EP0620932B1 - Elektrohydraulische steuervorrichtung und druckminderventil - Google Patents

Elektrohydraulische steuervorrichtung und druckminderventil Download PDF

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Publication number
EP0620932B1
EP0620932B1 EP94900117A EP94900117A EP0620932B1 EP 0620932 B1 EP0620932 B1 EP 0620932B1 EP 94900117 A EP94900117 A EP 94900117A EP 94900117 A EP94900117 A EP 94900117A EP 0620932 B1 EP0620932 B1 EP 0620932B1
Authority
EP
European Patent Office
Prior art keywords
control
pressure
reducing valve
piston
pressure reducing
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.)
Expired - Lifetime
Application number
EP94900117A
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German (de)
English (en)
French (fr)
Other versions
EP0620932A1 (de
Inventor
Georg Neumair
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.)
Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Original Assignee
Heilmeier and Weinlein Fabrik fuer Oel 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
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Publication of EP0620932A1 publication Critical patent/EP0620932A1/de
Application granted granted Critical
Publication of EP0620932B1 publication Critical patent/EP0620932B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and 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
    • F15B2211/3138—Directional control characterised by the positions of the valve element the positions being discrete
    • 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
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the 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
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid 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
    • F15B2211/50—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • 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 control device according to the preamble of claim 1 as well a directly controlled pressure reducing valve according to the preamble of claim 8.
  • DE-C-30 39 002 is a directly controlled pressure reducing valve in an electrohydraulic control device known in which in addition to the control piston a separate Throttle piston as volumetric piston for actuation two pressure switches is provided.
  • the throttle piston is centered with two springs.
  • the control pressure is on Output of the pressure reducing valve derived.
  • a pressure reducing valve known from DE-C-23 10 193 in an electrohydraulic control device Machine tool component is the Control piston in one Auxiliary piston arranged the is adjusted depending on the pressure and actuated a pressure switch as a volumetric flask.
  • the standard pressure for the control piston is upstream of the downstream one Directional valve derived.
  • the switching pressure for the Auxiliary piston and the pressure switch is from the acted upon consumer pressure line via a control line and derived a biased check valve.
  • the pressure reducing valve is complicated and multi-part.
  • the invention has for its object an electrohydraulic Control device of the latter type as well as a suitable one to create a controlled pressure reducing valve, the structurally simple and in terms of desired security function are reliable, and just a few, the number of potential sources of error reducing parts exist.
  • the control pressure is structurally simple directly in the directional control valve and only tapped there if the directional control valve properly with a consumer line connected to the outlet of the pressure reducing valve.
  • a separate monitoring of the directional valve for its correct Function is eliminated, as is the need for separate Control lines, a shuttle valve or Check valves.
  • the control device is simple and consists of a few components.
  • the safety function is reliable because the pressure switching device only if the directional control valve functions properly is operated.
  • the pressure switch device is at a Adjustment of the pressure reducing valve set with. Should the directional valve get stuck when pressed and the monitored Do not assume the tax position correctly, then none a response of the pressure switch device Control pressure generated.
  • the Pressure switch device does not emit or enter a good signal Error signal, so that warnings or damage-preventing Measures can be taken.
  • the standard pressure is only derived if the directional control valve, if necessary with a remaining stroke, is so far adjusted that the proper Supply of the clamping device is guaranteed is. Since the clamping pressure of the clamping device most important criterion for security is it expedient, the control pressure to reduce the supply pressure only when the consumer line is charged to derive for tensioning. On the other hand, can be used to release the tensioning device refrain from reducing the pressure and the supply pressure be used. For this purpose, when connecting the other consumer line via the directional valve no control pressure is derived from the outlet of the pressure reducing valve, so that the pressure reducing valve then opens and does not intervene regulatively.
