EP1158181A2 - Vérin électrohydraulique - Google Patents

Vérin électrohydraulique Download PDF

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Publication number
EP1158181A2
EP1158181A2 EP01111167A EP01111167A EP1158181A2 EP 1158181 A2 EP1158181 A2 EP 1158181A2 EP 01111167 A EP01111167 A EP 01111167A EP 01111167 A EP01111167 A EP 01111167A EP 1158181 A2 EP1158181 A2 EP 1158181A2
Authority
EP
European Patent Office
Prior art keywords
pump
piston
housing
actuator according
channel
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Withdrawn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
EP01111167A
Other languages
German (de)
English (en)
Other versions
EP1158181A3 (fr
Inventor
Torsten Dipl.-Ing. Gentzsch
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.)
EMG-ELTMA Hebezeuge Oschersleben GmbH
Original Assignee
EMG-ELTMA Hebezeuge Oschersleben 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 EMG-ELTMA Hebezeuge Oschersleben GmbH filed Critical EMG-ELTMA Hebezeuge Oschersleben GmbH
Publication of EP1158181A2 publication Critical patent/EP1158181A2/fr
Publication of EP1158181A3 publication Critical patent/EP1158181A3/fr
Withdrawn legal-status Critical Current

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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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and pump

Definitions

  • the invention relates to an electro-hydraulic actuator according to the preamble of Claim 1.
  • a known actuator of this type is a piston-cylinder unit in a housing arranged, one on the output shaft in the bottom region of the housing arranged electric motor one or two pump wheels are attached, which in the housing Pump the hydraulic oil contained against the end face of the piston.
  • this known Design results from the piston-cylinder unit arranged in front of the pump wheels a relatively long structure, large dimensions and long lowering times for the Piston.
  • the object of the invention is to provide an electrohydraulic actuator of the type specified Type in such a way that it has the most compact possible structure.
  • Fig. 1 shows schematically a housing 1 in which an electric motor 2 is arranged, the electrical supply lines are not shown.
  • 3 designates a pump, of which only the outline of the pump housing are shown and that of the Motor 2 is driven.
  • the pump 3, a high-pressure pump, is preferably a screw pump trained so that the pump housing with the lowest possible Diameter can be designed. Instead of a screw pump, you can also use a Gear pump can be provided.
  • a Annular piston 4 On the outer circumference of the pump 3 or of its cylindrical pump housing is a Annular piston 4 arranged, which is displaceable in a cylinder space 5 formed in the housing 1 is.
  • the annular piston 4 has a pot-shaped extension section 6 a piston rod 7 is attached, which is guided in a housing bore and the actuating element of the actuator.
  • the pot-shaped extension section 6 of the Annular piston 4 is guided in a cylindrical housing recess 8, which is a smaller one Has diameter than the cylinder space 5.
  • the annular piston 4, whose outer diameter is larger is as the outer diameter of the pot-shaped extension section 6, points to the Side of the extension section 6, an end face 9 and on the motor facing Side an end face 10.
  • a suction space 11 is formed which is filled with hydraulic medium is filled.
  • the extension section 6 and the piston rod 7 are each provided seals, not shown. Between the pump housing and the inner circumference of the piston there is an annular gap 18 through which the hydraulic medium passes a channel 15 can be sucked into the suction chamber 11 from a reservoir 16.
  • grooves extending in the axial direction can also be provided between the pump housing and the inner circumference of the piston so that the ribs between the Grooves a guide is formed and the suction chamber 11 of the pump with the Oil reservoir 16 is connected via the compensation channel 15.
  • a suction opening 12 is formed through which the hydraulic medium, preferably Transformer oil, sucked out of the piston chamber 11 and through one through the engine compartment or the motor housing leading, schematically indicated channel 13 and one in the housing 1 trained channel 14 is conveyed into the cylinder chamber 5, so that the end face 9 of the Ring piston 4 is pressurized in the direction indicated by the arrow.
