EP0761970A1 - Kompakte elektrohydraulische Einheit - Google Patents

Kompakte elektrohydraulische Einheit Download PDF

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Publication number
EP0761970A1
EP0761970A1 EP96401657A EP96401657A EP0761970A1 EP 0761970 A1 EP0761970 A1 EP 0761970A1 EP 96401657 A EP96401657 A EP 96401657A EP 96401657 A EP96401657 A EP 96401657A EP 0761970 A1 EP0761970 A1 EP 0761970A1
Authority
EP
European Patent Office
Prior art keywords
electro
unit according
pump body
pump
hydraulic unit
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
EP96401657A
Other languages
English (en)
French (fr)
Other versions
EP0761970B1 (de
Inventor
Jean-Yves Ollivier Vourc'h
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.)
Hydroperfect International Inc
Original Assignee
Hydroperfect International Inc
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=9482168&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0761970(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Hydroperfect International Inc filed Critical Hydroperfect International Inc
Publication of EP0761970A1 publication Critical patent/EP0761970A1/de
Application granted granted Critical
Publication of EP0761970B1 publication Critical patent/EP0761970B1/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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • 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
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses

Definitions

  • the invention relates to electro-hydraulic groups in which an electric motor drives a hydraulic pump for supplying circuits of various uses.
  • the invention relates more particularly to an electro-hydraulic group intended to supply hydraulic receivers of the type used in the automobile industry and in particular for assisting the management of these vehicles.
  • the embodiment of the invention relates more particularly to so-called compact groups which are sealed groups in which the assembly, hydraulic pump and motor, is contained in a sealed envelope also serving as a fluid reservoir.
  • the invention aims to reduce, even eliminate, the noise resulting from the operation of an electro-hydraulic group and provides that in the event of a breakdown of the vehicle's electrical circuit the presence of the electro-hydraulic control group does not not prevent free operation of the servo circuit, in particular of the vehicle steering circuit.
  • the compact electro-hydraulic group in which an electric motor drives a hydraulic pump, the pump body of which has cavities for damping sound waves partially surrounding at least the cavity containing the pump pinions is characterized in that at least some of the cavities communicate, by a lateral face of the pump body, with a chamber of a cover leading to a fitting of the operating circuit.
  • Fig. 1 is a partially schematic partial sectional elevation of the compact electro-hydraulic group of the invention, the section being taken along line I-I of FIG. 4.
  • Fig. 2 is a section, similar to FIG. 1, but seen along line II-II of FIG. 4.
  • Fig. 3 is a section similar to the previous figures but taken along line III-III of FIG. 4.
  • Fig. 4 is a section seen along line IV-IV of FIG. 1.
  • Fig. 5 is a section seen substantially along the plane V of FIG. 1.
  • Fig. 6 is a view similar to FIG. 5 but illustrating an additional characteristic of the invention.
  • Fig. 7 is a partial sectional elevation similar to FIG. 3 of the pump of the electro-hydraulic group illustrating a development of the invention.
  • the motor-pump unit comprises an electric motor 1 of which only the casing is silhouetted and a hydraulic pump 2 of which the input shaft 3 is driven by the motor 1 by means of a coupling 4.
  • the input shaft 3 as well as the driven shaft 5 of the pump 2 are mounted in bearings 6, 7 movable relative to the shafts 3 and 5 above by a device called hydrostatic compensation of which only linings 8 are represented.
  • the shafts 3 and 5 are provided with engaged pinions 9, 10 housed in a cavity 11 of the pump body 12.
  • the pump body 12 is made in a single piece, for example of aluminum alloy, and has, on either side of the cavity 11, two through holes 13, 14 for the installation of tightening bolts 15 now side cheeks 16, 17 against the two faces of the pump body 12, that is to say ensuring the cohesion of the pump outside of the assembly of the latter to the motor.
  • the side cheeks are made of material with a high modulus of elasticity, for example steel, in order to have a thickness as small as possible taking into account the forces which they have to bear.
  • Fig. 3 shows that the tightening bolts 15 ensure the junction not only of the cheeks 16, 17 on either side of the body 12 as well as the fixing of a cover 18 delimiting, opposite the cheek 17, a chamber 19 in which the fluid under high pressure, driven back by the pistons 9, 10, is brought through a lumen 20 of the cheek 17.
