EP1302663A1 - Groupe moto-pompe électro-hydraulique et clapet anti-retour - Google Patents

Groupe moto-pompe électro-hydraulique et clapet anti-retour Download PDF

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Publication number
EP1302663A1
EP1302663A1 EP02010499A EP02010499A EP1302663A1 EP 1302663 A1 EP1302663 A1 EP 1302663A1 EP 02010499 A EP02010499 A EP 02010499A EP 02010499 A EP02010499 A EP 02010499A EP 1302663 A1 EP1302663 A1 EP 1302663A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure relief
pump unit
motor pump
pressure
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
EP02010499A
Other languages
German (de)
English (en)
Other versions
EP1302663B1 (fr
Inventor
Martin Dipl.-Ing. Heusser
Gerhard Lörner
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.)
Hawe Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Hawe Hydraulik GmbH and Co KG
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 Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG, Hawe Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Publication of EP1302663A1 publication Critical patent/EP1302663A1/fr
Application granted granted Critical
Publication of EP1302663B1 publication Critical patent/EP1302663B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/02—Pumping installations or systems having reservoirs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/10—Other safety measures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/04—Draining
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20592—Combinations of pumps for supplying high and low pressure
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3116—Neutral or centre positions the pump port being open in the centre position, e.g. so-called open centre
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a directional control valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a return line
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to an electro-hydraulic motor pump unit according to the preamble Claim 1, an attachment element according to the preamble of claim 12 and a pressure relief valve according to the preamble of claim 13.
  • Electrohydraulic motor pump units according to DE 200 07 554 U are on Machine tools used to hydromechanical clamping or tool or To control workpiece holding devices. Furthermore, electrohydraulic motor pump units as transportable supply units for cutting or riveting devices, Tools or screwdrivers used.
  • the motor pump unit is with one Add-on element equipped that has the at least one consumer connection, at the respective consumer, for example via hydraulic hoses or Piping, is connected. Because of the high tightness of the valve components and also the manufacturing precision of the connectable hydraulic consumers remains a considerable amount even after the motor pump unit has been switched off System pressure maintained for a long time.
  • the invention has for its object a hydraulic motor pump unit to create the type mentioned, in which the long-term pressure retention the hydraulic valve components is eliminated in a structurally simple manner, and an attachment for a hydraulic pump unit, in particular with a AC motor, to indicate with the starting problems of the AC motor are avoidable, and finally a pressure relief valve in seat valve design to indicate that there is leakage in the closed position.
  • the pressure relief device automatically reduces the pressure as soon as the electric motor stands. This makes it much easier for the electric motor to restart. In particular in an AC motor, this effect is advantageous because of a AC motor otherwise requires a relatively high starting current, which if necessary could overload the fuses of the normal network. AC motors are used especially with portable motor pump units, so that Motor pump unit just connected to the normal network in mobile use can be. However, easy starting is also possible with other electric motors be desirable. Furthermore, hose or Loosen pipe couplings easily, and if necessary, the consumer reset by hand, for example in the event of an unexpected power failure is advantageous.
  • the attachment can be used to convert an electrohydraulic motor pump unit be attached to the electric motor, especially an AC motor, facilitate starting after a break.
  • the permanently open bypass means only a negligible loss. None is used for this additional function uses its own valve component, but the pressure relief valve that is necessary anyway.
  • the pressure relief valve creates leakage-free Shut-off position a leakage predetermined in its extent, however does not affect the pressure relief function. It can be used without an additional valve component the pressure held within a pressure relief valve Known period of time can be reduced, which is particularly the case with an electrohydraulic Motor pump unit with an AC motor as a drive source for The pump stage offers advantages to keep the starting current of the AC motor low to keep.
  • the pressure relief device is expediently incorporated into the attachment element.
  • the permanently open bypass means a loss in operation, but it does is negligible. After switching off the electric motor, the pressure builds up automatically from.
  • the pressure relief valve fulfills its normal operation Pressure limiting function and the function at the beginning of a break the pressure relief.
  • the two pressure relief valves to different Set response pressures.
  • the bypass in the pressure relief valve is useful arranged with the lower response pressure so that to reach no losses due to the higher working pressure. At a Reset or release stroke of a hydraulic consumer controlled by the motor pump unit the loss due to the bypass does not matter.
  • An AC motor as an electric motor offers the advantage of being connected to the normal AC network to be able to be connected.
  • the dual circuit pump stage enables it, initially with the low-pressure pump stage with a relatively large delivery rate to reach lower pressure levels, and then with the high pressure pump stage low flow rate to get to very high working pressures, e.g. except for about 800 bar.
  • the direction of movement of the hydraulic consumer is determined by means of the directional control valve controlled, each pressure relief valve the maximum working pressure monitored in one direction.
  • the bypass is located in one of the pressure relief valves, expedient in that the less important function or the lower pressure monitoring Pressure relief valve.
  • the bypass in a cone seat valve is structurally simple by flattening the Cone jacket of the valve cone formed.
  • the flattening forms in the shut-off position the pressure relief valve with the valve seat a passage or a throttle a predetermined size over which the leakage flows.
  • The is expedient Flattened by a sanded surface, the manufacture of which is simple.