  • the cylinder room 5a on the opposite end face 10 of the annular piston 4 is above the pressure equalization channel 15 in connection with the reservoir or oil space 16, which is connected via a further one Compensation channel 17 with the recess 8 between the bottom of the extension section 6 of the annular piston and housing 1 is connected.
  • Fig. 2 shows a modified embodiment in which a compressive force against the direction of the arrow P in Fig. 1 can be generated with the same direction of rotation of the pump 3.
  • the ring piston 4 ' is on the outer periphery of the bottom of the pot-shaped extension section 6 formed and the high pressure line 13, 14 opens into the cylinder space 5a, so that the annular surface 10 'of the annular piston 4' is pressurized and the opposite end face 9 'of the ring piston via the compensating line 17 with the reservoir 16 in connection stands.
  • the extension section 6 is on a section 26 of the housing 1, which limits the cylinder space 5a in the axial direction, with between this section 26 and the extension section 6 arranged a seal, not shown is.
  • the annular gap 18 is in the same way with the pressure compensation channel 15 in Connection as in the embodiment according to FIG. 1.
  • Fig. 3 shows an embodiment in which the annular piston 4 'with a pot-shaped extension section 6 in Fig. 2 by a cup-shaped piston 30 and an engaging in it Pot-shaped component 31 is divided.
  • the cup-shaped corresponding to the ring piston 4 ' Piston 30 is connected to the piston rod 7 and it is on its annular end face 10 'pressurized. Is between the outer circumference of this piston 30 and housing 1 a seal, not shown, is provided.
  • the suction chamber 11 of the pump 3 connected to the compensation channel 15 via the annular gap 18.
  • the unpressurized also stands Cylinder chamber 8 with the oil reservoir 16 in connection via the compensation channel 17.
  • Motor 2 pump 3 and working piston with piston rod 7 are arranged on one axis, where a compact design in the axial direction results from the fact that the high-pressure side Cylinder space of the piston, in FIG. 1 the cylinder space 5 and in FIGS. 2 and 3 the cylinder space 5a, extends around a portion of the pump housing. This allows the pot-shaped Pistons overlap the pump housing. 3 can the piston 30 can also be disc-shaped without the axial overall length being greater is, with such a modification of the piston essentially the bottom surface of the shown pot-shaped piston 30 corresponds.
  • a compact design in diameter is achieved in particular by reducing the Diameter of the pump housing reached, which also the annular piston 4, 4 'or
  • the outer circumference of the piston 30 can be designed so that it is the diameter of the motor 2 not towered over.
  • the piston rod 7 is in operation of the pump 3 attracted to actuate, for example, a brake device, not shown, as by the arrow P indicated.
  • the end face 9 of the annular piston 4 is pressurized, so that a high tensile force arises on the piston rod 7.
  • the piston rod 7 is in the same direction of rotation of the pump 3 pressed on the outside, as indicated by an arrow.
  • the piston rod 7 can be arranged with an external or outside the housing 1, tension or compression spring, not shown, are acted against in the direction of arrow P, around the ring piston 4 after switching off the pump 3 to an initial position to the left in Fig. 1 to move.
  • a weight force on the piston rod can also be used for this return movement 7 attack.
  • an external spring can be provided to act on the piston rod 7.
  • Fig. 4 shows a circuit diagram of the actuator of Fig. 1, for the sake of simplicity a conventional piston-cylinder unit is shown.
  • Pot element are the same reference numerals as used in Fig. 1.
  • the pump 3 sucks through a filter 21 Hydraulic medium on and promotes this via the pressure channels 13, 14 in the cylinder chamber 5, the channel 13 leading through the engine compartment schematically outside the engine area is reproduced.
  • An electromagnetically operated switching valve 20 is between the pressure channel 13, 14 and the return channel 17, being shown in FIG. 4 Switch position (switch-off position) of valve 20, pump 3 via connecting channel 22 and promotes the return channel 17 back into the reservoir 16.
  • the switching valve 20 is generally parallel to the supply voltage of the actuator co-controlled.
  • Fig. 4a shows an embodiment with return delay
  • a preferably adjustable throttle 24 is arranged, by which when switching of the switching valve 20 in the reproduced switch-off position, the pressure from the pressure channel 14 and the cylinder chamber 5 slowly reduced via the throttle 24 in an adjustable manner is to a too rapid movement of the piston 4 by a restoring force, not shown to prevent.
