EP2488764A1 - Agencement de soupape - Google Patents

Agencement de soupape

Info

Publication number
EP2488764A1
EP2488764A1 EP10768695A EP10768695A EP2488764A1 EP 2488764 A1 EP2488764 A1 EP 2488764A1 EP 10768695 A EP10768695 A EP 10768695A EP 10768695 A EP10768695 A EP 10768695A EP 2488764 A1 EP2488764 A1 EP 2488764A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
piston
pressure medium
pilot
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
EP10768695A
Other languages
German (de)
English (en)
Other versions
EP2488764B1 (fr
Inventor
Philipp Hilzendegen
Peter Bruck
Hermann Albert
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 EP2488764A1 publication Critical patent/EP2488764A1/fr
Application granted granted Critical
Publication of EP2488764B1 publication Critical patent/EP2488764B1/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
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow control valve
    • 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
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • 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
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87193—Pilot-actuated

Definitions

  • the invention relates to a valve arrangement for pressure control of a pressure medium from a pressure medium pump to at least a first consumer, with a pilot operated pressure control valve, acted upon by the pressure medium main piston and a pilot piston, wherein a pressure space between a piston rear side of the main piston and the pilot piston can be relieved.
  • Pressure control valves are used regularly. In this case, the not controlled by the pressure control valve pressure medium flow is discharged under relatively large power and pressure losses for a pressure medium pump via a pressure relief valve.
  • LS load-sensing pressure from the load tap of the consumer is present in a pressure chamber after the pilot piston.
  • the pump pressure can be essentially compared with the spring preload on the control piston plus the pressure at the load (LS) and at a decommissioning division of the consumer dissipate the pressure medium with less energy loss than when used with a pressure relief valve.
  • the power loss of such known pilot-operated pressure control valves with pressure compensator function can not be completely avoided.
  • DE 103 22 585 A1 describes a valve arrangement for regulating the pressure of a pressure medium from a pressure medium pump to a consumer, wherein a main control valve can be hydraulically actuated by a pilot valve.
  • a valve modular system with at least one valve housing having at its opposite ends both inside and outside the circumference and inside the housing standardized nominal sizes for attaching further valve components.
  • Such valve components may be a valve piston, an energy store, a pilot valve and at least one fluid port for defining the valve assembly formed in the manner of a Einschraubpatrone in an environment.
  • DE 10 2005 059 240 A1 shows and describes a hydrostatic drive system with a variable-stroke pressure medium pump which supplies a consumer with pressure medium via control valves.
  • a variable-stroke pressure medium pump which supplies a consumer with pressure medium via control valves.
  • serving as a recirculation pressure compensator is set to a minimum control pressure difference.
  • the pressure medium pump is set to a minimum delivery volume, wherein the pressure medium flow coming from the pressure medium pump via the pressure compensator flows with low power losses to a pressure medium container.
  • DE 689 08 31 7 12 describes a pressure control valve whose main valve is pilot-controlled by a pilot valve which is arranged in a common valve housing. Based on this prior art, the present invention seeks to provide a valve arrangement for pressure control of a pressure medium, which allows a further minimization of the pressure loss when no consumer is connected. This object is achieved with a valve arrangement having the features of patent claim 1 in its entirety.
  • a valve arrangement for pressure control of a pressure medium is provided by a pressure medium pump to a consumer, which provides a pilot-operated pressure control valve with a spring-loaded main piston.
  • a pilot piston which controls a valve seat for a fluid-carrying connection to a back pressure chamber of the main piston, is part of the pressure control valve.
  • the piston-back pressure chamber of the main piston is pressurized by the pump pressure via a first throttle in the main piston, so that the recirculation pressure compensator thus formed allows a comparison between the pump pressure and the pressure at the load tap plus the spring preloads of the main control piston and the pilot piston.
