EP2855946A1 - Valve destinée à un ensemble de valves - Google Patents

Valve destinée à un ensemble de valves

Info

Publication number
EP2855946A1
EP2855946A1 EP13722998.5A EP13722998A EP2855946A1 EP 2855946 A1 EP2855946 A1 EP 2855946A1 EP 13722998 A EP13722998 A EP 13722998A EP 2855946 A1 EP2855946 A1 EP 2855946A1
Authority
EP
European Patent Office
Prior art keywords
valve
stage
pressure
load
relief
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
EP13722998.5A
Other languages
German (de)
English (en)
Other versions
EP2855946B1 (fr
Inventor
Philipp Hilzendegen
Peter Bruck
Dominique DEHLINGER
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.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik 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 Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP2855946A1 publication Critical patent/EP2855946A1/fr
Application granted granted Critical
Publication of EP2855946B1 publication Critical patent/EP2855946B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/166—Controlling a pilot pressure in response to the load, i.e. supply to at least one user is regulated by adjusting either the system pilot pressure or one or more of the individual pilot command pressures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/024—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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/004—Cartridge 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
    • F15B2211/20—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
    • F15B2211/30—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
    • F15B2211/305—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
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and output member
    • 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/3059—Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595—Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • 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
    • F15B2211/50527—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 using cross-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
    • F15B2211/505—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6052—Load sensing circuits having valve means between output member and the load sensing circuit using 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control 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
    • F15B2211/70—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
    • F15B2211/7058—Rotary output members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2559—Self-controlled branched flow systems
    • Y10T137/2574—Bypass or relief controlled by main line fluid condition
    • Y10T137/2579—Flow rate responsive
    • Y10T137/2589—Pilot valve operated
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/7722—Line condition change responsive valves
    • Y10T137/7758—Pilot or servo controlled
    • Y10T137/7762—Fluid pressure type
    • Y10T137/7769—Single acting fluid servo
    • Y10T137/777—Spring biased

