EP0499794A1 - Pompe hydraulique - Google Patents

Pompe hydraulique Download PDF

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Publication number
EP0499794A1
EP0499794A1 EP92100785A EP92100785A EP0499794A1 EP 0499794 A1 EP0499794 A1 EP 0499794A1 EP 92100785 A EP92100785 A EP 92100785A EP 92100785 A EP92100785 A EP 92100785A EP 0499794 A1 EP0499794 A1 EP 0499794A1
Authority
EP
European Patent Office
Prior art keywords
pressure
chamber
control
delivery
pressure chamber
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.)
Granted
Application number
EP92100785A
Other languages
German (de)
English (en)
Other versions
EP0499794B1 (fr
Inventor
Rolf Dr. Klumpp
Claus-Peter Höptner
Uwe Matena
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.)
Daimler Benz AG
Original Assignee
Daimler Benz AG
Mercedes Benz 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 Daimler Benz AG, Mercedes Benz AG filed Critical Daimler Benz AG
Publication of EP0499794A1 publication Critical patent/EP0499794A1/fr
Application granted granted Critical
Publication of EP0499794B1 publication Critical patent/EP0499794B1/fr
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
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • F04C14/06—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations specially adapted for stopping, starting, idling or no-load operation
    • F04C14/065—Capacity control using a multiplicity of units or pumping capacities, e.g. multiple chambers, individually switchable or controllable

Definitions

  • the invention relates to a hydraulic pump with a first pump, which draws from a common suction chamber into a first chamber forming the pressure outlet of the hydraulic pump, and a second pump, which draws into a second chamber, according to the preamble of patent claim 1.
  • Such a hydraulic pump is known from DE-A-38 37 599.
  • the problem on which the invention is based is to make this known pump structurally simpler and thereby achieve less expensive production.
  • a generic hydraulic pump with the characterizing features of claim 1 represents a solution to the problem according to the invention.
  • an oil pump is already known from DE-A-31 42 604, in which two pump units either deliver from a common suction chamber into a common pressure outlet or separate pressure outlets and have a one-way valve connecting the two pressure outlets to one another.
  • that oil pump cannot be compared with the invention, since the one-way valve there has a different function.
  • the one-way valve according to the invention ensures that the flow rates of both pump units below a first delivery pressure limit value prevailing at the pressure outlet are directed into a common pressure outlet of the pump, the one-way valve of the previously known device is switched and controlled in such a way that it only rises above a preset delivery pressure at the pressure outlet the pump can open while it is kept closed by a control valve at a delivery pressure below this limit.
  • the two feed pumps are not intended to deliver to a common pressure output at a low delivery pressure at the pump outlet, but rather at a high delivery pressure at the pump outlet, that pump has an entirely different type of control and Switch mechanism on, whereby the structure and function of the necessary valve controls in both cases are not comparable.
  • two jointly driven circulation displacers 1 and 2 work, of which the circulation displacer 1 promotes a primary and the circulation displacer 2 a secondary flow.
  • Both circulation displacers 1, 2 deliver from a common suction chamber 3.
  • the circulation displacer 1 delivers into a first chamber 4 and the circulation displacer 2 into a second chamber 5.
  • the first chamber 4 opens directly into the pressure outlet 6 of the hydraulic pump.
  • the two chambers 4 and 5 are connected to one another by a one-way valve 7 opening in the direction of the first chamber 4.
  • the suction chamber 3 can be connected to the second chamber 5 via a first control valve 8 and also to the first pressure chamber via a second control valve 9.
  • the second control valve 9 is expediently designed as a throttle valve.
  • the two valves 8 and 9 are actuated via a control slide 10 which is guided in a bore 11 of the hydraulic pump. On one end, the control slide is acted upon by a spring 12 in its longitudinal axis. This end face is exposed to the pressure of the suction chamber 3. The opposite end face of the control slide is exposed to the pressure of the first chamber 4.
  • the control valves 8 and 9 are actuated by control pistons 13 and 14, which are part of the control slide 10.
  • the control piston 13 is part of the valve 9 and the control piston 14 is part of the valve 8.
  • the two control pistons 13 and 14 additionally also perform the function of those guided in the bore 11 Piston.
  • the control piston 13 is connected to the first chamber 4 via a channel 15.
  • the spring-loaded control piston 14 borders with its one end face to the second chamber 5 and with its other end face to a damping chamber 17 which is connected to the suction chamber 3 via a throttle bore 16.
  • the delivery pressure at the pressure outlet of the hydraulic pump is below a predetermined first delivery pressure limit, at which the secondary delivery flow leaves the pressure outlet 6 of the delivery pump together with the primary delivery flow.
  • the one-way valve 7 connecting these two chambers is opened.
  • the control valves 8 and 9 are closed in this working state of the pump.
  • the flow rates of the two rotary displacers 1 and 2 are each hatched differently, with a distinction also being made between pressure conditions on the pressure and suction side. As far as the flow rates are connected to each other on the pressure side at the same pressure level, both flow rates are marked identically.
  • the second control valve 9 is also open. Through this control valve 9, a partial flow of the primary delivery flow of the first circulation displacer 1, which is to be returned to the suction chamber, flows in a pressure-throttled manner.
  • the control valve 9 is designed as a throttle valve so that the necessary pressure difference between the pressure output 6 of the hydraulic pump and the suction chamber 3, which are connected to one another via the valve 9, is maintained.
  • the hydraulic pump described is preferably intended and suitable for conveying lubricating oil into the lubricating oil circuit of an internal combustion engine.
  • the hydraulic pump In the working position according to FIG. 2, the hydraulic pump is in such an application when the internal combustion engine is switched off.
  • the delivery flows of the two rotary displacers 1 and 2 are initially supplied together on the pressure side to the lubricating oil circuit.
  • This common supply of both flow rates is necessary in the start and idle phase of the engine at the low speeds prevailing there and the associated low flow rate. It is too notice that both rotary displacers 1 and 2 are driven on a common shaft at the same speed.
  • the purpose of the pressure-relieved return of individual partial flows of the hydraulic pump is to avoid performance losses of the pump at high speeds, which inevitably result from unnecessarily high flow rates working against pressure.
  • the rotary displacers which can be used for the invention can be of any type, and they can be elements of a gear, trochoid, sickle, Eaton, screw or vane pump, for example.
EP92100785A 1991-02-19 1992-01-18 Pompe hydraulique Expired - Lifetime EP0499794B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4105030A DE4105030C2 (de) 1991-02-19 1991-02-19 Zahnradpumpe zur Förderung von Schmieröl in einer Brennkraftmaschine
DE4105030 1991-02-19