  • the cheek 16 held by the tightening bolts 15 is, moreover, centered on the pump body 12 by pins 21 and the free face of the cheek 16 has a crown 22 projecting, to ensure the centering of the motor 1 which is fixed to the pump body 12 by bolts 23 passed through through holes 24 of the body 12, these holes as well as the bolts being clearly visible in particular in FIGS. 2, 5 and 6.
  • the pump body 12 has, between the cavity 11 containing the pinions 9, 10 and its periphery, a housing 25 passing right through it in which is disposed the cartridge 26 of a pressure relief valve 27 (fig. 1) whose the piston 28 pushed by a calibration spring 29 is in communication by a bore 30 with the chamber 19 in which the fluid is discharged under high pressure.
  • a pressure relief valve 27 (fig. 1) whose the piston 28 pushed by a calibration spring 29 is in communication by a bore 30 with the chamber 19 in which the fluid is discharged under high pressure.
  • Fig. 1 shows that the pressure relief valve crosses the cheek 17.
  • the piston 28 of the pressure relief valve 27 controls the opening of discharge channels 31 leading to the interior of the cavity 25 which is in communication with the interior of an envelope 32 forming a reservoir via a light 33 (fig. 1).
  • the pump body 12 has, in its face facing the cheek 17, cavities such as 34, 35 and 36 which surround the cavity 11 containing the pinions 9, 10 of the pump. These cavities, which communicate with the chamber 19 of fluid under high pressure, constitute cavities ensuring the damping of the sound waves generated by the operation of the pump.
  • At least some of the cavities 34, 35, 36 can be connected together to cause circulation of the fluid under high pressure which they contain.
  • the pump body 12 comprises an intake duct 37 which leads to the cavity 11 containing the pinions (fig. 5) and which opens inside the casing 32 filled with fluid under low pressure.
  • the pump body 12 delimits a channel 38 opening in one of the so-called Helmholtz cavities, in this case the cavity 34, and leading by a conduit 39 inside the envelope 32.
  • a non-return valve 40 consisting of a ball, a spring and a retaining member is disposed in the channel 38 and is held against its seat by the pressure prevailing in the cavity 34 in communication with the chamber 19 of the cover 18.
  • the channel 38 and the non-return valve 40 constitute a bypass path for the fluid between the low pressure and high pressure circuits, which makes it possible, if necessary, to use a fluid receiving mechanism in the event of a failure. power supply to the pump drive electric motor. Indeed, the circulation between the low pressure and high pressure circuits which can be established by the non-return valve 40 makes it possible to avoid a blockage as could occur with regard to the receiving mechanism which could not be operated manually if the high pressure circuit cannot be supplied by the low pressure circuit.
  • the implementation of the conduit 41 has the effect of further improving the damping of the sound waves generated by the operation of the pump.
  • the pump has great compactness since it is the pump body which delimits all the cavities necessary for fitting both the pinions and the damping chambers of the pressure relief valve and inlet and outlet conduits, this pump body being closed by thin cheeks, which ensures a very compact overall.
  • the hydraulic assembly thus constitutes a unit to which the electric motor 1 is then fixed by the installation of bolts 23 which contribute to ensuring the sealing functions of the pump as illustrated in FIG. 2.
  • the assembly, hydraulic unit - hydraulic motor is then engaged inside the casing 32.
  • the cover 18 forms a fitting 42 on which the casing 32 is engaged, the sealing being ensured by an O-ring 43.
  • the fitting 42 is preferably provided so as to allow rapid connection with a mounting bracket.
  • the threaded bore 44 allows the attachment of a supply pipe to a receiver.
  • the embodiment according to fig. 7 shows that the cheek 17 delimits two chambers 19 and 34.
  • the pump begins in chambers 19 and 34 by calibrated channels 20, 45 and 46 that designated by 20 corresponding to the actual discharge of the pump.
  • the flow is then carried out by the high pressure outlet of the bore 44 by an additional calibrated channel 47.
  • the distribution of the volume in two high pressure chambers 19 and 34 makes it possible, by adjusting the channels or lights 20, 45, 46 and 47, to reduce the pressure pulsations generated by the pinions, pressure pulses which are thus damped due to communications multiples produced between the damping chambers and between the discharge parts of the pinions and the damping chambers.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Hydraulic Motors (AREA)
EP96401657A 1995-08-30 1996-07-25 Kompakte elektrohydraulische Einheit Expired - Lifetime EP0761970B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9510219 1995-08-30
FR9510219A FR2738302B1 (fr) 1995-08-30 1995-08-30 Groupe electro-hydraulique compact