  • an inexpensive 4/2 or 4/3 directional spool used in Housing has a control channel, the mouth part is the consumer pressure tap.
  • the mouth part is the consumer pressure tap.
  • the pressure tap can if necessary for only one or both consumer lines to be used.
  • the pressure relief directly across the cross slot to the tank connection ensured. If the pressure tap is not used, the tank connection can be closed.
  • the measure of claim 7 is important so that the flow paths always open in the predetermined manner and are closed.
  • the locking device holds the slide piston in the event of a power failure in the control position, so the tensioning device does not release immediately. It would be conceivable the latch with two scans for proper Monitor snapping to ensure the correct one Switching the directional spool signal to tap. This is useful for embodiments where the control pressure does not have the pressure tap but tapped elsewhere on the pressure reducing valve becomes. Alternatively, the actuating magnets could or the spool is monitored with position sensors.
  • the directly controlled pressure reducing valve according to claim 8 is characterized by a few individual parts, a compact one Construction and high reliability because of the pressure switching device Actuated directly by the control piston via the tappet becomes. If the control spring of the The pressure switching device needs a pressure reducing valve not to be adjusted separately.
  • the pressure reducing valve can be used universally for use hydraulic control devices where for pressure monitoring using a pressure switching device a rule print is available.
  • the execution according to claim 9 has the advantage of direct actuation of the Pressure switch through the control piston.
  • the pressure reducing valve consists of only a few individual parts and builds compact.
  • the movement or position of the control piston mechanically via the tappet transfer to the pressure switch plunger.
  • the tappet does not become pressure-dependent, but depends on the path Control piston adjusted. It can be the pressure switch Arrange sideways, what compact dimensions of the pressure reducing valve and an exact adjustment of the pressure switch enables.
  • Movement transmission is structurally simple according to claim 12. It can be a conventional one Control pistons are used because of the spring abutment the coupling takes over.
  • control pressure either directly from the one charged Consumer line or derived directly in the pressure reducing valve.
  • the pressure reducing valve can also be used for other operating modes be used where the control pressure not derived from the way to the consumer becomes.
  • the embodiment according to claim 14 is universal different modes of operation customizable by each required channel connected, the other is closed.
  • An electrohydraulic control device S according to FIG. 1 is used for the safety-monitored actuation of a Machine tool component K, like a double-acting one Hydraulic cylinder of a tensioning device Automatic lathes.
  • Constant pump 1 sucks from a tank 2 and charges against a pressure relief valve via a pressure line 3 a pressure accumulator 4. From the pressure line 3 branches a line 3a to a pressure reducing valve V.
  • a return line 5a leads from the pressure reducing valve V. a return line 5 and to the tank 2.
  • With the pressure reducing valve V is a pressure switch device D structurally connected.
  • the pressure reducing valve V is on the outlet side via a line 6 to a directional valve W, namely one 4/2 directional spool, connected, from which a return line 5b leads to the return line 5 (connections P and T on the directional valve W).
  • the directional valve W is on the output side via consumer lines 11, 12 with the machine tool component K connected (connections A and B).
  • the directional valve W has a consumer pressure tap Z (indicated schematically in the directional valve symbol), via a control line 7 with a control input 20 of the pressure reducing valve V is connected.
  • the directional valve W contains a slide piston 8 by two actuating magnets 9, 10 between two control positions a and b is convertible. In intermediate positions between the the two control positions is the pressure tap Z with the Return line 5b connected and the control line 7 depressurized.
  • the structure of the pressure reducing valve V is shown in FIG. 2 and 3 (1st embodiment) can be seen in detail.
  • the Pressure reducing valve V contains 13 in a housing bore a control piston 14 with two control edges 15 which are aperture-like the output connected to line 6, which cuts the housing bore 13 with its mouth 18, alternately with a pressure connection 19 (to the Line 3a connected) and a tank connection 17 (to the return line 5a connected) connects to Output 6 to set a certain pressure.
  • the control piston 14 has a piston end 16 which with the Control input 20 fed control pressure can be applied is opposite to the force of a spring 22, which are arranged in a pressure-relieved chamber 28 and is adjustable in its bias, and the control piston 14 applied via a spring abutment 23.
  • a groove 24 is provided, into which a Head part 27 in a parallel to the housing bore 13 Bore 25 displaceable plunger 26 in a form-fitting manner intervenes.