  • the flattening should be parallel to the cone generator, so that it is at the Grinding strokes when grinding the cone shell by interrupting the rotary movement of the valve cone can be precisely shaped by adjusting the grinding tool.
  • bypass could be at least in the case of a cone or ball seat valve a notch may be formed in the valve seat.
  • the bypass is expediently dimensioned such that it has a leakage of approx. 0.3 to 0.4 Liters per minute at 150 bar. This allows an at least extensive Pressure relief, for example within a few seconds, e.g. approx. 5 Seconds, bring about.
  • the damping effect is enhanced when the cavity of the damping piston is open to the outside via at least one channel and contains a check valve.
  • An electro-hydraulic motor pump unit G (Fig. 1) is used as a supply unit e.g. of a hydromechanical tool either installed stationary or as transportable unit used.
  • a housing 1 which is also an oil reservoir T can be an electric motor M with a fan 2 as the drive of at least one internal pump stage P is provided.
  • the electric motor M can be a three-phase motor, a DC motor or also, especially for mobile applications, be an AC motor that can be supplied from the normal network.
  • An add-on element C is attached to the housing 1 or integrated therein stands with at least one, not shown, pressure side connection of the pump stage P in connection, and also with the return leading into the housing 1.
  • the add-on element C has in Fig. 1 a block-like housing 7 on which a directional control valve 3 is attached with a switching magnet 4.
  • On the attachment element C are a or two or more consumer connections A, B or 5, 6 are provided.
  • the Consumer connection B or 6 is, preferably in the add-on element C, a hydraulic, assigned automatic pressure relief device D, via which when switched off Electric motor M the system pressure, at least in the electro-hydraulic motor pump unit G to at least the consumer connections A, B due to leakage is degradable, and possibly even up to the hydraulic consumer not shown in FIG. 1.
  • FIG. 2 shows the housing 1 and the housing in dash-dot lines 7, and a hydraulic consumer Z (for example a double-sided differential cylinder), for driving a tool, a clamping device, a holding device, or the like. Via an actuating element 17.
  • the Hydraulic consumer Z is via hydraulic hoses or piping 8, 9 to the Consumer connections A, B or 5, 6 connected.
  • the electric motor M is an AC motor that has its Fan 2 and a high-pressure pump stage P1 with a small flow rate as well as one Low pressure pump stage P3 drives with a larger flow, which from the tank T suck.
  • Both pump stages P1, P3 are connected to a common pressure line 10 connected, the low-pressure pump stage P3 via a check valve 11 secured and via a pressure control valve that is pilot-controlled from the pressure line 10 formed switching valve 12 can be connected to a return 13.
  • the Pressure line 10 leads to an input of the directional control valve 3, which is by spring force durable in the switching position shown and by the switching magnet 4 in the other switch position is convertible.
  • the consumer connection is in the switch position shown B connected to the pressure line 10 via a working line 15 (Reset movement or release stroke), while the consumer connection A via a Working line 14 is connected to the return 13 and is thus relieved of pressure.
  • Both Working lines 14, 15 are each via a pressure relief valve R1, R2 to the return 13 secured.
  • the hydraulic, automatic pressure relief device D is formed by a bypass 16 integrated in the pressure relief valve R2.
  • Both Pressure relief valves R1, R2 are seat valves that are in the shut-off position Seal leak-free. Thanks to the bypass 16 occurs in the shut-off position of the Pressure relief valve R2 leakage to the return 13 through which the system pressure is broken down.
  • the bypass 16 is, for example, dimensioned so that it is at 150 bar (e.g. the response pressure of the pressure relief valve R2) a leakage between 0.3 and 0.4 Liters per minute, which enables the pressure to be generated in a few seconds, e.g. about 5 seconds.
  • 150 bar e.g. the response pressure of the pressure relief valve R2
  • Fig. 3 is a longitudinal section of the extension element C in a plane in which the switching valve 12 and the pressure relief valve R2 are visible.
  • the pressure relief valve R2 is installed in a chamber of the housing 7, the return 13 and the Working line 15 cuts.
  • An insert element 18 is positioned in the chamber a valve seat 19 positioned between the return 13 and the working line 15. With the valve seat 19, a valve cone 20 works together by the response pressure generating spring 21 in the direction of the valve seat 19 and against Pressure in the working line 15 is loaded.
  • the integrated pressure relief device D with the bypass 16 is between the valve cone 20 and the valve seat 10 formed, as will be explained with reference to FIGS. 4 and 5.
  • the valve cone 20 has e.g. a coaxial at the large diameter end Shaft 23 for pressing on a spring abutment 22.
  • the small diameter End portion of the valve cone 20 is extended by a neck 27 which is a hollow damping piston 28 is arranged.
  • a cavity 29 of the damping piston 28 is in a channel 30 with the environment of the valve cone 20 in Connection and contains a ball check valve with a valve ball 31 and one Closing spring 32.
  • the lower, open-shaped end of the cavity 29 is through a Plug 33 closed.
  • the valve cone has a cone jacket 25 as a seating surface, which is in a seating area 24 cooperates with the valve seat 19.
  • a flattened portion 26 is in the conical jacket 25 shaped, the bypass as an interruption of the cone jacket 25 with the valve seat 19 16 forms.
  • the flattened area 26 is, for example, a ground surface in the cone jacket 25, the surface being at least approximately parallel to the cone-producing extends.
  • a grinding depth Y of approx. 2 to 5% of the conical jacket diameter X im Seating area 24 results in a suitable size of the bypass.
  • the flattened portion 26 instead of the flattened portion 26 also has at least one longitudinal notch.
  • FIG. 6 shows an alternative embodiment of the pressure relief valve R2, that as a ball seat valve with a valve ball 20 'in cooperation with the Valve seat 19 'is formed.
  • the bypass 16 is through at least one notch or ablation 34 in the valve seat 19 'when working with the spherical surface.
  • the principle of providing a notch in the valve seat 19 ' could also be provided with a cone seat valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)
EP02010499A 2001-10-15 2002-05-08 Groupe moto-pompe électro-hydraulique et clapet anti-retour Expired - Fee Related EP1302663B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE20116921U DE20116921U1 (de) 2001-10-15 2001-10-15 Elektrohydraulisches Motorpumpenaggregat, Anbauelement und Druckbegrenzungsventil
DE20116921U 2001-10-15

