EP0782672B1 - Regeleinrichtung für verdrängerpumpen - Google Patents

Regeleinrichtung für verdrängerpumpen Download PDF

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Publication number
EP0782672B1
EP0782672B1 EP95932754A EP95932754A EP0782672B1 EP 0782672 B1 EP0782672 B1 EP 0782672B1 EP 95932754 A EP95932754 A EP 95932754A EP 95932754 A EP95932754 A EP 95932754A EP 0782672 B1 EP0782672 B1 EP 0782672B1
Authority
EP
European Patent Office
Prior art keywords
piston
channel
bore
choke
spring
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
EP95932754A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0782672A1 (de
Inventor
Konrad Eppli
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen AG
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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Publication of EP0782672A1 publication Critical patent/EP0782672A1/de
Application granted granted Critical
Publication of EP0782672B1 publication Critical patent/EP0782672B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • 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
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids

Definitions

  • the invention relates to a control device for positive displacement pumps, especially vane pumps, the one Have pressure chamber, which has a bore in which a Throttle piston is displaceable against the force of a spring, with a pressure channel connected to an outlet in Connection is established.
  • the throttle piston controls an outlet cross section depending on the pump speed or Flow rate.
  • a rear face of the flow control piston protrudes into a chamber, the downstream of the throttle device the outlet pressure contains.
  • the flow control piston gives depending of the differential pressure acting on the two end faces a connection from the pressure chamber to a pump inlet channel free.
  • Such a control device is from the DE 41 01 210-A1 known.
  • This pump shifts the throttle piston with increasing speed by one a dynamic pressure acting on the front.
  • One cuts Control edge of a piston opening connected to a pressure chamber so that the decreasing passage cross-section flow less and less pressure oil to an outlet leaves.
  • This arrangement represents the throttle device.
  • the differential pressure acts also on the back of the piston of the throttle device.
  • the throttle piston locks with its Front one connected to the pressure chamber or the interior Passage from, what a relatively stiff spring is required. This spring force must start when Pump can be overcome by the delivery pressure. For this reason must be in a double-flow pump in one pressure zone significantly higher pump pressure are built up so that the Pump proportionate due to different pressures runs loudly.
  • the piston is also included as a stepped piston Fit that performed a certain amount of work makes necessary.
  • the invention is based, with as possible low construction costs a control device for a to create falling flow characteristic without the power consumption the pump significantly.
  • the falling Characteristic should also be independent of the opening path and of the differential pressure of the flow control piston to be one Avoid disturbance.
  • the new throttle device is designed so that the pressure chamber in the area of the one containing the throttle piston Drilling via a bypass channel with a spring chamber at all times is connected and the throttle piston cross-section one connecting the spring chamber with the outlet channel Throttle channel controls.
  • the throttle piston begins to move through a narrow bore in the control plate and thus the flow characteristic to influence. Part of the Derive the flow rate to the pressure chamber.
  • the vane pump is used to deliver pressure oil in a container, not shown, to a container, not shown Consumers, for example an auxiliary steering system.
  • a rotor set 3 used in an oil-filled pressure chamber 1 of a housing 2 .
  • the rotor set 3 consists of a cam ring 4 and a rotor 5.
  • the rotor 5 is in Arranged inside the cam ring 4 and has radially directed Slits in which wings 6 can be moved.
  • Working chambers formed by control surfaces adjacent Control plates 7 and 8 are limited in the axial direction.
  • the housing 2 is composed of a bearing housing 10 and a Pot-shaped housing cover 11 assembled.
  • the rotor 5 is mounted in the bearing housing 10 via a drive shaft 12.
  • the bearing point in the bearing housing 10 is the only one Bearing of the drive shaft 12. This means that the Drive shaft 12 in the housing cover 11 in the radial direction is not stored.
  • the drive shaft is supported rather on the housing cover 11 in the axial direction.
  • a flow control valve 13 for the control of the the pressure connection led pressure oil provided.
  • Training the flow control valve 13 and one more existing, not visible pressure relief valve generally known, for example from US-A 5 098 259 and is therefore not described in detail.
  • Suction and pressure channels that connect the working chambers with the suction connection, the flow control valve 13 and the pressure relief valve connect, arranged in the bearing housing 10. Also these channels are well known and are therefore not described in detail.
  • the control plate 7 In a double-flow pump, the control plate 7 two breakthroughs 14 and 14A, which with the between the Rotor 5, the cam ring 4 and the wings 6 formed pressurized working chambers. in the The delivery pressure prevails in pressure chamber 1.
  • On the top Breakthrough 14 axially connects a piston bore 15.
  • the Piston bore 15 contains a throttle piston 17, on the presses a spring 16 inserted into a spring chamber 15A.
  • the pressure chamber 1 is above a bypass channel 18 constantly via the spring chamber 15A and one by the throttle piston 17 controllable throttle channel 20 with an outlet duct 21 leading to the consumer in connection.
  • a chamfer 19 on the throttle piston 17 controls the Throttling.
  • a suction channel 9 is connected to the oil container.
  • the bypass channel 18 is, as from the cross section of FIG Fig. 2 can be seen, poured T-shaped in the bearing housing 10 and with its vertical channel section 18A to the piston bore 15 open. In every position of the Throttle piston 17 therefore remains the connection of the Receive pressure chamber 1 to the outlet channel 21. The throttle piston 17 therefore does not require a snug fit.
  • the differential pressure increases with increasing speed the face of the opening 14A facing the Flow control valve 13 belonging to control piston 22.
  • the control piston 22 acts as a pressure compensator and moves it against the force of a spring 23 and against the force of in a chamber 24 prevailing outlet pressure to the right.
  • the end face of the control piston 22 opens an inlet channel 25. A partial stream thus arrives in a known manner back on the inlet side of the pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP95932754A 1994-09-21 1995-09-15 Regeleinrichtung für verdrängerpumpen Expired - Lifetime EP0782672B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4433598A DE4433598A1 (de) 1994-09-21 1994-09-21 Regeleinrichtung für Verdrängerpumpen
DE4433598 1994-09-21
PCT/EP1995/003629 WO1996009475A1 (de) 1994-09-21 1995-09-15 Regeleinrichtung für verdrängerpumpen