  • the plunger 26 is mechanical via the spring abutment 23 motion transmitting with the control piston 14 coupled.
  • the plunger 26 is sealed to one pressure ram 28 guided out of the bore 25, with which a pressure switch 29 of the pressure switching device D can be actuated.
  • Two channels 30, 32 are via a connecting channel 33 connected to the control input 20.
  • the channel 30 intersects the mouth 18 and then the channel 33.
  • the channel 32 leads to a connection 7 'in the outside of the pressure reducing valve V to which the control line 7 can be connected is.
  • the channel is 30 by a plug between the mouth 18 and the channel 33 shut off and to the outside by a screw plug 31 sealed.
  • the connection 7 ' is open and connected to the control line 7. Will the Port 7 'closed, then the connection to Mouth 18 opened so that the control input 20 with the Control pressure is fed from outlet 6.
  • To the connection 7 'a control line could also be connected be the higher one via a shuttle valve Consumer pressure in one of the two consumer lines 11, 12 leads.
  • the spring 22 could be a progressive spring arrangement Be characteristic. For this purpose, several can be done in stages springs to come into effect are provided or one with differently wound sections Feather.
  • a progressive characteristic has the advantage that the switching pressure of the pressure switch 29 with increasing Flow rate or near increasing working pressure is at the working pressure.
  • the flow pockets 41 are offset in the circumferential direction two diametrically opposed longitudinal channels 44 (milled grooves in the sealing section 42) provided that connected to each other via an oblique through hole 48 are.
  • On the one longitudinal channel 44 (in FIG. 5 below) is a control channel mouth 45 in the slide bore 34 aligned with a control channel 51 (with the Control line 7 connected) belongs.
  • the opposite Longitudinal channel 44 is cut by a transverse slot 49, the movement of the slide piston 8th runs over a tank connection 46 of a tank channel 50 and then a flow connection between the longitudinal channels 44 and the return line 5b (Fig. 1) produces about which the control line 7 is relieved of pressure.
  • the tank connection 46 is offset to the side relative to the longitudinal channel 44, so that it is only run over by the transverse slot 49.
  • the spool 8 is in its Control position b shown, in which the outlet 40 with the Inlet 38 is connected, while the outlet 39 with the Tank connection 43 is connected.
  • the one in the consumer line 12 prevailing pressure is the control pressure of the Control channel mouth 45 abandoned, so that it over the Control line 7 to the control input 20 of the pressure reducing valve (Fig. 1) is transmitted.
  • the pressure reducing valve with a single control element namely the adjusting screw for the preload of the spring or spring arrangement 22 the setting of the pressure reducing valve and the pressure switching device D synchronously are changeable.
  • the control piston e.g. 14 in Fig. 2
  • the pressure reducing valve V at the same time as the measuring piston of the pressure switch 29 used because between the control piston and the pressure switch no further, pressure-dependent adjustable element is provided.
  • control piston has 14 'of the pressure reducing valve V' at its the control input 20 adjacent end a molded axial Tappet 54, which is aligned with the pressure switch 29 is and operated it.
  • the plunger 54 penetrates one Sealing arrangement of the housing bore.
  • the control pressure is here derived from output 6 via channel 30, 33. Is this channel is closed, then the control input 20 also as shown to the pressure tap Z in Fig. 1 or also directly to the two consumer lines via a shuttle valve 11, 12 may be connected.
  • W a 4/3 directional spool can be provided (indicated in Fig. 1).
  • the consumer pressure tap Z is excluded in the correct tax position or positions (a and / or b) - either by connection with the Tank connection or by a connection to the tank connection or through a connection with the straight with the Return line open consumer line unloaded.
  • the middle position is above the Slide the control line for the control pressure directly connected to the return line while either both consumer lines blocked or connected together the return line are connected.
  • Will rule pressure derived only in a tax position then the Control line in the other control position with the straight one connected to the return open consumer line and relieved.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Fluid Pressure (AREA)
  • Gripping On Spindles (AREA)
  • Servomotors (AREA)
  • Multiple-Way Valves (AREA)
EP94900117A 1992-11-10 1993-11-09 Elektrohydraulische steuervorrichtung und druckminderventil Expired - Lifetime EP0620932B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4237901A DE4237901C2 (de) 1992-11-10 1992-11-10 Elektrohydraulische Steuervorrichtung und Druckminderventil
DE4237901 1992-11-10
PCT/EP1993/003129 WO1994011797A1 (de) 1992-11-10 1993-11-09 Elektrohydraulische steuervorrichtung und druckminderventil