  • a by the respective set spring voltages higher pressure of the pressure medium pump than the pressure at the load tap of the consumer turns it.
  • it is further provided to arrange a relief valve for the space between the main piston and the pilot piston.
  • the relief valve is formed as a poppet or poppet valve, wherein a valve element of the relief valve is arranged such that at no pressure of the load tap, which corresponds to a de-operation division of the consumer, a pressure medium flow from the space between main piston and pilot piston to a pressure medium tank, tank or in the LS-line allows.
  • the relief valve When operating in non-pressurized circulation, the relief valve is open and the main valve can also be opened.
  • the pilot valve is closed.
  • the relief valve according to the invention thus enables a substantial reduction of the pressure losses of the valve assembly in comparison to the known circuits of circulation pressure compensators.
  • a second channel portion of the longitudinal channel is fluidly associated with the second pressure chamber, which is Deutschenfahrbar by the pilot piston.
  • the second throttle can serve as an attenuator for the relief valve.
  • the relief valve is arranged in the housing of the pressure control valve.
  • the valve element of the relief valve is axially movable in one Longitudinal bore out. Via at least one annular recess in the housing of the pressure regulating valve or in the valve element of the relief valve, a fluid-conducting connection to one or the other channel section of the longitudinal channel can be produced in at least one displacement position of the valve element.
  • the valve element of the relief valve is preferably biased by means of an energy accumulator (compression spring) in the direction of the second pressure chamber, which is passable by the pilot piston.
  • the pilot piston of the pilot valve can in this case control a fluid-conducting connection between a load tap LS and a free, the energy storage opposite side of the valve element of the relief valve.
  • the valve element of the relief valve blocks a fluid-conducting connection between the pressure chamber of the main piston and the pressure fluid reservoir.
  • the valve element of the relief valve is brought under the action of the energy storage in a movement position in which a direct fluid-conducting connection between the pressure chamber of the main piston is opened via the relief valve to the pressure medium container.
  • Pressure fluid flows through the annular recess on the relief valve.
  • the annular recess is connected to the second pressure chamber of the pilot piston or of the pressure chamber through which the pilot piston can carry fluid.
  • the relief valve can be arranged in parallel arrangement to the pressure regulating valve between a pressure medium pump and the pressure medium container.
  • the relief valve may be directly piloted, but it may also be advantageous to form the relief valve as an electrically operable 2/2-way valve, which is controlled for example by a pressure signals of a pressure sensor processing control and / or regulating device.
  • Fig.l b is a detail I in Figure 1 a;
  • Fig.l c is a schematic, not to scale longitudinal section through a valve assembly according to the invention with a relief valve in the control position of the main valve and the pilot valve with closed switching position of the relief valve;
  • Fig.ld a detail I in Fig.lc; a further embodiment of a pressure regulating valve according to the invention with a relief valve;
  • Fig. T f is a detail I in Fig.1 e;
  • FIG. 2 shows a hydraulic circuit diagram for a further embodiment of the valve arrangement according to the invention.
  • FIG. 3 shows a further hydraulic circuit diagram of a further embodiment of the valve arrangement with a connection of a relief valve after a first throttle and before a second throttle between the main control valve and the pilot valve of the pressure regulating valve; 4 and 5 further embodiments in the manner of a hydraulic
  • 1 a shows a closed, hydraulic circuit of a valve arrangement 1, with a constant-pressure medium pump 3 for supplying a consumer 4 with pressure medium 2.
  • the consumer 4 is shown as a hydraulic motor with two possible directions of flow.
  • the consumer 4 is driven by an electrically operated 4/3-way valve 19.
  • This valve control is preceded by a 2/2-way valve 20 with pressure limiting function in the open switching position.
  • two consumers 4 are connected in parallel with each identical valve control technology, which can be supplied by the constant-pressure medium pump 3.
