EP0081703A1 - Opérateur électrohydraulique - Google Patents

Opérateur électrohydraulique Download PDF

Info

Publication number
EP0081703A1
EP0081703A1 EP82110794A EP82110794A EP0081703A1 EP 0081703 A1 EP0081703 A1 EP 0081703A1 EP 82110794 A EP82110794 A EP 82110794A EP 82110794 A EP82110794 A EP 82110794A EP 0081703 A1 EP0081703 A1 EP 0081703A1
Authority
EP
European Patent Office
Prior art keywords
drive according
throttle
pressure
pump
adjusting member
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
EP82110794A
Other languages
German (de)
English (en)
Other versions
EP0081703B1 (fr
Inventor
Egon Dipl.-Ing. Lechner
Siegfried Mayer
Dieter Dipl.-Ing. Weigle
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0081703A1 publication Critical patent/EP0081703A1/fr
Application granted granted Critical
Publication of EP0081703B1 publication Critical patent/EP0081703B1/fr
Expired legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input

Definitions

  • the invention relates to an actuator according to the preamble of the main claim.
  • the pump consists of a delivery thread, which is arranged with little radial play in a surrounding housing. Due to the rotation of the conveying thread, pressure medium is conveyed from one side to the other and the housing having axial mobility with respect to the conveying thread is displaced in the axial direction and performs the function of an adjusting member.
  • the disadvantage is that the pump is extremely dependent on viscosity, so that the actuator no longer works at high pressure medium temperatures (when using oil).
  • the drive according to the invention with the characterizing features of the main claim has the advantage that it is not only very simple, but also works reliably under all operating conditions. Advantageous further developments and improvements of the features specified in the main claim are possible through the measures listed in the subclaims. It is particularly advantageous to have the pump work in a closed circuit since there are practically no pressure medium losses.
  • FIG. 1 shows an electrohydraulic actuator in a schematic representation
  • FIG. 8 shows a detail.
  • 10 denotes a direct current electric motor which drives a reversible hydrostatic pump 11, in particular a gear pump.
  • Two delivery lines 12 and 13 are connected to these and lead to two pressure chambers 14, 15 of an actuating cylinder 16.
  • a double-acting piston 17 is arranged in a tightly sliding manner, which is loaded on both sides by springs 18, 19 arranged in the pressure chambers 14, 15. These hold the piston 17 in the middle position when the pump 11 is out of operation.
  • the device to be actuated is connected to the two piston rods 20, 21 protruding from the actuating cylinder - or of course only to one - e.g. a directional valve.
  • the two delivery lines 12, 13 are connected between the pump 11 and the actuating cylinder 16 by a line 22, in which a throttle 23, or even better an orifice, is arranged.
  • a diaphragm is particularly suitable because it is much less sensitive to viscosity than a choke.
  • the pump 11 operates in an open circuit.
  • Suction lines 26, 27 lead from the pressure lines 12, 13 to a container 28.
  • a check valve 29 or 30 is arranged in each suction line and can open in the direction from the container to the suction line.
  • the actuating cylinder is replaced by a directional control valve 32, ie this is now adjusted directly by the differential pressure in the pressure lines 12, 13 against the force of the springs 18, 19. Since they are basically the same parts, they also have the same reference numbers.
  • the throttle in the connecting line 22 is now adjustable and designated 33.
  • the mode of operation is not extensive res from the previously described, ie instead of a control piston, the slide of the directional valve is now adjusted directly.
  • the throttle 33 can be designed as a laminar throttle.
  • a linear characteristic requires a temperature-compensated laminar choke or an electronically controlled voltage on the direct current motor (compensation of choke and motor characteristic). 'The temperature compensation is possible via an expansion working element or a bimetal lines 58, 59 with throttles 60, 61 can be connected for the purpose of targeted leakage; however, this is not absolutely necessary.
  • the embodiment of Figure 4 differs from the previous ones essentially in that there is no longer a connecting line between the pressure lines 12, 13.
  • the pressure difference is now generated by throttles or orifices 35, 36, each of which is arranged in a line 37, 38 which leads from the delivery line 12 or 13 and leads to the container.
  • the chokes can be adjustable. None changes in the basic functionality. If the pump 10 delivers into the delivery line 12, a pressure corresponding to the setting of the throttle 25 builds up in this, and the valve is actuated.
  • the throttles can be adjustable as a function of pressure and temperature in order to adapt to the engine characteristic.
  • the throttles are arranged in lines 40, 41, which start from the pressure spaces 42, 43 of the directional control valve 32.
  • the chokes are designated 44, 45 and coupled to one another via a linkage 46 in such a way that they open in opposite directions NEN or close.
  • the function is again the same as in the exemplary embodiment according to FIG. 4 or the previous ones.
  • the check valves 29, 30 which act as suction valves are also provided. It is also possible to equip the last described embodiment without the check valves; the throttles 44, 45 can be used for suction from the container 28 (FIG. 6).
  • the embodiment according to FIG. 7 - which partially corresponds to the two previous ones with the throttle 44, 45 at the two pressure chambers of the valve, but not coupled this time - again has the connecting line 22 between the two pressure lines 12, 13, in which the throttle 23 is arranged is. Suction valves 29, 30 are also provided. With such a device, a partial exchange of the circulating pressure medium is achieved via the throttles 44, 45 in the control valve. These can of course also be coupled again or set individually.
  • FIG. 9 shows the simplest embodiment of an actuator according to the invention, which, however, is only effective on one side here.
  • the pump is now not reversible but delivers via a pressure line 50 into the pressure chamber 51 of the actuating cylinder 52 acting on one side.
  • Line 54 with throttle 53 is connected in parallel to the pressure line. The mode of operation is readily apparent from what has been described above.
  • the exemplary embodiment according to FIG. 8 shows a practical embodiment of the control valve 32, for example according to FIG. 5.
  • the control slide 60 has two external collars 61, 62 which control widening outlets and inlets 63, 64 on the housing. These parts form the chokes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
  • Actuator (AREA)
EP82110794A 1981-12-05 1982-11-23 Opérateur électrohydraulique Expired EP0081703B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813148174 DE3148174A1 (de) 1981-12-05 1981-12-05 Elektrohydraulischer stellantrieb
DE3148174 1981-12-05