Publications (2)

Publication Number Publication Date
EP0782672A1 EP0782672A1 (de) 1997-07-09
EP0782672B1 true EP0782672B1 (de) 1998-12-02

Family

ID=6528751

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95932754A Expired - Lifetime EP0782672B1 (de) 1994-09-21 1995-09-15 Regeleinrichtung für verdrängerpumpen

Country Status (8)

Country Link
US (1) US5810565A (ko)
EP (1) EP0782672B1 (ko)
JP (1) JPH10505889A (ko)
KR (1) KR100344812B1 (ko)
BR (1) BR9508971A (ko)
DE (2) DE4433598A1 (ko)
ES (1) ES2124589T3 (ko)
WO (1) WO1996009475A1 (ko)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19651386B4 (de) * 1996-12-11 2004-12-16 Zf Friedrichshafen Ag 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
JP3656205B2 (ja) * 1997-06-25 2005-06-08 株式会社日立製作所 パワーステアリング装置用油圧ポンプ
DE19745118B4 (de) * 1997-10-11 2006-10-12 Wabco Gmbh & Co.Ohg Druckerzeugungsanlage
DE19745448C1 (de) * 1997-10-15 1999-01-21 Zahnradfabrik Friedrichshafen Verdrängerpumpe
DE19747341A1 (de) * 1997-10-27 1999-04-29 Zahnradfabrik Friedrichshafen Regeleinrichtung für Verdrängerpumpen
JPH11148480A (ja) * 1997-11-14 1999-06-02 Mitsubishi Heavy Ind Ltd 圧縮機
DE19833373A1 (de) * 1998-07-24 2000-01-27 Zahnradfabrik Friedrichshafen Förderstromregeleinrichtung für Verdrängerpumpen
DE19833700A1 (de) * 1998-07-27 2000-02-03 Zahnradfabrik Friedrichshafen Förderstromregeleinrichtung für Verdrängerpumpen
DE19909963B4 (de) * 1999-03-06 2006-12-21 Zf Friedrichshafen Ag Verdrängerpumpe
DE102006016431A1 (de) * 2006-04-07 2007-10-18 Zf Lenksysteme Gmbh Verdrängerpumpe
CN107867323B (zh) 2016-09-28 2019-11-22 比亚迪股份有限公司 电机油泵总成、转向系统和车辆
CN107867325B (zh) * 2016-09-28 2019-11-05 比亚迪股份有限公司 电机油泵总成、转向系统和车辆
CN107869461B (zh) * 2016-09-28 2019-06-25 比亚迪股份有限公司 电机油泵总成、转向系统和车辆

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2839003A (en) * 1956-02-20 1958-06-17 Thompson Prod Inc Combination flow control and relief valve
JPS5862394A (ja) * 1981-10-08 1983-04-13 Jidosha Kiki Co Ltd オイルポンプ
JP2840087B2 (ja) * 1989-08-29 1998-12-24 株式会社ユニシアジェックス 液体ポンプ
JP2937500B2 (ja) * 1990-01-17 1999-08-23 ツァーンラトファブリック フリードリッヒシャーフェン アクチェンゲゼルシャフト 容積形ポンプ用調整装置
JP2895169B2 (ja) * 1990-06-11 1999-05-24 株式会社ユニシアジェックス ベーンポンプ

Also Published As

Publication number Publication date
DE4433598A1 (de) 1996-03-28
WO1996009475A1 (de) 1996-03-28
US5810565A (en) 1998-09-22
BR9508971A (pt) 1997-11-11
JPH10505889A (ja) 1998-06-09
ES2124589T3 (es) 1999-02-01
KR970705707A (ko) 1997-10-09
EP0782672A1 (de) 1997-07-09
KR100344812B1 (ko) 2002-11-07
DE59504439D1 (de) 1999-01-14

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