Definitions

  • the invention relates to a valve for a valve arrangement for pressure control of a fluid in a hydraulic system for pressure supply at least one hydraulic consumer comprising a pilot stage and a main control stage for at least partially releasing or blocking a fluid path from a supply port to a drain port, a discharge stage for pressure relief between the pre-control and the main control stage arranged fluid space, wherein the relief stage compares the at one of the at least one hydraulic load associated load connection pending load pressure with the discharge pressure at the drain port and releases the pressure relief on approach or equality of both pressures.
  • Such a valve is known, for example, from WO 201 1/045063 A1 and is used to adapt the pumped fluid flow and the supply pressure to the requirements of the at least one hydraulic consumer.
  • a hydraulic load-sensing system reports the load pressure, in the case of several hydraulic consumers the highest load pressure, back to the valve and takes it into account in the pressure control so that at a load pressure close to or equal to the discharge pressure via the discharge stage a so-called depressurized circulation is set.
  • the discharge stage closed again and the pre-tax and the main tax level take their respective control position. In this way, the power loss in the hydraulic system for pressure supply of the at least one hydraulic consumer can be reduced.
  • the present invention has the object to simplify the construction of the valve and to make the valve more functions accessible. This object is achieved by a valve having the features of claim 1 in its entirety.
  • the discharge stage can be connected directly to the load connection and load pressure, both the transfer of the load pressure to the discharge stage and the valve integrated pressure relief of Fluid idraums with a few, to be formed in a simple manner pressure - or Fl u idid connections be realized.
  • the valve has a valve housing with at least one in this, preferably as a bore, formed connecting line from Lastanschuss to the discharge stage. Via the connecting line, the load pressure applied to the load connection can be led directly to the unloading stage, ie without the passage or passage of further fluid spaces. With further fluid spaces possibly associated delays or interference during operation of the valve according to the invention are avoided.
  • a particularly compact design of the valve is achieved if at least one of the stages comprises a valve piston, which is arranged displaceably in a respective piston chamber in the valve housing and is preferably biased.
  • the discharge chamber associated with the piston chamber is at one end with the load pressure, which is typically present in a load-sensing line, and at the other end acted upon by the discharge pressure or acted upon.
  • the relief stage can be used as a slide or seat valve be formed, wherein the valve piston or the valve element is arranged and biased such that a fluid drain from the fluid chamber to the pressure relief at no or only a small load pressure can be released.
  • the pump pressure can be transmitted to the fluid space via the main control stage, preferably via a through bore formed in the corresponding valve piston.
  • the fluid space is fluidly connected to the controllable through the relief stage pressure relief, according to the ratio between the two pending at the relief stage pressures, the load pressure and the discharge pressure, this one releasing the pressure relief of the fluid space or assumes a blocking position.
  • the fluid space can be subdivided into a first subspace assigned to the pilot stage and a second subspace assigned to the main control stage, wherein a throttle is preferably arranged between the two subspaces.
  • a choke arranged between the second subspace and the first subspace of the fluid space can thus serve as an attenuator for the desolvation stage.
  • the relief stage controls a connection from the fluid space, in particular from the second subspace, to a discharge line assigned to the discharge port.
  • a connecting line from the pilot stage to the discharge line is provided in a fluid-conducting manner. Via the connecting line, a pressure relief of a corresponding piston chamber of the pilot stage can take place. This connection line can be led from the second piston chamber to the relief line in the valve housing. If a further connecting line is provided from the fluid space, in particular from the first subspace, to the load connection, a further throttle is preferably arranged in the further connecting line.
  • a desired pressure level between the fluid chamber and the load port can be adjusted.
  • fluid such as hydraulic oil
  • the valve according to the invention can regulate a corresponding load pressure when connecting the load connection to a hydraulic consumer.
  • the relief stage releases a load-sensing line for load pick-off at the at least one hydraulic consumer.
  • the relief stage can be arranged, for example, in parallel arrangement to the pilot control and main control stage between a pump and a container for fluid.
  • the discharge stage can be directly piloted, but it is also conceivable to form the discharge stage as an electrically operable 2/2-way valve, which can be controlled, for example, by a control and / or regulating device processing the signals of a pressure sensor.
  • the invention further comprises a valve arrangement for pressure regulation of a fluid supplied in a hydraulic system for supplying pressure to at least one hydraulic consumer, with at least one valve according to the invention.
  • FIG. 1 shows a valve arrangement for pressure control of a guided in a hydraulic system for supplying pressure to two hydraulic consumers fluid, with a valve according to the invention shown in section;
  • Fig. 3 is an enlarged detail of Fig. 2b.
  • FIG. 1 shows a valve arrangement 10 with a closed, hydraulic circuit for supplying two hydraulic consumers 12a, 12b with fluid.
  • Fluid is conveyed with a designed as a fixed displacement pump 14 from a reservoir 16 to the hydraulic consumers 12a, 12b, which are each designed as a hydraulic motor with two possible flow directions.
  • a valve 18 By means of a valve 18 according to the invention, the hydraulic circuit from the pump 14 and the hydraulic consumers 12a, 12b is closed.
  • the hydraulic consumers 12a, 12b are each controlled via an electrically operated 4/3-way valve 20a, 20b.
  • a shuttle valve 22a, 22b of the respective hydraulic consumers 12a, 12b applied load pressure in a load-sensing (LS) line 26a, 26b is reported.
  • LS load-sensing
  • This valve control is preceded by a 2/2-way valve 24a, 24b with a pressure limiting function in the open switching position.
  • the volume flow of the fluid delivered by the pump 14 is regulated via the valve 18.
  • This combination of a fixed displacement pump with the valve 18 for pressure control is a cost-effective alternative to a variable displacement pump.
  • each check valve 28a, 28b In the load sensing on the respective hydraulic load 12a, 1 2b provided load sensing lines 26a, 26b, a check valve 28a, 28b is connected in the hydraulic circuit before each shuttle valve 22a, 22b, each check valve 28a, 28b has the same set opening pressure and in the direction of the valve 18, more precisely in the direction of the load-sensing connection LS opens.
  • the valve 18 is connected via its Lastanschi uss LS with the load-sensing lines 26 a, 26 b and connectable.
  • the valve 18 is connected with its supply connection P to the supply line 29 which is supplied with pressure by the pump 14 and leads to the hydraulic consumers 12a, 12b, and with its discharge connection T to a reservoir 16, which may be a pressure medium container or a tank or connectable.
  • the valve 18 is an independent, tradeable unit and can be used as needed in the valve assembly 10.
  • FIGS. 2a-2d The design of the valve 18 is shown in FIGS. 2a-2d, which in each case shows in section the valve 18 with a cartridge-like valve housing 30 designed as a screw-in valve.
  • a first piston space 32 Coaxially to the axis of rotation R, in the valve housing 30, a first piston space 32, a fluid space 34, which is arranged in a first subspace 35b and a second subspace 35a. is divided, and a second piston chamber 36 is formed.
  • a pilot stage 48 are formed in the first piston chamber 32.
  • a third in the valve housing 30 formed piston chamber 52. Parallel to the fluid chamber 34 and with this, more precisely with the second subspace 35a, via a connection 60 fluidly or pressure-carrying connected. Slidably disposed in the third piston chamber 52 and biased by a third spring element 56 is a Valve piston of the relief stage 54.
  • the third piston chamber 52 is connected via a connecting line 61 to the load port LS and via a discharge line 62 to the drain port T, so that at the discharge stage 54 the load pressure and the discharge pressure are present.
  • the relief stage 54 compares the load pressure with the discharge pressure and, as soon as the load pressure at the load connection LS is close to or equal to the discharge pressure at the discharge connection T, opens a bypass for pressure relief of the fluid rail 34.
  • the bypass is realized by a connection 60 between the fluid space 34 and the discharge line 62 leading to the discharge port T, the connection 60 being releasable by the valve piston of the relief stage 54, as shown in FIGS. 2 b and 2 c. or, as shown in Figs. 2a and 2d, is closable.
  • an annular groove 58 formed therein is arranged in the crossing region between the third piston chamber 52 directed parallel to the axis of rotation R and the connection 60 extending transversely to the third piston chamber 52 or to the axis of rotation R.
  • the open position cf. 3, fluid from the fluid space 34 via the connection 60, at the annular groove 58 of the valve piston of the discharge stage 54 over, drain via the discharge line 62 to the drain port T.
  • valve piston assigned to the pilot stage 48 acted on by the second spring element 50, abuts against a valve seat formed at the corresponding end of the fluid chamber 54 or the first sub-chamber 35 b.
  • the valve piston assigned to the main control stage 38 acted on by the first spring element 40, is arranged in the valve housing 30 such that a fluid path 40 from the supply port P is blocked via radial passage openings 42 which are formed in a section of the valve housing 30.
  • the load pressure present at the load connection LS exceeds the discharge pressure or tank pressure present at the discharge connection T, so that the third spring element 56 acting on the valve piston of the discharge stage 54 is compressed and the bypass for pressure relief, here the connection 60, is closed, in other words closed ,
  • valve piston moves into the position releasing the connection 60 as shown in FIGS. 2b and 2c.
  • a fluid path from the supply connection P or pump connection to the drain connection T or tank connection is released.
  • the valve piston of the main control stage 38 is in the representation of Fig. 2c in its maximum fluid path releasing position and abuts a formed on the valve housing 30 valve seat.
  • Via a further connection 60 ', which, designed as a bore, is guided from the second piston chamber 36 to the relief line 62 in the valve housing 60, fluid can also flow out of this fluid space to the outlet connection T.
  • the fluid pressure present at the main control stage 38 on the pump side can be transferred to the fluid space 34 between the main control stage 38 and the pilot stage 48.
  • the relief stage 54 and correspondingly the connection 60 are closed from the fluid space 34 to the discharge port T and the precursor stage 48 is opened by the increasing fluid pressure in the fluid space 34, as shown in FIG. 2d.
  • the valve or switching position of FIG. 2 a the blocking of the fluid path from the supply connection P to the discharge connection T, again occurs.
  • a further throttle 66 Via a further throttle 66, a pressure stage in the further connecting line 64 is specified.
  • the valve 18 offers as another function, in other words option, an outflow of fluid, such as hydraulic oil, via the further connecting line 64.
  • the valve 18 controls the corresponding load pressure, which Relief level 54 can be reduced as needed.