  • a check valve 25 is provided, the pressure reduction in the direction Pump 3, which in this case is out of operation, is prevented.
  • Fig. 4b shows an embodiment in which instead of the pressure relief valve 23 in Fig. 4 Control valve 27 is arranged between pressure channel 13, 14 and return channel 17 to a enable process-dependent actuating force control via a setpoint.
  • pressure relief valve 23 is a preset, so not variable valve.
  • the control valve 27 is actuated by a magnet 28, so that it is via magnetic control from 0 to 10 volts z. B. depending on a predetermined Process can be operated.
  • Fig. 5 shows in different views a practical embodiment of the actuator 1, wherein the housing 1 is formed as an approximately rectangular block on the Top of the additional housing 19 for the oil chamber 16 and the switching valve 20 is attached.
  • the pressure relief valve 23 is arranged in the additional housing 19. With 40 in Fig. 5 is the connection reproduced for the electrical supply lines for the electric motor, the are pressure-tight into the housing 1.
  • the pressure relief valve is shown at 23 in FIG and at 24 the adjustable throttle.
  • Oil chamber 16 can also be integrated in the housing 1, but it is for the different Design of individual types of actuators useful, the oil space 16 with the attached valves to the housing 1 to attach. To achieve the shortest positioning times of the piston, it is expedient to seal the oil chamber 16 with the associated valves so tightly to be arranged on the piston 4, 4 'or 30 as possible.
  • the oil volume in the oil reservoir 16 by an elastic member, for example a rubber wall 29 opposite one to which atmospheric pressure is applied via a line 33 Space delimited.
  • This elastic rubber wall 29 serves to compensate for the Oil volume and enables position-independent installation of the actuating device.
  • the Rubber wall 29 is expediently guided by a piston guided in the housing part 19 34 performed, which is acted upon by atmospheric pressure and a compensatory movement in Can execute arrow direction.
  • the elastic member 29 serves also for an air-free filling of the cylinder space.
  • the force as well as the stroke range of the actuator can be within the scope of a type program be set or designed according to the respective requirements.
  • the actuator can be used for a variety of purposes, for example as a brake release device or as a spreading device, the piston rod between intervening elements to be spread.
  • the engine 2 shown in Fig. 1 only by outline is conveniently in a corresponding recess of the housing 1 is pressed. But it is also possible that Motor 2 to place on a housing 1, which the pump 3 with the surrounding cylinder space 5 and the piston 4 receives.
  • an impeller pump can be provided in the embodiment
  • hydraulic medium is sucked out of the suction chamber 11 and conveys into the channel 13.
  • a cylinder is arranged around the impeller, not shown, of the pump the outer circumference of the piston 4 is guided with the interposition of the annular gap 18, while the open side of the cylinder corresponds to the suction opening 12 and the opposite Pressure-tight side with the motor housing or a corresponding pressure channel 13 connected is.
  • Fig. 6 shows two types of attachment of an actuator according to the invention.
  • the housing 1 is articulated to a component or a stationary part 34 at 35.
  • the piston rod 7 protruding from the housing on the opposite side can be articulated, for example, with a lever 36.
  • the housing 1 is firmly screwed to a component or a stationary part 37, the piston rod 7 projecting through this component.
  • cooling fins which are screwed on as a separate cooling unit on the circumference of the housing 1 can, as shown in FIG. 7.
  • independent cooling units are independent of the housing 38 formed, depending on the housing design with shorter (Fig. 7a) or longer Ribs (Fig. 7b) are provided.
  • the individual cooling units 38 can also be different have wide ribs.
  • such independent cooling units 38 on the housing 1 of the actuator on one or more Sides screwed or glued.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Reciprocating Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
EP01111167A 2000-05-26 2001-05-10 Vérin électrohydraulique Withdrawn EP1158181A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000126147 DE10026147C2 (de) 2000-05-26 2000-05-26 Elektrohydraulisches Betätigungsgerät
DE10026147 2000-05-26