  • the hydraulic system provides a constant-pressure fluid pump 3 as a cheaper alternative to a variable, but requires control of their flow to operate the consumer 4 with a predetermined speed can. It requires a flow control valve, in particular a pressure control valve, which overall represents a simpler overall solution, which incidentally is more cost-effective than that which results when using a variable displacement.
  • a flow control valve in particular a pressure control valve, which overall represents a simpler overall solution, which incidentally is more cost-effective than that which results when using a variable displacement.
  • FIG. 1 a is to represent a load-independent constant speed of both consumers 4, a single pressure control valve 5 with a feedforward control, taking into account a load tap LS for both consumers 4 is provided.
  • the load tap LS is in each case initially separated at each changeover valve 18 for each consumer 4.
  • a check valve 22 is switched into the hydraulic circuit before each changeover valve 18.
  • Each check valve 22 In this case, the same set opening pressure and opens in the direction of the pressure regulating valve 5, in particular in the direction of its load-sensing connection LS.
  • the operation of the pressure control valve 5 corresponds to a pilot-operated rotary pressure balance 1 7, wherein in a common housing 12 three different functionally different valves are summarized.
  • the basic functional connection of the valves is also shown in Figure 2 in a schematic circuit diagram in dissolved construction.
  • a main valve 23 having a main piston 6 and a biasing compression spring 24,
  • a relief valve 10 formed as a miniature valve with a valve element 27 or relief valve piston and an energy store 28 holding it in the direction of a closed position.
  • the main piston 6 in a bore 29 of the housing 12 is longitudinally displaceably guided in a main valve control section.
  • the main piston 6 controls a centrally and axially guided into the housing 12 pressure medium inlet 30.
  • a possible fluid-conducting connection to a radially out of the housing 12 Druckstoffan- circuit 31, which optionally consists of several radially arranged passage holes in the housing 12 and is connected to a pressure medium container 1 1, from which the pressure medium pump 3 pressure means for the hydraulic circuit is removed, produced.
  • the main valve 23 is designed in terms of its effective cross-section such that the entire volume flow of pressure medium from the 2 i con- stant pressure pump 3 are directed to the pressure fluid reservoir 1 1 can.
  • a first throttle 13 is arranged in the form of a through hole or bore with a definable diameter in its piston crown. This makes it possible that the pressure on the pump side is reported to the piston rear side 9 of the main piston 6.
  • the main piston 6 is formed substantially as a cylindrical sleeve with a piston crown as a fluid separation, so that on the piston rear side 9 a cup-shaped pressure chamber 8 is formed, which serves for centering and receiving the compression spring 24 and the further pressure medium 2 can accommodate.
  • a bore 32 with a diameter of about 1/5 of the guided in the valve housing 12 main piston 6 is centrally mounted.
  • the bore 32 has a second, second throttle 14 approximately at its axial center.
  • the bore 32 is divided into a first channel section 32 'and a second channel section 32'.
  • the first channel section 32 ' is the one Pressure chamber 8 of the main valve 23 associated, the second channel section 32 ", however, is a second pressure chamber 35, which is Wegbar by the pilot piston 7 assigned.
  • the pilot piston 7 in turn is formed as a flat disc with a centering aid 33 in the form of a truncated cone for a compression spring 26.
  • the pilot piston 7 is acted upon by the force of the compression spring 26, which is supported with radial play in a bore 34 for the pilot piston 7 and the compression spring 26.
  • the piston front side, second pressure chamber 35 is the same pressure chamber as the space 34, in which the compression spring 26 is introduced. So far there is no need for poetry.
  • the space 34 of the pilot valve piston 7 opens a, the housing wall of the housing 12 traversing hole 36 for the load tap LS consumer 4.
  • the flow pressure of the pilot valve 25 results from the pressure defined by the pressure spring 26 plus the pressure at the load tap LS , Is the pump pressure greater than the pressure in LS and that of the pressure set the 26 of the pilot piston 7 and set by the spring 24 of the main piston pressure, so the pilot valve 25 opens and due to the main valve 23 and pressure medium can flow through the main valve 23 to the pressure medium container 1 1.
  • FIGS. 1 f further show the pressure control valve 5 is additionally the relief valve 10 with a valve element 27 which is arranged in an axial region A in a longitudinal bore 40 movable between the pilot valve 25 and the main valve 23, in particular in parallel.
