WO2011000515A1 - Ensemble à soupape - Google Patents

Ensemble à soupape Download PDF

Info

Publication number
WO2011000515A1
WO2011000515A1 PCT/EP2010/003851 EP2010003851W WO2011000515A1 WO 2011000515 A1 WO2011000515 A1 WO 2011000515A1 EP 2010003851 W EP2010003851 W EP 2010003851W WO 2011000515 A1 WO2011000515 A1 WO 2011000515A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
switching
directional control
control valve
tank
Prior art date
Application number
PCT/EP2010/003851
Other languages
German (de)
English (en)
Inventor
Dirk-Walter Herold
Holger Engert
Original Assignee
Robert Bosch 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 Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to CN201080033573.4A priority Critical patent/CN102472299B/zh
Priority to EP10739848A priority patent/EP2449268B1/fr
Publication of WO2011000515A1 publication Critical patent/WO2011000515A1/fr

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
    • 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure

Definitions

  • the invention relates to a valve arrangement with a pilot-operated valve according to the preamble of patent claim 1.
  • a valve arrangement with a pilot-operated valve according to the preamble of patent claim 1.
  • DE 44 05 143 C2 such a valve arrangement is disclosed.
  • This has a continuously adjustable main control valve as a main stage and an electro-magnetically actuated pilot valve as a precursor.
  • the main control valve is used to control a pressure medium connection between a pressure source, a drain and a consumer in the form of a hydraulic cylinder.
  • a main control valve of the main control valve is controllable via two control chambers and has a spring return.
  • the control chambers for adjusting the main control piston are controlled via the pilot valve. About this the control rooms are then connected to the drain or the pressure medium source.
  • the disadvantage here is that with increasing nominal size of the pilot valve and the production costs and production costs increase.
  • the present invention seeks to provide a cost-effective, dynamic pilot-operated valve.
  • a pilot-operated valve of a valve arrangement has a
  • the main stage has a directional valve - for example, a poppet valve - with at least one control chamber, which via a directional control valve of the precursor. can be connected to a pressure source or a drain or tank. At least one switching valve is arranged parallel to the directional valve of the preliminary stage.
  • This solution has the advantage that a high pressure medium throughput between the at least one control chamber of the main stage and the tank or the pressure medium source - depending on how the switching valve is arranged - is made possible by the switching valve.
  • a high pressure medium throughput and short positioning times of the main stage can be achieved.
  • a pilot valve of the precursor with a small nominal size has low manufacturing costs, high dynamics and high robustness. Since the switching valve is also extremely inexpensive, a pilot-operated valve according to the invention is overall extremely cost-effective and robust.
  • the directional control valve of the preliminary stage can be a proportional directional control valve or continuous directional control valve.
  • control chamber of the directional control valve of the main stage via the proportional directional control valve of the precursor with the pressure source or the tank and at least one switching valve to the tank and / or via at least one switching valve with the pressure source connected.
  • this has an input and an output port.
  • a pressure medium connection between the input and the output terminal is locked in a spring-biased blocking position.
  • the input and the output port are in pressure medium connection (it would be conceivable to form the switch positions exactly the reverse).
  • a plurality of switching valves may be arranged in the preliminary stage for connecting the control chamber to the tank.
  • a plurality of switching valves may be provided.
  • a switching valve has two inlet and two outlet connections. In a spring-biased basic position, the two inlet connections and the two outlet connections and in a switching position, in each case one inlet and one outlet connection are connected.
  • two flow paths between the control chamber of the directional control valve of the main stage and the tank or the pressure medium source can run, at the same time low space requirement of the switching valve.
  • the directional control valve of the main stage has two control chambers, via which a main control piston is proportionally adjustable via the precursor.
  • a respective control chamber can be easily connected via at least a first switching valve to the pressure source and at least a second switching valve to the tank.
  • FIG. 1 shows a hydraulic circuit diagram with a valve arrangement according to a first embodiment
  • Figure 2 is a hydraulic circuit diagram with the valve assembly according to a second embodiment
  • FIG. 3 shows a hydraulic circuit diagram with the valve arrangement according to a third exemplary embodiment
  • FIG. 4 shows a hydraulic circuit diagram with the valve arrangement according to a fourth exemplary embodiment
  • FIG. 5 is a hydraulic circuit diagram with the valve assembly according to a fifth embodiment.
  • 1 shows a hydraulic circuit diagram of a valve arrangement according to the invention with a pilot-operated valve according to a first embodiment.
  • the valve is a 2/2-way valve 1, which serves to open and close a pressure medium connection between a hydraulic accumulator 2 and a pressure source and a consumer in the form of a hydraulic cylinder 4.
