EP0620932A1 - Dispositif de commande electrohydraulique et vanne de detente - Google Patents

Dispositif de commande electrohydraulique et vanne de detente

Info

Publication number
EP0620932A1
EP0620932A1 EP94900117A EP94900117A EP0620932A1 EP 0620932 A1 EP0620932 A1 EP 0620932A1 EP 94900117 A EP94900117 A EP 94900117A EP 94900117 A EP94900117 A EP 94900117A EP 0620932 A1 EP0620932 A1 EP 0620932A1
Authority
EP
European Patent Office
Prior art keywords
control
pressure
reducing valve
pressure reducing
piston
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
EP94900117A
Other languages
German (de)
English (en)
Other versions
EP0620932B1 (fr
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
Application filed by Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG filed Critical Heilmeier and Weinlein Fabrik fuer Oel Hydraulik GmbH and Co KG
Publication of EP0620932A1 publication Critical patent/EP0620932A1/fr
Application granted granted Critical
Publication of EP0620932B1 publication Critical patent/EP0620932B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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 electrohydraulic control device according to the preamble of claim 1 and a directly controlled pressure reducing valve according to the preamble of claim 8.
  • a control signal of the machine tool is transmitted when the required clamping pressure is present, or an error signal is transmitted when the clamping pressure falls below. If the clamping pressure is not reached, the good signal remains off.
  • the clamping pressure is controlled via a pressure reducing valve independently of a supply pressure and its pressure value on the pressure reducing valve is adjusted to the respective requirement. Different workpieces or different materials of the workpieces require different clamping pressures.
  • a directly controlled pressure reducing valve in which, in addition to the control piston, a separate pot piston loaded by its own spring is provided which, as a measuring piston, actuates a pressure switch independently of pressure.
  • a directly controlled pressure reducing valve in an electrohydraulic control device in which, in addition to the control piston, a separate throttle piston is provided as a measuring piston for actuating two pressure switches.
  • the throttle piston is centered with two springs.
  • the control pressure is derived at the outlet of the pressure reducing valve.
  • the pressure switch is actuated by the pilot valve of the control piston of the pressure reducing valve.
  • the control pressure for the control piston and for the closing element of the pilot valve is derived from the consumer line, which is acted upon by the directional control valve, via a shuttle valve common to both consumption lines.
  • a pressure reducing valve known from DE-C-23 10 193 in an electrohydraulic control device of a machine tool component, this is from the control spring and the control pressure applied to the control piston are arranged inside an auxiliary piston, which is adjusted independently of the force of the control spring and actuates a pressure switch as a measuring piston.
  • the control pressure for the control piston is derived upstream of the downstream directional control valve.
  • the switching pressure for the auxiliary piston and the pressure switch is derived from the pressurized consumer pressure line via a control line and a prestressed check valve.
  • Two control lines with check valves and a common leakage line with a discharge throttle are required for the safety function.
  • the invention has for its object to provide an electro-hydraulic control device of the last-mentioned type and a directly controlled pressure reducing valve which is also suitable for such a control device, which are structurally simple and nevertheless very reliable with regard to the desired safety function and only from a few , there are the number of individual parts reducing potential sources of error.
  • the pressure reducing valve should also be universally usable in other control devices in which pressure is monitored by a pressure switching device.
  • the control pressure is structurally simple in the directional control valve and tapped there only if the directional valve has ordinarily connected a consumer line to the outlet of the pressure reducing valve.
  • a separate monitoring of the directional control 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 switch device is only actuated when the directional valve is functioning properly. When the pressure reducing valve is adjusted, the pressure switching device can also be adjusted to the new requirement.
  • a control pressure which causes the pressure switching device to respond will also be generated for the pressure reducing valve.
  • the pressure switch device does not emit a good signal or an error signal, so that a warning is given or measures to prevent damage can be taken.
  • the control pressure is only derived in the pressure tap when the directional control valve has possibly been adjusted so far, if possible, that the correct supply of the tensioning device is reliably ensured. Since the tensioning pressure of the tensioning device is the most important criterion for safety, it is expedient to derive the regulating pressure to reduce the supply pressure only when the consumer line for tensioning the tensioning device is acted on.
  • the pressure can be reduced and the supply pressure used to loosen the clamping device.
  • no control pressure is diverted from the outlet of the pressure reducing valve, so that the pressure reducing valve then opens fully and does not intervene in a regulating manner.
  • the directly controlled pressure reducing valve is characterized by a few individual parts, a compact structure and high reliability, since the pressure switching device is actuated directly by the control piston via the tappet.
  • the pressure switching device When the control spring of the pressure reducing valve is adjusted, the pressure switching device need not be readjusted separately. Since the response of the pressure switching device necessary for the safety function is ensured regardless of how and which control pressure adjusts the control piston, the pressure reducing valve can be used universally for hydraulic control devices in which a control pressure is used for pressure monitoring by means of a pressure switching device Available.