  • the relief valve 10 which is shown in its integration into the housing 12 in an enlarged view in Figures 1 b, d and f, is radially laterally offset from a longitudinal axis 37 of the valve housing 12 and has an approximately same diameter as through The bore 32 formed load bore above and below the second throttle 14.
  • a valve element 27 or a relief valve piston is shown abutting an upper stop, to which it terminates approximately flush with the end of the bore 34 for receiving the pilot piston 7.
  • the relief valve piston is of a smaller energy storage 28, a compression spring, for example, a flow pressure of 0.5 bar, spring-loaded at its opposite end in the sense of an open position.
  • a compression spring for example, a flow pressure of 0.5 bar, spring-loaded at its opposite end in the sense of an open position.
  • an annular recess 41 which is formed as an annular groove 38 in the periphery of the relief valve piston, is provided.
  • 1 b, 1 c and 1 d of the valve assembly 1 communicates the annular recess 41 each with the first channel portion 32 'of the bore 32.
  • the relief valve piston assumes the position shown in Fig.la, 1 e and I f.
  • the annular groove 38 thereby comes into coincidence with an associated opening 39 of the bore 34.
  • Pressure medium can thus be from the pressure chamber 8 on the piston rear side 9 of the main piston 6 via the bore 32, the opening 39 and a connection line 42 communicating with the opening Housing 12 via the annular groove 38 to an outlet 1 5 of the relief valve 10 are performed.
  • the pressure medium 2 then flows without pressure in this respect without the pressure medium pump 3 having to pump against the set pressure at the pilot control valve 25.
  • FIGS. 1e and 1f in turn show in a schematic, not to scale longitudinal section a comparison with the Fig.la, 1 b, 1 c and 1 d modified variant of a valve assembly 1, in turn, combined in a housing 12 of the pressure control valve 5 with an extent offset 39th in that it is ensured that the outflow of the pressure medium 2 from the pressure chamber 8 takes place in the LS line.
  • the opening 39 is assigned to the second channel section 32 ", so that the second throttle 14 has a damping effect on the entire operation of the valve arrangement 1, in particular on the main piston 6.
  • 2 and 3 show the interconnection of the three valves 10, 23 and 25 with a pressure medium tap according to the solutions according to FIGS. 1 a and 1 c. In this way, the valve arrangement 1 according to the invention can be realized even in a dissolved valve design.
  • FIGS. 4 and 5 again show a circuit diagram comparable to that of FIG. 3, wherein the relief valve 10 can be formed as a 2/2-way valve 16, but designed for the entire volume flow of the pressure medium pump 3.
  • the relief valve can be integrated as a rule small constructive valve in an existing pressure control valve. It is advantageous in this respect to arrange the relief valve axially between the pilot valve and the main valve, wherein a valve piston of the relief valve can be inserted from the pilot control valve side into a housing of the pressure regulating valve. It can thereby also make the main bore for the relief valve from the same valve side as a throttle between the pressure chamber and the pilot valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un agencement de soupape pour le réglage de pression d'un agent de pression (2) d'une pompe d'agent de pression (3) vers au moins un premier consommateur (4), comprenant une soupape de réglage de pression (5) précommandée, un piston principal (6) alimenté avec l'agent de pression (2) et un piston pilote (7), une chambre de pression (8) située entre un côté arrière de piston (9) du piston principal (6) et le piston pilote (7) pouvant être déchargée, qui est caractérisé en ce qu'une soupape de décharge (10) est reliée par écoulement de fluide à l'espace de pression (8), laquelle s'ouvre lors d'une pression de l'agent de pression sur le prélèvement de charge (LS), qui reproduit une position de mise hors service du consommateur (4) et refoule de l'agent de pression (2) avec une faible pression dans un réservoir d'agent de pression (11) ou sur la pompe d'agent de pression (3) et qui ferme la soupape de décharge (10) lorsque la pression d'agent de pression sur le prélèvement de charge (LS) reproduit une position de mise en service du consommateur (4).
EP10768695.8A 2009-10-16 2010-10-14 Système de vanne Active EP2488764B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009049548A DE102009049548A1 (de) 2009-10-16 2009-10-16 Ventilanordnung
PCT/EP2010/006289 WO2011045063A1 (fr) 2009-10-16 2010-10-14 Agencement de soupape