Abstract

L'invention concerne une valve (18) destinée à un ensemble de valves (10) pour la régulation de la pression d'un fluide transporté dans un système hydraulique pour une alimentation en pression d'au moins un utilisateur (12a, 12b) hydraulique, comprenant un étage pilote (48) et un étage principal (38) pour la libération au moins partielle ou le barrage du trajet d'un fluide provenant d'un raccordement d'alimentation (P) vers un raccordement de sortie (T), un étage de délestage (54) pour le délestage en pression d'une chambre de fluide (34) disposée entre l'étage pilote (48) et l'étage principal (38). L'étage de délestage (54) compare la pression de charge se situant à un raccordement de charge (LS), attribué à au moins un utilisateur (12a, 12b) hydraulique, avec la pression de sortie au raccordement de sortie et libère la détente de pression lors d'un rapprochement ou d'une égalisation des deux pressions. La valve est caractérisée en ce que l'étage de délestage (54) peut être raccordé directement au raccordement de charge (LS) et peut être soumis à une pression de charge.
EP13722998.5A 2012-05-25 2013-05-15 Valve destinée à un ensemble de valves Active EP2855946B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210010522 DE102012010522A1 (de) 2012-05-25 2012-05-25 Ventil für Ventilanordnung
PCT/EP2013/001438 WO2013174489A1 (fr) 2012-05-25 2013-05-15 Valve destinée à un ensemble de valves

Publications (2)

Publication Number Publication Date
EP2855946A1 true EP2855946A1 (fr) 2015-04-08
EP2855946B1 EP2855946B1 (fr) 2021-03-03

Family

ID=48446238

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13722998.5A Active EP2855946B1 (fr) 2012-05-25 2013-05-15 Valve destinée à un ensemble de valves

Country Status (4)

Country Link
US (1) US9677575B2 (fr)
EP (1) EP2855946B1 (fr)
DE (1) DE102012010522A1 (fr)
WO (1) WO2013174489A1 (fr)

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DE102015001755A1 (de) * 2015-02-11 2016-08-11 Hydac Fluidtechnik Gmbh Druckbegrenzungsventil
DE102017008359A1 (de) * 2017-09-06 2019-03-07 Hydac Fluidtechnik Gmbh Ventil
US11583455B2 (en) 2019-10-28 2023-02-21 Stryker Corporation Hydraulic valve and system
DE102021001960A1 (de) * 2021-04-14 2022-10-20 Hydac Fluidtechnik Gmbh Ventil
US11905782B2 (en) * 2022-01-27 2024-02-20 National Coupling Company, Inc. Regulator having check valve manifold for use in subsea control circuit

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DE102012010522A1 (de) 2013-11-28
EP2855946B1 (fr) 2021-03-03
US9677575B2 (en) 2017-06-13
US20150107699A1 (en) 2015-04-23
WO2013174489A1 (fr) 2013-11-28

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