  • the measure according to claim 3 ensures that no control pressure is generated in intermediate positions and / or in a central position of the directional control valve, but that any existing pressure is even reduced. The easiest way to release the pressure is to connect it to the return.
  • a co Most cost-effective 4/2 or 4/3 directional spool valve is used, which has a control channel in the housing, the mouth of which is part of the consumer pressure tap. No modification of the basic concept of the directional spool valve is required to accommodate the pressure tap. If required, the pressure tap can be used for only one or for both consumer lines; in the opposite case, it is deactivated by plugging.
  • the longitudinal channel is cut or milled into the slide piston for the pressure tap in each or only one control position.
  • the design and arrangement of the longitudinal channel ensures that no control pressure is derived in intermediate positions, and that the pressure switching device only generates a signal when the directional spool has switched properly to passage. An additional monitoring of the consumer lines is saved.
  • the pressure relief is ensured directly via the transverse slot to the tank connection. If the pressure tap is not used, the tank connection can be closed.
  • the directional spool and the pressure reducing valve can be arranged with the switching device in a common, compact housing.
  • the measure of claim 7 is important so that the flow paths are always opened and closed in the predetermined manner.
  • the latching device keeps the spool in the control position in the event of a power failure, and thus the tensioning device does not release immediately. It would be conceivable to monitor the latching device with two scans for proper latching in order to tap a signal representing the correct switching of the directional spool. This is expedient for embodiments in which the regulating pressure is tapped not at the pressure tap but at another point on the pressure reducing valve. Alternatively, the actuating magnets or the spool could be monitored with position sensors.
  • the embodiment of the pressure reducing valve according to claim 9 has the advantage of direct actuation of the pressure switch by the control piston.
  • the pressure reducing valve consists of only a few individual parts and is compact.
  • the movement or position of the control piston is mechanically transmitted via the plunger to the pressure switch plunger.
  • the tappet is not adjusted depending on the pressure, but rather depending on the travel of the control piston.
  • the pressure switch can be arranged on the side, which enables compact dimensions of the pressure reducing valve and an exact adjustment of the pressure switch.
  • the progressive characteristic of the spring or spring arrangement allows the smallest possible pressure difference at the switching point of the pressure switch, e.g. when building up pressure at the outlet of the pressure reducing valve or when changing the flow rate.
  • the transmission of motion is structurally simple in the embodiment according to claim 12.
  • a conventional Licher control piston are used because the spring abutment takes over the coupling.
  • control pressure is derived either directly from the consumer line in question or directly in the pressure reducing valve.
  • the pressure reducing valve can also be used for other modes of operation in which the control pressure is not derived from the way to the consumer.
  • the embodiment according to claim 14 is universally adaptable to different modes of operation by connecting the respectively required channel and closing the other.
  • 1 is a block diagram of an electrohydraulic control device
  • Fig. 7 shows a section of a modified
  • FIG. 8 shows a section of a further modified embodiment of the pressure reducing valve.
  • An electrohydraulic control device S according to FIG. 1 is used for the safety-monitored actuation of a machine tool component K, such as a double-acting hydraulic cylinder of a clamping device of an automatic lathe.
  • An air-cooled constant pump 1 driven by a motor M draws in from a tank 2 and charges a pressure accumulator 4 against a pressure limiting valve via a pressure line 3.
  • a line 3a branches off from the pressure line 3 to a pressure reducing valve V.
  • a return line 5a leads from the pressure reducing valve V to a return line 5 and to the tank 2.
  • a pressure switching device D is structurally connected to the pressure reducing valve V.
  • the pressure reducing valve V is connected via a line 6 to a directional valve W, specifically a 4/2 directional spool, from which a return line 5b leads to the return line 5 (connections P and T on the directional valve W).
  • the directional control valve W is connected to the machine tool component K via consumer lines 11, 12 (connections A and B).
  • the directional control valve W has a consumer pressure tap Z (indicated schematically in the symbol of the directional control valve), which is connected via a control line 7 to a control input 20 of the pressure reducing valve V.
  • the directional control valve W contains a spool 8 which can be switched between two control positions a and b by means of two actuating magnets 9, 10. In intermediate positions between the In both control positions, the pressure tap Z is connected to the return line 5b and the control line 7 is depressurized.
  • the structure of the pressure reducing valve V can be seen in detail from FIGS. 2 and 3 (1st embodiment).
  • the pressure reducing valve V contains in a housing bore 13 a control piston 14 with two control edges 15, which in the manner of an aperture connects the outlet connected to line 6, which cuts the housing bore 13 with its mouth 18, alternately with a pressure connection 19 (to line 3a connected) and a tank connection 17 (connected to the return line 5a) to set a certain pressure in the outlet 6.
  • the control piston 14 has a piston end 16, which can be acted upon by the control pressure fed in at the control input 20, counter to the force of a spring 22, which is arranged in a pressure-relieved chamber 28 and whose prestress is adjustable, and the control piston 14 acted upon by a spring abutment 23.