Publications (2)

Publication Number Publication Date
EP2488764A1 true EP2488764A1 (fr) 2012-08-22
EP2488764B1 EP2488764B1 (fr) 2016-06-08

Family

ID=43383531

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10768695.8A Active EP2488764B1 (fr) 2009-10-16 2010-10-14 Système de vanne

Country Status (4)

Country Link
US (1) US8973609B2 (fr)
EP (1) EP2488764B1 (fr)
DE (1) DE102009049548A1 (fr)
WO (1) WO2011045063A1 (fr)

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DE202011101545U1 (de) * 2011-06-08 2012-09-13 Robert Bosch Gmbh Hydraulik-Steuerblock und Proportional-Entlastungsventil und Hydraulische Schaltanordnung zur feinfühligen hydraulischen Steuerung
GB2501486A (en) * 2012-04-24 2013-10-30 Jc Bamford Excavators Ltd Work machine having a hydraulic system comprising variable orifice ratios
DE102012010522A1 (de) 2012-05-25 2013-11-28 Hydac Fluidtechnik Gmbh Ventil für Ventilanordnung
CN102889253A (zh) * 2012-09-20 2013-01-23 三一重工股份有限公司 液压系统及工程机械
EP2757024B1 (fr) * 2013-01-16 2015-06-24 Danfoss Power Solutions Aps Agencement de contrôle hydraulique de direction
CH708930A1 (de) * 2013-12-06 2015-06-15 Liebherr Machines Bulle Sa Druckbegrenzungsventil.
CN105840574B (zh) 2015-01-16 2018-04-06 徐工集团工程机械股份有限公司 负载敏感多路阀及工程机械液压系统
US10323762B2 (en) * 2016-04-21 2019-06-18 Parker-Hannifin Corporation Three-way pressure control and flow regulator valve
DE102017200418A1 (de) * 2017-01-12 2018-07-12 Robert Bosch Gmbh Ventilbaugruppe zur Zweikreis-Summierung
US20190032811A1 (en) * 2017-07-25 2019-01-31 Pratt & Whitney Canada Corp. Damped relief valve using double pistons
CN107355550B (zh) * 2017-08-17 2023-06-06 广东美的暖通设备有限公司 节流阀
DE102017008359A1 (de) * 2017-09-06 2019-03-07 Hydac Fluidtechnik Gmbh Ventil
DE102021001960A1 (de) * 2021-04-14 2022-10-20 Hydac Fluidtechnik Gmbh Ventil
CN113738793B (zh) * 2021-09-09 2022-02-22 北京裕峻汽车技术研究院有限公司 一种制动系统及液力缓速器的控制方法
DE102022002192A1 (de) 2022-06-17 2023-12-28 Hydac Fluidtechnik Gmbh Volumenstromversorgung

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DE19744337A1 (de) * 1997-10-07 1999-04-08 Mannesmann Rexroth Ag Vorgesteuertes Druckbegrenzungsventil
DE10039936A1 (de) * 2000-08-16 2002-03-07 Fluidtech Gmbh Ventil
US6966329B2 (en) * 2003-01-27 2005-11-22 Hydraforce, Inc. Proportional pilot-operated flow control valve
US7063100B2 (en) * 2003-03-06 2006-06-20 Hydraforce Inc. Flow regulator with pressure relief combination valve
DE10322585B4 (de) * 2003-05-20 2018-12-06 Hydac Fluidtechnik Gmbh Ventilbaukastensysteme
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DE102010005524A1 (de) * 2010-01-23 2011-07-28 Robert Bosch GmbH, 70469 Stromregelventil mit Dämpfungskammer

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Title
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Also Published As

Publication number Publication date
DE102009049548A1 (de) 2011-04-21
US20120199765A1 (en) 2012-08-09
EP2488764B1 (fr) 2016-06-08
US8973609B2 (en) 2015-03-10
WO2011045063A1 (fr) 2011-04-21

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