Publications (2)

Publication Number Publication Date
EP1302663A1 true EP1302663A1 (fr) 2003-04-16
EP1302663B1 EP1302663B1 (fr) 2008-10-08

Family

ID=7962892

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02010499A Expired - Fee Related EP1302663B1 (fr) 2001-10-15 2002-05-08 Groupe moto-pompe électro-hydraulique et clapet anti-retour

Country Status (4)

Country Link
US (1) US6739129B2 (fr)
EP (1) EP1302663B1 (fr)
DE (2) DE20116921U1 (fr)
ES (1) ES2314009T3 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2318720B1 (fr) 2008-09-03 2012-10-31 Parker-Hannifin Corporation Commande de vitesse d'un actionneur hydraulique dissymétrique soumis à des conditions de charge de basculement
JP5666233B2 (ja) * 2010-10-08 2015-02-12 ナブテスコ株式会社 航空機アクチュエータの油圧装置
CO6280066A1 (es) 2010-10-21 2011-05-20 Serinpet Ltda Unidad hidraulica de bombeo mecanico con motor unico
EP2642122B1 (fr) * 2012-03-21 2014-05-21 HAWE Hydraulik SE Groupe motopompe
CN103363163B (zh) * 2012-03-27 2015-06-17 上海英威腾工业技术有限公司 用于电液伺服注塑机的泄压阀
EP2799713B1 (fr) * 2013-05-03 2020-09-09 HAWE Hydraulik SE Agrégat de pompes de moteur
AU2014411549B2 (en) * 2014-11-19 2020-12-17 Serinpet Ltda Representaciones Y Servicios De Petroleos Hydraulic mechanical pumping unit comprising a built-in radiator
US11958177B2 (en) * 2018-09-07 2024-04-16 Milwaukee Electric Tool Corporation Hydraulic piston pump for a hydraulic tool
JP1663497S (fr) * 2019-07-29 2020-07-13
JP1663520S (fr) * 2019-07-29 2020-07-13
USD924938S1 (en) 2019-07-29 2021-07-13 Hawe Hydraulik Se Housing portion for a hydraulic pump

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4197705A (en) * 1978-05-30 1980-04-15 General Signal Corporation Hydraulic control system
US4362084A (en) * 1979-06-15 1982-12-07 Sperry Corporation Hydraulic actuator controls
US5454223A (en) * 1993-05-28 1995-10-03 Dana Corporation Hydraulic load sensing system with poppet valve having an orifice therein
DE20007554U1 (de) * 2000-04-26 2000-08-10 Heilmeier & Weinlein Motor-Pumpenaggregat

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4694649A (en) * 1983-02-04 1987-09-22 Howeth David F Pressure limiting acceleration control system and valve for hydraulic motors

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4197705A (en) * 1978-05-30 1980-04-15 General Signal Corporation Hydraulic control system
US4362084A (en) * 1979-06-15 1982-12-07 Sperry Corporation Hydraulic actuator controls
US5454223A (en) * 1993-05-28 1995-10-03 Dana Corporation Hydraulic load sensing system with poppet valve having an orifice therein
DE20007554U1 (de) * 2000-04-26 2000-08-10 Heilmeier & Weinlein Motor-Pumpenaggregat

Also Published As

Publication number Publication date
ES2314009T3 (es) 2009-03-16
US20030070428A1 (en) 2003-04-17
EP1302663B1 (fr) 2008-10-08
DE50212860D1 (de) 2008-11-20
US6739129B2 (en) 2004-05-25
DE20116921U1 (de) 2002-01-03

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