Publications (2)

Publication Number Publication Date
EP0499794A1 true EP0499794A1 (fr) 1992-08-26
EP0499794B1 EP0499794B1 (fr) 1994-04-06

Family

ID=6425335

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92100785A Expired - Lifetime EP0499794B1 (fr) 1991-02-19 1992-01-18 Pompe hydraulique

Country Status (4)

Country Link
US (1) US5211544A (fr)
EP (1) EP0499794B1 (fr)
JP (1) JP2528415B2 (fr)
DE (1) DE4105030C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0745774A2 (fr) * 1995-05-30 1996-12-04 MAGNETI MARELLI S.p.A. Pompe à débit variable

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19745118B4 (de) * 1997-10-11 2006-10-12 Wabco Gmbh & Co.Ohg Druckerzeugungsanlage
US6161515A (en) * 1998-07-29 2000-12-19 Borgwarner Inc. Method for controlling output pressure of an engine oil pump
US6082321A (en) * 1998-07-29 2000-07-04 Borgwarner Inc. Method for controlling output pressure of an engine oil pump
US6761544B2 (en) * 2001-04-09 2004-07-13 Schlumberger Technology Corporation Lubrication system for downhole application

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3837599A1 (de) * 1988-11-05 1990-05-10 Daimler Benz Ag Zahnradpumpe mit zwei im pumpengehaeuse nebeneinander angeordneten zahnradpaaren

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2512432A1 (de) * 1975-03-21 1976-09-30 Zahnradfabrik Friedrichshafen Ventil fuer hydrauliksysteme
US4245964A (en) * 1978-11-08 1981-01-20 United Technologies Corporation Efficiency fluid pumping system including sequential unloading of a plurality of pumps by a single pressure responsive control valve
US4412789A (en) * 1980-10-31 1983-11-01 Jidosha Kiki Co., Ltd. Oil pump unit
US4502845A (en) * 1983-03-24 1985-03-05 General Motors Corporation Multistage gear pump and control valve arrangement
JPS6123485U (ja) * 1984-07-18 1986-02-12 東京部品工業株式会社 調量回路を設けた歯車ポンプ
DE3608469A1 (de) * 1986-03-14 1987-10-01 Bosch Gmbh Robert Hydraulikanlage
JPS6441607U (fr) * 1987-09-07 1989-03-13
US5087177A (en) * 1989-10-31 1992-02-11 Borg-Warner Automotive, Inc. Dual capacity fluid pump

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3837599A1 (de) * 1988-11-05 1990-05-10 Daimler Benz Ag Zahnradpumpe mit zwei im pumpengehaeuse nebeneinander angeordneten zahnradpaaren

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0745774A2 (fr) * 1995-05-30 1996-12-04 MAGNETI MARELLI S.p.A. Pompe à débit variable
EP0745774A3 (fr) * 1995-05-30 1997-06-04 Magneti Marelli Spa Pompe à débit variable

Also Published As

Publication number Publication date
US5211544A (en) 1993-05-18
JP2528415B2 (ja) 1996-08-28
JPH0579471A (ja) 1993-03-30
DE4105030A1 (de) 1992-08-20
EP0499794B1 (fr) 1994-04-06
DE4105030C2 (de) 1994-11-24

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