Publications (2)

Publication Number Publication Date
EP1158181A2 true EP1158181A2 (fr) 2001-11-28
EP1158181A3 EP1158181A3 (fr) 2004-01-02

Family

ID=7643677

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01111167A Withdrawn EP1158181A3 (fr) 2000-05-26 2001-05-10 Vérin électrohydraulique

Country Status (3)

Country Link
EP (1) EP1158181A3 (fr)
DE (1) DE10026147C2 (fr)
ES (1) ES2165339T1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005054738A1 (fr) * 2003-12-05 2005-06-16 Plugging Specialists International Asa Verins hydrauliques et bouchon a verin hydraulique
WO2010141281A1 (fr) * 2009-06-02 2010-12-09 Haldex Hydraulics Corporation Actionneur au point d'utilisation
US8448432B2 (en) 2007-02-13 2013-05-28 The Board Of Regents Of The University Of Texas System Actuators
DE102016110779A1 (de) * 2016-06-13 2017-12-14 Emg Automation Gmbh Elektrohydraulische Betätigungsvorrichtung mit Kühlmodulen
US10077816B2 (en) 2013-05-28 2018-09-18 Pintsch Bubenzer Gmbh Functional unit and electrohydraulic brake release device including such a unit
EP3003807B1 (fr) 2013-05-28 2019-02-20 Pintsch Bubenzer GmbH Releveur de frein électrohydraulique et ensemble de freinage
WO2023006454A1 (fr) * 2021-07-27 2023-02-02 Hydraulik Nord Technologies GmbH Unité hydraulique

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10320456B4 (de) * 2003-05-08 2005-10-06 Hense Systemtechnik Gmbh & Co. Kg Schwenkmotor
DE102005060436B4 (de) * 2005-12-15 2010-02-04 Eads Deutschland Gmbh Aktuator
DE102014215080A1 (de) * 2014-07-31 2016-02-04 Robert Bosch Gmbh Hydraulische Achse

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2035813A (en) * 1932-04-09 1936-03-31 Carl E Johnson Electrolift
US2457467A (en) * 1945-03-08 1948-12-28 Cons Vultee Aircraft Corp Electrically and hydraulically operated extensible strut
DE852188C (de) * 1950-05-09 1952-10-13 Elektro Mechanik G M B H Elektrohydraulische Verstellvorrichtung
DE1550812A1 (de) * 1966-05-31 1969-10-09 Klose Kommandit Ges Elektrohydraulisches Verstellgeraet mit hydraulischem Akkumulator
DE2103701C3 (de) * 1971-01-27 1974-06-27 Elektro-Mechanik Gmbh, 5961 Wendenerhuette Elektrohydraulische Verstellvorrichtung
DE3218001A1 (de) * 1982-05-13 1983-11-17 Elektro-Mechanik Gmbh, 5963 Wenden Elektrohydraulische verstellvorrichtung
DE4116399C2 (de) * 1991-05-18 1995-07-13 Hemscheidt Fahrwerktech Gmbh Kolbenzylindereinheit insbesondere zur Verwendung als Federbein in Fahrzeug-Federungssystemen
US5758862A (en) * 1996-08-27 1998-06-02 Sturman Industries Solenoid pump operated valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005054738A1 (fr) * 2003-12-05 2005-06-16 Plugging Specialists International Asa Verins hydrauliques et bouchon a verin hydraulique
US7568504B2 (en) 2003-12-05 2009-08-04 Tdw Offshore Services As Hydraulic cylinders and plug with hydraulic cylinder
US8448432B2 (en) 2007-02-13 2013-05-28 The Board Of Regents Of The University Of Texas System Actuators
WO2010141281A1 (fr) * 2009-06-02 2010-12-09 Haldex Hydraulics Corporation Actionneur au point d'utilisation
US10077816B2 (en) 2013-05-28 2018-09-18 Pintsch Bubenzer Gmbh Functional unit and electrohydraulic brake release device including such a unit
EP3003808B1 (fr) 2013-05-28 2019-02-13 Pintsch Bubenzer GmbH Unité fonctionnelle et releveur de frein électrohydraulique équipé d'une telle unité
EP3003807B1 (fr) 2013-05-28 2019-02-20 Pintsch Bubenzer GmbH Releveur de frein électrohydraulique et ensemble de freinage
EP3003808B2 (fr) † 2013-05-28 2022-09-28 DELLNER BUBENZER GERMANY GmbH Unité fonctionnelle et releveur de frein électrohydraulique équipé d'une telle unité
DE102016110779A1 (de) * 2016-06-13 2017-12-14 Emg Automation Gmbh Elektrohydraulische Betätigungsvorrichtung mit Kühlmodulen
WO2023006454A1 (fr) * 2021-07-27 2023-02-02 Hydraulik Nord Technologies GmbH Unité hydraulique

Also Published As

Publication number Publication date
DE10026147A1 (de) 2001-12-06
DE10026147C2 (de) 2002-04-18
ES2165339T1 (es) 2002-03-16
EP1158181A3 (fr) 2004-01-02

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