Publications (2)

Publication Number Publication Date
EP0081703A1 true EP0081703A1 (fr) 1983-06-22
EP0081703B1 EP0081703B1 (fr) 1986-02-26

Family

ID=6147968

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82110794A Expired EP0081703B1 (fr) 1981-12-05 1982-11-23 Opérateur électrohydraulique

Country Status (3)

Country Link
EP (1) EP0081703B1 (fr)
JP (1) JPS58102807A (fr)
DE (2) DE3148174A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2163875A (en) * 1984-08-28 1986-03-05 Commercial Shearing Positioning of hydraulic elements
US4872310A (en) * 1986-12-12 1989-10-10 British Aerospace, Plc Electro-hydraulic actuator assembly
EP0362592A2 (fr) * 1988-10-04 1990-04-11 ITT Automotive Europe GmbH Direction assistée hydraulique pour véhicules
EP0482329A1 (fr) * 1990-09-22 1992-04-29 Steag Ag Vérin hydraulique pour vanne de commande et de régulation
EP0665381A1 (fr) * 1994-01-28 1995-08-02 PAUL PLEIGER Maschinenfabrik GmbH & Co. KG Dispositif pour actionner des valves à commande hydraulique
GB2422862A (en) * 2005-02-03 2006-08-09 Schlumberger Holdings Apparatus for actuating downhole tools
WO2009071264A1 (fr) * 2007-12-04 2009-06-11 Robert Bosch Gmbh Système hydraulique muni d'une vanne à descente rapide réglable
US7610754B2 (en) 2005-02-03 2009-11-03 Daikin Industries, Ltd. Fluid pressure unit and fluid pressure unit control method

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19600650C2 (de) * 1996-01-10 2003-05-28 Trinova Gmbh Antrieb für einen hydraulischen doppelwirkenden Aktuator
DE19958257B4 (de) * 1999-12-03 2008-04-24 Bosch Rexroth Aktiengesellschaft Halboffener Hydraulikkreislauf
JP2004263645A (ja) * 2003-03-03 2004-09-24 Opton Co Ltd 液圧装置
RU2544927C1 (ru) * 2011-03-07 2015-03-20 Муг Инк. Подводная система привода
DE202013002862U1 (de) 2013-03-26 2013-04-23 BUKO Solutions GmbH Verstellvorrichtung
DE102013005127B4 (de) 2013-03-26 2017-10-19 BUKO Solutions GmbH Verstellvorrichtung
DE102013008792B4 (de) * 2013-05-23 2016-12-22 Thomas Magnete Gmbh Verfahren und Vorrichtung zur Verstellung einer hydraulischen Verstellpumpe
CN105003481B (zh) * 2015-07-01 2017-02-01 天津大学 集成式变阻尼液压支撑系统

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH201066A (de) * 1937-10-26 1938-11-15 Escher Wyss Maschf Ag Hydraulischer Servomotor zur Betätigung von drehbaren Abschlussorganen.
DE841094C (de) * 1950-09-05 1952-06-13 Elektro Mechanik G M B H Elektrohydraulischer Verstellantrieb mit Schiebersteuerung
US2916879A (en) * 1956-04-04 1959-12-15 John T Gondek Combination hydraulic power unit
FR1518913A (fr) * 1967-02-15 1968-03-29 Puma Soc Dispositif de commande d'un vérin à double effet ou analogue
FR2009929A1 (fr) * 1968-05-21 1970-02-13 Bbc Brown Boveri & Cie Dispositif hydroelectrique de commande

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4218884A (en) * 1978-11-08 1980-08-26 Harold Gold Hydraulic speed governor
DE2940403A1 (de) * 1979-10-05 1981-04-09 G.L. Rexroth Gmbh, 8770 Lohr Vorrichtung zur regelung eines stellgliedes, insbesondere zur regelung des hubwerkes eines schleppers, maehdreschers o.dgl.