  • a groove 24 is provided in the spring abutment 23, in which a head part 27 of a plunger 26, which can be displaced in a bore 25 parallel to the housing bore 13, engages in a form-fitting manner.
  • the plunger 26 is mechanically coupled to the control piston 14 via the spring abutment 23 in a motion-transmitting manner.
  • the tappet 26 is aligned with a pressure tappet 28 which is sealed out of the bore 25 and by means of which a pressure switch 29 of the pressure switching device D can be actuated.
  • Two channels 30, 32 are connected to the control input 20 via a connecting channel 33.
  • the channel 30 cuts 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.
  • the channel 30 is blocked by a plug between the mouth 18 and the channel 33 and sealed off from the outside by a screw plug 31.
  • the terminal 7 ' is open and connected to the control line 7. If the connection 7 'is closed, then the connection to the mouth 18 is opened so that the control input 20 is fed with the control pressure from the output 6.
  • a control line could also be connected to the connection 7 ', which leads the respective higher consumer pressure in one of the two consumer lines 11, 12 via a shuttle valve.
  • the spring 22 could be a spring arrangement with a progressive characteristic.
  • a plurality of springs which act in steps or a spring provided with differently wound sections can be provided.
  • a progressive characteristic curve has the advantage that the switching pressure of the pressure switch 29 is close to the working pressure with increasing delivery rate or with increasing working pressure.
  • the slide piston 8 is guided in a sealed, displaceable manner and displaceable by means of a plunger 37.
  • the plungers 37 are adjusted by the actuating magnets 9, 10.
  • a latching device 36 mechanically secures the two control positions of the spool piston 35.
  • In the slide bore 34 there is a central inlet 38 connected to the outlet 6 of the pressure reducing valve V, on the two sides of which outlets 39, 40 are arranged in the form of turned grooves .
  • a tank connection 43, T is provided, to which the return line 5b (FIG. 1) is connected.
  • two diametrically opposite flow pockets 41 are formed, which are connected internally in the slide piston 8 and in each control position connect the inlet 38 to an outlet 39 or 40, while via one Constriction 35 in the spool 8 of the other outlet 40, 39 is connected to the adjacent tank connection 43.
  • a flow pocket 41 on one side of the slide piston 8 would suffice; For reasons of pressure compensation and the smooth running of the slide piston 8, two diametrically opposite flow pockets 41 are expedient.
  • two diametrically opposed longitudinal channels 44 (milled grooves in the sealing section 42) are provided, which are connected to one another via an oblique through-bore 48.
  • a control anal orifice 45 in the slide bore 34 is aligned with the one longitudinal channel 44 (bottom in FIG. 5) and belongs to a control channel 51 (connected to the control line 7).
  • the opposite longitudinal channel 44 is cut by a transverse slot 49 which, when the slide piston 8 moves, passes over a tank connection 46 of a tank channel 50 and then establishes a flow connection between the longitudinal channels 44 and the return line 5b (FIG. 1), via 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 shown in its control position b, in which the outlet 40 with the Inlet 38 is connected, while the outlet 39 is connected to the tank connection 43.
  • the pressure prevailing in the consumer line 12 is given up as the control pressure of the control channel mouth 45, so that it is transmitted via the control line 7 to the control input 20 of the pressure reducing valve (FIG. 1).
  • the transverse slot 49 (FIG. 5) is to the right of the tank connection 46. In this way, not only is the correct pressure in the consumer line 12 reported as control pressure, but it is also ensured that the spool 8 has actually reached its correct control position b. If the spool 8 gets stuck in the intermediate position, for example without the latching device 36 having intervened, the control channel mouth 45 is connected to the tank via the transverse slot 49 and no control pressure is reported.
  • the setting of the pressure reducing valve and the pressure switching device D can be changed synchronously.
  • the control piston, e.g. 14 in FIG. 2 of the pressure reducing valve V is simultaneously used as the measuring piston of the pressure switch 29, because no further pressure-dependent adjustable element is provided between the control piston and the pressure switch.
  • control piston 14 'of the pressure reducing valve V has an integrally formed axial tappet 54 at its end adjacent to the control input 20, which is aligned with the pressure switch 29 and actuates it.
  • the plunger 54 penetrates one Sealing arrangement of the housing bore.
  • the control pressure is derived from output 6 via channel 30, 33. If this channel is closed, then the control input 20 can also be connected to the pressure tap Z in FIG. 1 as shown or directly to the two consumer lines 11, 12 via a shuttle valve.
  • the plunger 26 ' is, as in FIG. 2, coupled to the control piston 14 via the spring abutment.
  • the plunger 26' has a switching gate 56, on which a Probe arm 55 of a pressure switch 29 'abuts, which is arranged on the outside on one side of the pressure reducing valve V "and is part of the pressure switching device D.
  • a 4/3-way spool could be provided as the directional valve W (indicated in FIG. 1).
  • the consumer pressure tap Z is - except in the correct control position or positions (a and / or b) - either by the connection to the tank connection or by a connection to the tank connection or by a connection to the return line Open consumer line relieved.
  • the control line for the regulating pressure is connected directly to the return line in the middle position via the spool, while either both consumer lines are shut off or connected together to the return line. If control pressure is derived only in one control position, the control line in the other control position is connected to the load line which is just open to the return line and is 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)
  • Multiple-Way Valves (AREA)
  • Servomotors (AREA)