Publications (2)

Publication Number Publication Date
EP0761970A1 true EP0761970A1 (de) 1997-03-12
EP0761970B1 EP0761970B1 (de) 1999-01-07

Family

ID=9482168

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96401657A Expired - Lifetime EP0761970B1 (de) 1995-08-30 1996-07-25 Kompakte elektrohydraulische Einheit

Country Status (9)

Country Link
US (1) US5692883A (de)
EP (1) EP0761970B1 (de)
JP (1) JP4115548B2 (de)
CN (1) CN1146963A (de)
AR (1) AR003377A1 (de)
BR (1) BR9603535A (de)
DE (2) DE761970T1 (de)
ES (1) ES2127609T3 (de)
FR (1) FR2738302B1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19833372A1 (de) * 1998-07-24 2000-01-27 Zahnradfabrik Friedrichshafen Zahnradpumpe
DE102004021885A1 (de) * 2004-05-04 2005-12-01 Zf Lenksysteme Gmbh Rotations-Hydropumpe
WO2006111314A1 (de) * 2005-04-21 2006-10-26 Trw Automotive Gmbh Motor-pumpen-aggregat, insbesondere für eine fahhrzeug-servolenkung
EP1026392B2 (de) † 1999-02-04 2012-05-30 Hydroperfect International Hpi Zahnradpumpe und Elektropumpengruppe versehen mit einer solchen Pumpe
WO2016062538A1 (de) * 2014-10-21 2016-04-28 Magna Powertrain Bad Homburg GmbH Vorrichtung zur druckkompensation

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3667034B2 (ja) * 1996-07-17 2005-07-06 光洋精工株式会社 電動ポンプ
US6158983A (en) * 1997-04-24 2000-12-12 Trw Inc. Pump having muffler for attenuating noise
US5961309A (en) * 1997-04-24 1999-10-05 Trw Inc. Gear pump with noise attenuation
EP0987439B1 (de) 1998-09-18 2003-11-26 Koyo Seiko Co., Ltd. Elektrisch angetriebene Pumpe
US6305919B1 (en) * 1999-08-24 2001-10-23 Visteon Global Technologies, Inc. Hydraulic pump housing with an integral dampener chamber
US6419042B1 (en) 2000-10-03 2002-07-16 Trw Inc. Integrated electric power hydraulic steering system
US7124775B2 (en) * 2003-02-05 2006-10-24 Neng-Chao Chang Micro pump device with liquid tank
US8122867B2 (en) * 2008-11-17 2012-02-28 GM Global Technology Operations LLC Engine with oil pump muffler and noise damper
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
CN106438341B (zh) * 2016-10-21 2018-11-02 珠海格力电器股份有限公司 泵

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2036873A (en) * 1978-12-01 1980-07-02 South Western Ind Res Silencing Fluid Pumps and Motors
DE2922731A1 (de) * 1979-06-05 1980-12-18 Bosch Gmbh Robert Kraftstoff-foerderaggregat
EP0088674A1 (de) * 1982-03-04 1983-09-14 Hydroperfect International Hpi Elektro-hydraulische Einheit für Servolenkungsanlagen, insbesondere für Fahrzeuge
DE3438680A1 (de) * 1983-10-21 1985-05-15 Hitachi, Ltd., Tokio/Tokyo Kraftstoff-foerderpumpe
WO1986004393A1 (en) * 1985-01-15 1986-07-31 Zahnradfabrik Friedrichshafen Ag Vane cell pump
EP0541337A1 (de) * 1991-11-04 1993-05-12 Vickers Incorporated Elektromotorisch angetriebene Hydrovorrichtung, mit integrierter Pumpe