Publications (2)

Publication Number Publication Date
EP0620932A1 EP0620932A1 (de) 1994-10-26
EP0620932B1 true EP0620932B1 (de) 1998-07-29

Family

ID=6472511

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94900117A Expired - Lifetime EP0620932B1 (de) 1992-11-10 1993-11-09 Elektrohydraulische steuervorrichtung und druckminderventil

Country Status (8)

Country Link
EP (1) EP0620932B1 (enrdf_load_stackoverflow)
JP (1) JP3632927B2 (enrdf_load_stackoverflow)
KR (1) KR100238784B1 (enrdf_load_stackoverflow)
AT (1) ATE169132T1 (enrdf_load_stackoverflow)
DE (1) DE4237901C2 (enrdf_load_stackoverflow)
ES (1) ES2119145T3 (enrdf_load_stackoverflow)
TW (1) TW273588B (enrdf_load_stackoverflow)
WO (1) WO1994011797A1 (enrdf_load_stackoverflow)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE9413273U1 (de) 1994-08-17 1994-10-06 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Spannmodul für Werkzeugmaschinen-Spannvorrichtung
DE29518705U1 (de) 1995-11-24 1996-01-18 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Spannmodul
DE29605911U1 (de) * 1996-03-29 1997-07-24 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Elektrohydraulische Steuervorrichtung
DE19637256A1 (de) * 1996-09-13 1998-03-19 Index Werke Kg Hahn & Tessky Werkstückspindeleinrichtung für eine Werkzeugmaschine
DE29808294U1 (de) 1998-05-07 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Elektrohydraulischer Spannmodul
DE29808295U1 (de) 1998-05-07 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Sitzventil
DE19935473B4 (de) * 1999-07-13 2006-02-02 Bosch Rexroth Aktiengesellschaft Hydraulisches Druckregelventil
CN103437752B (zh) * 2013-09-12 2015-10-21 中煤科工集团西安研究院有限公司 一种用于煤矿坑道钻机远程液控系统

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2249743A1 (de) * 1972-10-11 1974-04-18 Kloeckner Humboldt Deutz Ag Ventilaggregat
DE2310193C2 (de) * 1973-03-01 1974-11-21 Index-Werke Kg Hahn & Tessky, 7300 Esslingen Sicherheits-Druckregelventil zur Einstellung eines konstanten Arbeitsdrukkes
DE2602844B2 (de) * 1976-01-27 1978-08-17 Eisenwerk Weserhuette Ag, 4970 Bad Oeynhausen Elektrisch gesteuertes Druckregelventil
DE3039002C2 (de) * 1980-10-15 1983-02-10 Lutz 7306 Denkendorf Leupold Druckregelventil
DE3204055C2 (de) * 1982-02-06 1984-06-28 Lutz 7306 Denkendorf Leupold Druckbegrenzungs- oder -regelventil
DE3532592A1 (de) * 1985-09-12 1987-03-19 Rexroth Mannesmann Gmbh 3-wege-druckminderventil mit sekundaerdruckueberwachung
DE3918418A1 (de) * 1989-04-17 1990-10-18 Rexroth Mannesmann Gmbh Elektrische messwerterfassung fuer ein regelventil
ES2027502A6 (es) * 1990-11-19 1992-06-01 Bendix Espana Valvula reguladora de presion de fluido.

Also Published As

Publication number Publication date
JPH07502936A (ja) 1995-03-30
TW273588B (enrdf_load_stackoverflow) 1996-04-01
KR100238784B1 (ko) 2000-01-15
JP3632927B2 (ja) 2005-03-30
ATE169132T1 (de) 1998-08-15
ES2119145T3 (es) 1998-10-01
EP0620932A1 (de) 1994-10-26
DE4237901A1 (de) 1994-05-11
WO1994011797A1 (de) 1994-05-26
DE4237901C2 (de) 1996-02-01

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