Abstract

Dispositif de commande électrohydraulique (S) pour système de serrage d'un tour automatique, comprenant une vanne de détente (V) raccordée à une source de pression (1), dont la sortie est reliée, par l'intermédiaire d'une vanne de distribution (W), à deux conduites utilisatrices alimentées alternativement (11, 12), un interrupteur manométrique (D) incorporé à la vanne de détente (V), et une entrée régulatrice (20) sollicitée par une pression de régulation, cependant qu'il est prévu, dans la vanne de distribution (W), une prise de pression utilisatrice (Z), où se présente la pression de régulation uniquement dans la position de commande (a et/ou b) de la vanne de distribution (W) pour laquelle la sortie (6) de la vanne (V) est convenablement reliée à une conduite utilisatrice (11, 12), ladite prise de pression (Z) étant reliée à l'entrée régulatrice (20). Il est prévu, dans la vanne de détente (V), entre le piston régulateur (14) et l'interrupteur manométrique (D), une liaison mécanique transférant le mouvement, au moyen de laquelle ledit interrupteur manométrique (D) est actionné directement par le piston régulateur (14) lorsqu'on atteint la pression de surveillance réglée par la force d'un ressort (22).
EP94900117A 1992-11-10 1993-11-09 Dispositif de commande electrohydraulique et vanne de detente Expired - Lifetime EP0620932B1 (fr)

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 (fr) 1992-11-10 1993-11-09 Dispositif de commande electrohydraulique et vanne de detente

Publications (2)

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

Family

ID=6472511

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94900117A Expired - Lifetime EP0620932B1 (fr) 1992-11-10 1993-11-09 Dispositif de commande electrohydraulique et vanne de detente

Country Status (8)

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

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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
DE29808295U1 (de) 1998-05-07 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Sitzventil
DE29808294U1 (de) 1998-05-07 1998-08-13 Heilmeier & Weinlein Fabrik für Oel-Hydraulik GmbH & Co KG, 81673 München Elektrohydraulischer Spannmodul
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

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Also Published As

Publication number Publication date
ES2119145T3 (es) 1998-10-01
EP0620932B1 (fr) 1998-07-29
TW273588B (fr) 1996-04-01
ATE169132T1 (de) 1998-08-15
KR100238784B1 (ko) 2000-01-15
DE4237901A1 (de) 1994-05-11
DE4237901C2 (de) 1996-02-01
JPH07502936A (ja) 1995-03-30
WO1994011797A1 (fr) 1994-05-26
JP3632927B2 (ja) 2005-03-30

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