveying a medium
US6164922A (en) * 1997-06-24 2000-12-26 Luk Fahrzeug-Hydraulik Gmbh & Co. Kg Flow control valve for a pump for conveying a medium
GB2332482B (en) * 1997-06-24 2001-10-03 Luk Fahrzeug Hydraulik Pump for conveying a medium
KR101228190B1 (ko) * 2010-05-25 2013-01-30 성균관대학교산학협력단 지능형 최소 침습 수술 도구

Also Published As

Publication number Publication date
CA1245100A (fr) 1988-11-22
US4637782A (en) 1987-01-20
JPS60192889A (ja) 1985-10-01

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PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

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AK Designated contracting states

Designated state(s): DE FR GB IT SE

17P Request for examination filed

Effective date: 19860217

17Q First examination report despatched

Effective date: 19870506

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18W Application withdrawn

Withdrawal date: 19870925

RIN1 Information on inventor provided before grant (corrected)

Inventor name: TEUBLER, HEINZ

Inventor name: SCHULZ, RENE