  • the directional control valve 1 is used as a main stage 6, which is pre-controlled by a precursor 8.
  • the hydraulic accumulator 2 is connected via a pressure line 10 to a first working port 12 of the directional control valve 1 of the main stage 6.
  • a working line 16 which is connected to a cylinder chamber 18 of the hydraulic cylinder 4, is connected to a second working connection 14 of the directional control valve 1.
  • the cylinder chamber 18 is separated by a guided in the hydraulic cylinder 4 piston 20 by an annular space 22 which is penetrated by a piston 20 connected to the piston rod 24.
  • the directional control valve 1 has a valve seat 26 associated with stepped piston 28.
  • a remote from the valve seat 26 control surface 30 of the stepped piston 28 defines a control chamber 32 which is connectable via the precursor 8 with the pressure line 10 and thus with the hydraulic accumulator 2 or with a tank 34.
  • a closing spring 36 is arranged, which acts on the stepped piston 28 via the control surface 30 in the direction of the valve seat 26 with a spring force.
  • a displacement measuring piston 38 of a displacement transducer 40 is supported for determining the stroke path of the stepped piston 28.
  • the stepped piston 28 has a radially stepped-back portion 42 which rests on the valve seat 26 in the closed state of the directional control valve 1. Due to the reclassified portion 42, the stepped piston 28 has a repellent from the control surface 30 annular surface 44 and an end face 46. In the closed state of the directional control valve 1, the annular surface 44 in pressure fluid communication with the working port 12 and thus the pressure line 10 and the end face 46 with the working port 14 and thus the working line 16 connected.
  • a control line 48 is connected to the control chamber 32 of the directional control valve 1, which is connected to a working port A of a directional valve 50 of the precursor 8.
  • This is an electromagnetically via a proportional solenoid 52 - conceivable would be a servo or piezo element - actuated
  • the directional control valve 50 further has a pressure port P, which is in fluid communication with the pressure line 10 via a connecting line 54. Via a tank connection T, the directional control valve 50 is connected to a tank line 56 connected to the tank 34.
  • a pilot valve of the directional control valve 50 is biased by a valve spring 57 in a basic position a, in which the pressure port P is connected to the working port A - depending on the application, the basic position a could also be designed differently.
  • About the proportional solenoid 52 of the pilot spool is displaced in the direction of working positions b, in which the working port A is connected to the tank port T.
  • the control chamber 32 of the directional control valve 1 of the main stage 6 is in fluid communication with the hydraulic accumulator 2.
  • the control chamber 32 of the directional control valve 1 of the main stage 6 is in fluid communication with the hydraulic accumulator 2.
  • the control chamber 32 of the directional control valve 1 is moved via the proportional solenoid 52 in the direction of the working positions b, whereby the control chamber 32 of the directional control valve 1 is connected to the tank 34 and the pressure in this control chamber 32 is reduced , If the pressure forces acting in the opening direction on the annular surface 44 and the end surface 46 of the stepped piston 28 exceed the pressure forces acting on the control surface 30 and the spring force of the closing spring 36, then the stepped piston 28 lifts off the valve seat 26.
  • two switching valves 58, 60 are arranged in the preliminary stage 8 parallel to the directional control valve 50, via which a pressure medium connection between the control chamber 32 of the directional control valve 1 and the tank 34th is on and zuu mortbar.
  • the switching valves 58, 60 are electromagnetically adjustable 2/2-way valves and each have a connected to the control line 48 working port A and connected to the tank line 56 tank port T.
  • Switching valve 58 or 60 is biased via a valve spring 62 into a blocking position x, in which the pressure medium connection between the tank connection T and the working connection A is disconnected. Via an electromagnetically actuated actuator 64, the valve spool of the switching valve 58 or 60 can be switched to an open position y, in which the working port A is connected to the tank port T.
  • the operation of the directional control valve 1 will be explained with the switching valves 58, 60 according to the first embodiment.
  • the control chamber 32 is connected via the precursor 8 to the tank 34.
  • the valve spool of the switching valve 58 and 60 is additionally brought into the open position y, whereby a faster discharge of the control chamber 32 to the tank 34 takes place.
  • the second switching valve 58 or 60 is additionally brought into the open position y.
  • the positioning time can thus be shortened by additional operation of one or both switching valves 58, 60. Due to the pressure relief of the control chamber of the stepped piston 28 is moved via the annular surface 44, which is acted upon by the pressure in the hydraulic accumulator 2, in the opening direction. For example, 70% of a required opening stroke of the stepped piston 28 is reached, the switching valves 58 and 60 are switched to the blocking position x, whereby the remaining stroke is controlled via the directional control valve 50 of the precursor 8. With the directional control valve 50 alone, an accurate positioning of the step piston 28 of the directional control valve 1 is made possible.
  • the directional control valve 50 and the switching valves 58 and 60 are de-energized in the normal position a or blocking position x.