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH201066A (de) * 1937-10-26 1938-11-15 Escher Wyss Maschf Ag Hydraulischer Servomotor zur Betätigung von drehbaren Abschlussorganen.
DE841094C (de) * 1950-09-05 1952-06-13 Elektro Mechanik G M B H Elektrohydraulischer Verstellantrieb mit Schiebersteuerung
US2916879A (en) * 1956-04-04 1959-12-15 John T Gondek Combination hydraulic power unit
FR1518913A (fr) * 1967-02-15 1968-03-29 Puma Soc Dispositif de commande d'un vérin à double effet ou analogue
FR2009929A1 (fr) * 1968-05-21 1970-02-13 Bbc Brown Boveri & Cie Dispositif hydroelectrique de commande

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2163875A (en) * 1984-08-28 1986-03-05 Commercial Shearing Positioning of hydraulic elements
FR2573169A1 (fr) * 1984-08-28 1986-05-16 Commercial Shearing Appareil de positionnement a distance d'une valve
US4872310A (en) * 1986-12-12 1989-10-10 British Aerospace, Plc Electro-hydraulic actuator assembly
EP0362592A2 (fr) * 1988-10-04 1990-04-11 ITT Automotive Europe GmbH Direction assistée hydraulique pour véhicules
WO1990003908A2 (fr) * 1988-10-04 1990-04-19 Alfred Teves Gmbh Direction assistee hydraulique pour vehicules automobiles
WO1990003908A3 (fr) * 1988-10-04 1990-06-28 Teves Gmbh Alfred Direction assistee hydraulique pour vehicules automobiles
EP0362592A3 (fr) * 1988-10-04 1990-09-05 ITT Automotive Europe GmbH Direction assistée hydraulique pour véhicules
EP0482329A1 (fr) * 1990-09-22 1992-04-29 Steag Ag Vérin hydraulique pour vanne de commande et de régulation
EP0665381A1 (fr) * 1994-01-28 1995-08-02 PAUL PLEIGER Maschinenfabrik GmbH & Co. KG Dispositif pour actionner des valves à commande hydraulique
GB2422862A (en) * 2005-02-03 2006-08-09 Schlumberger Holdings Apparatus for actuating downhole tools
US7610754B2 (en) 2005-02-03 2009-11-03 Daikin Industries, Ltd. Fluid pressure unit and fluid pressure unit control method
WO2009071264A1 (fr) * 2007-12-04 2009-06-11 Robert Bosch Gmbh Système hydraulique muni d'une vanne à descente rapide réglable

Also Published As

Publication number Publication date
EP0081703B1 (fr) 1986-02-26
DE3148174A1 (de) 1983-06-09
JPS58102807A (ja) 1983-06-18
DE3269488D1 (en) 1986-04-03

Similar Documents

Publication Publication Date Title
DE2446963C2 (de) Hydraulische Stelleinrichtung
EP2960561B1 (fr) Vanne hydraulique
EP0081703A1 (fr) Opérateur électrohydraulique
DE3323363C2 (fr)
EP1657452B1 (fr) Oscillateur pneumatique
DE1921977C3 (de) Ventileinrichtung zur Steuerung der Druckmittelwege eines doppelwirkenden Servomotors
DE2808810A1 (de) Variables riemenscheibengetriebe
EP0103250B1 (fr) Soupape de contrôle pour contrôle hydraulique
EP1910720A1 (fr) Soupape de vidange conçue pour un circuit hydraulique
DE2434440C3 (de) Vorrichtung zur Wegesteuerung des Druckmittels zu und von einem doppeltwirkenden hydraulischen Motor
DE2230589A1 (de) Verstelleinrichtung zur Änderung des Hubs von hydraulischen Rotationsmaschinen
DE2719029C2 (fr)
EP0044518A1 (fr) Dispositif de régulation du débit d'une pompe réglable
DE2038813C2 (de) Druckmittelbetätigtes Mehrwegeventil in Schieberbauart
DE19757157C2 (de) Hydraulischer Linearantrieb
DE19705827A1 (de) Hydrauliksysteme
DE2841083C2 (fr)
EP1251277B1 (fr) Système de contrôle de puissance basé sur la pression moyenne
DE19522744B4 (de) Elektrohydraulische Steuervorrichtung
DE2101727A1 (de) Vorrichtung zur Regelung des Hubs hubveranderhcher Hydraulikpumpen
DE2236888A1 (de) Steuersystem fuer variable hydraulikpumpen oder motore
DE102016209509A1 (de) Hydraulisches Antriebssystem für Gabelstapler
DE2817484A1 (de) Stelleinrichtung fuer eine hydrostatische maschine
DE1273292B (de) Hydrostatisches Getriebe mit einer Fuellpumpe
DE2611088B2 (de) Steuereinrichtung für einen hydraulischen Arbeitzylinder mit einem Differentialkolben

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19821123

AK Designated contracting states

Designated state(s): DE FR GB IT

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Designated state(s): DE FR GB IT

REF Corresponds to:

Ref document number: 3269488

Country of ref document: DE

Date of ref document: 19860403

ET Fr: translation filed
ITF It: translation for a ep patent filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19870731

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19870801

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19881122