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3121529A (en) * 1962-05-02 1964-02-18 Polysius Gmbh Blower
US4174196A (en) * 1976-07-28 1979-11-13 Hitachi, Ltd. Screw fluid machine
GB2102074B (en) * 1981-07-18 1985-01-30 Dowty Group Services Positive-displacement fluid-machines
FR2522824A1 (fr) * 1982-03-05 1983-09-09 Commissariat Energie Atomique Dispositif pour appliquer des signaux logiques de test a deux etats sur une entree d'un circuit logique et application aux tests automatiques d'une pluralite de circuits logiques
JPS603293U (ja) * 1983-06-21 1985-01-11 三菱電機株式会社 ポンプ装置
US5401150A (en) * 1994-02-28 1995-03-28 General Signal Corporation Noise reduced liquid sealed compressor
US5507151A (en) * 1995-02-16 1996-04-16 American Standard Inc. Noise reduction in screw compressor-based refrigeration systems

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2036873A (en) * 1978-12-01 1980-07-02 South Western Ind Res Silencing Fluid Pumps and Motors
DE2922731A1 (de) * 1979-06-05 1980-12-18 Bosch Gmbh Robert Kraftstoff-foerderaggregat
EP0088674A1 (de) * 1982-03-04 1983-09-14 Hydroperfect International Hpi Elektro-hydraulische Einheit für Servolenkungsanlagen, insbesondere für Fahrzeuge
DE3438680A1 (de) * 1983-10-21 1985-05-15 Hitachi, Ltd., Tokio/Tokyo Kraftstoff-foerderpumpe
WO1986004393A1 (en) * 1985-01-15 1986-07-31 Zahnradfabrik Friedrichshafen Ag Vane cell pump
EP0541337A1 (de) * 1991-11-04 1993-05-12 Vickers Incorporated Elektromotorisch angetriebene Hydrovorrichtung, mit integrierter Pumpe

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19833372A1 (de) * 1998-07-24 2000-01-27 Zahnradfabrik Friedrichshafen Zahnradpumpe
WO2000005504A1 (de) * 1998-07-24 2000-02-03 Zf Lenksysteme Gmbh Zahnradpumpe
US6506029B1 (en) 1998-07-24 2003-01-14 Zf Lenksysteme Gmbh Gear pump
EP1026392B2 (de) † 1999-02-04 2012-05-30 Hydroperfect International Hpi Zahnradpumpe und Elektropumpengruppe versehen mit einer solchen Pumpe
DE102004021885A1 (de) * 2004-05-04 2005-12-01 Zf Lenksysteme Gmbh Rotations-Hydropumpe
DE102004021885B4 (de) * 2004-05-04 2009-10-01 Zf Lenksysteme Gmbh Rotations-Hydropumpe
WO2006111314A1 (de) * 2005-04-21 2006-10-26 Trw Automotive Gmbh Motor-pumpen-aggregat, insbesondere für eine fahhrzeug-servolenkung
WO2016062538A1 (de) * 2014-10-21 2016-04-28 Magna Powertrain Bad Homburg GmbH Vorrichtung zur druckkompensation

Also Published As

Publication number Publication date
JP4115548B2 (ja) 2008-07-09
FR2738302B1 (fr) 1997-10-10
DE69601290T2 (de) 1999-06-02
US5692883A (en) 1997-12-02
JPH09105385A (ja) 1997-04-22
DE69601290C5 (de) 2010-10-28
AR003377A1 (es) 1998-07-08
BR9603535A (pt) 1998-05-12
FR2738302A1 (fr) 1997-03-07
DE69601290D1 (de) 1999-02-18
EP0761970B1 (de) 1999-01-07
DE761970T1 (de) 1997-09-11
ES2127609T3 (es) 1999-04-16
CN1146963A (zh) 1997-04-09

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