  • the control chamber 32 is then connected to the hydraulic accumulator 2 via the directional control valve 50, as a result of which the stool piston 28, via the control surface 30, is connected to the pressure of the hydraulic accumulator 2 and the
  • a short positioning time of the stepped piston 28 of the directional control valve 1 is required, for example, when the hydraulic cylinder 4 is used for injecting injection molding agent into an injection molding machine.
  • rapid pressurization of the piston 20 of the hydraulic cylinder 4 via the cylinder space 18 is necessary and thus a fast pressure medium connection between the working line 16 connected to the cylinder space 18 and the pressure line 10 connected to the hydraulic accumulator 2 is necessary.
  • FIG. 2 shows, in a hydraulic circuit diagram, the valve arrangement according to a second exemplary embodiment.
  • the preliminary stage 8 has two additional switching valves 66, 68. These serve to close the directional valve 1 of the main stage 6 quickly.
  • the switching valves 66 and 68 each have a working connection A connected to the control line 48 and a pressure connection P connected to the connecting line 54 and thus to the pressure line 10 the switching valves 66 and 68 correspond to those of the illustrated in Figure 1 switching valves 58 and 60th
  • the switching valves 66, 68 is a shorter positioning time of the stepped piston 28 in the closing direction, in comparison to the first embodiment of Figure 1, allows.
  • the switching valves delta, 60 and the directional control valve 50 of the precursor 8 are energized and energized the switching valve 66, whereby the control chamber 32 of the directional control valve 1 of the main stage 6 via the switching valve 66 and the directional control valve 50 is in pressure fluid communication with the pressure line 10 and thus with the hydraulic accumulator 2.
  • an increased pressure medium throughput of the hydraulic accumulator 2 is created to the control chamber 32, resulting in a shortened positioning time.
  • To further shorten the positioning time is
  • the switching valve 68 can be actuated, whereby the pressure medium throughput is further increased.
  • FIG. 3 shows a hydraulic circuit diagram of the valve arrangement according to a third exemplary embodiment. This corresponds approximately to the first embodiment of Figure 1, wherein instead of the switching valves 58, 60, a single switching valve 70 is arranged in the preliminary stage parallel to the directional control valve 50.
  • the switching valve 70 is a 4/2-way valve with two working ports A1, A2 or feed ports connected to the control line 48 and two tank ports T1, T2 or drain ports connected to the tank line 56.
  • a valve spool of the switching valve 70 is biased by a valve spring 72 in a basic position h, in which the two working ports A1, A2 and the two tank ports T1, T2 are in fluid communication.
  • valve slide By way of an electromagnetically actuatable actuator 74, the valve slide can be switched to an open position i, in which the working port A1 is in fluid communication with the tank port T2 and the working port A2 is in fluid communication with the tank port T1.
  • an electromagnetically actuatable actuator 74 By way of an electromagnetically actuatable actuator 74, the valve slide can be switched to an open position i, in which the working port A1 is in fluid communication with the tank port T2 and the working port A2 is in fluid communication with the tank port T1.
  • the pressure medium flow rate over the switching valve 70 for example, the sum of the two pressure medium volume flow rates of the switching valves 58 and 60 of Figure 1 correspond, with only a single switching valve 70 is required and, for example, space can be saved.
  • the valve slide of the switching valve 70 is actuated into the open position i in addition to the directional valve 50 connected to the working position b.
  • the control line 48 is connected via the switching valve 70 to the tank port 56 via the working port A1 and the tank port T2 and via the working port A2 and the tank port T1, whereby the control chamber 32 of the directional control valve 1 and the tank 34 are in fluid communication.
  • FIG. 4 shows in a hydraulic circuit diagram the valve arrangement according to a fourth exemplary embodiment.
  • This has, in addition to the third embodiment of Figure 3, a switching valve 76 which corresponds to the switching valve 70.
  • the switching valve 76 serves to reduce the positioning time of the stepped piston 28 of the directional control valve 1 of the main stage 6 in the closing direction.
  • a valve spool of the switching valve 76 is biased by a valve spring 78 in a basic position k, in which the two working ports A1, A2 and the two pressure ports P1, P2 are interconnected.
  • valve slide of the switching valve 76 can be switched to the open position I, in which the working port A1 is in pressure-medium communication with the pressure port P2 and the working port A2 is in pressure-medium communication with the pressure port P1, whereby the pressure line 10 is connected via the connecting line 54, the pressure ports P1, P2 and the working ports A1, A2 is connected to the control line 48 and thus to the control chamber 32 of the directional control valve 1.
  • Figure 5 apparently in a hydraulic circuit diagram, a valve assembly in a fifth embodiment.
  • the main stage 6 in this case has a 4/3-way valve or continuous-way valve 82 with two control chambers 84, 86 for pressurizing and moving a main control piston 82 of the directional control valve.
  • a 4/3-way valve for example, a 2/2-way or 3/2-way valve can be used.
  • the control chambers 84, 86 can each be connected via the precursor 8 to the tank 34 or a pressure medium source 88.
  • the pre-stage 8 has an electromagnetically continuous proportional magnets 90, 92 - is conceivable, for example, a servo or piezoelectric element or a linear motor - adjustable 4/3-way valve 94 and four parallel arranged switching valves 96, 98, 100, 102.
  • the directional control valve 94th is connected via a pressure port P to a pressure line 104 connected to the pressure medium source 88. With a tank connection T, the directional control valve 94 is connected to a tank line 106 connected to the tank 34.
  • a first working port A of the directional control valve 94 is connected via a first working line 108 to the left in Figure 5 control chamber 84 of the directional control valve 82 and a second working port B is connected via a second working line 110 with the right control chamber 86 in fluid communication.
  • a valve spool of the directional control valve 94 of the precursor 8 is centered via two valve springs 112, 114 in a basic position r and by energizing the proportional solenoid 90 in the direction of working positions m, in which the working port A to the tank port T and the working port B to the pressure port P in Pressure medium connection are, displaceable. In the basic position r, both working connections to the tank connection T are in pressure medium connection.
  • the valve spool of the directional valve 94 is displaceable in the direction of working positions n via the proportional magnet 92, in which the working port A is in pressure-fluid communication with the pressure port P and the working port B is in fluid communication with the tank port T.
  • the pressure medium source 88 connected control chamber 84 and 86 in the working positions m and n of the directional control valve 94 is then connected to the tank 34.
  • the directional control valve 82 of the main stage 6 has four connections in FIG. 5, these are not explained in detail. Essential to the directional control valve 82 is that the
  • Main control piston via the control chambers 84, 86 with a shortened positioning time by the switching valves 96 to 102 is displaceable.
  • the switching valves 96 to 102 correspond to those of the first two exemplary embodiments from FIGS. 1 and 2.
  • the switching valve 100 is connected via a working connection A to the working line 110 and to a pressure connection P to the pressure line 104. Also via a working port A, the switching valve 102 is connected to the working line 110 and to a tank port T to the tank line 106.
  • the right-hand control chamber 86 of the directional control valve 82 can thus be connected to the pressure medium source 88 and via the switching valve 102 to the tank 34.
  • the switching valve 98 is connected via a working port A to the working line 108 and via a pressure port P to the pressure medium source 88 and the switching valve 96 via a working port A to the working line 108 and a tank port T to the tank 34.
  • the left control chamber 84 of the directional control valve 82 is thus connected via the switching valve 98 with the pressure medium source 88 and with the switching valve 96 to the tank 34.
  • the main control piston of the directional control valve 82 of the main stage 6 is biased via valve springs 116, 118 in a blocking position u, displaceable via the control chamber 86 in the direction of working positions w and over the control chamber 84 in the direction of working positions v.
  • a displacement sensor 120 measures the displacement of the main control piston.
  • the switching valves 98 and 102 are switched to blocking positions x, whereby the control chambers 84 and 86 are controlled only via the directional control valve 94 of the precursor 8. For an accurate positioning of the main control piston of the directional control valve 82 is possible.
  • the control chamber 86 is correspondingly connected via the directional control valve 94 to the pressure source 88 and the control chamber 84 to the tank 34. To shorten the positioning time then the switching valve 96 and the switching valve 100 are opened.
  • the switching valves of Figures 1 to 5 have an extremely short switching time.
  • the actuators 74 and 80 of the switching valves 70 and 76 of Figures 3 and 4 are designed for example for 12 volts. Experiments have shown that an overvoltage excitation - for example 24 V - is possible, which advantageously further reduces the switching time of the switching valves 70 and 76.
  • the switching valves 58, 60; 66, 68; 96, 98, 100, 102 in Figures 1, 2 and 5 may also be formed as a 3/2-way valve.
  • a working port A in a first switching position with a sequence and in a second switching position with a pressure source can be connected.
  • a pilot operated valve with a main and a preliminary stage.
  • Main stage has a directional control valve, which is designed for example as a seat or slide valve.
  • a directional control valve has at least one control chamber, which is connected via a directional control valve of the preliminary stage with a pressure source or a tank.
  • a switching valve is arranged parallel to the directional control valve of the precursor. This is extremely inexpensive • and robust, has a low switching time and allows an increase in the

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Servomotors (AREA)
  • Fluid-Driven Valves (AREA)

Abstract

L'invention concerne une soupape pilote présentant un étage principal et un étage préliminaire. L'étage principal présente un distributeur qui est configuré par exemple en tant que distributeur à clapet ou distributeur à tiroir. Un tel distributeur présente au moins un espace de commande qui est en communication, via un distributeur de l'étage préliminaire, avec une source de pression ou un réservoir. En vue de réduire le temps de réglage du distributeur de l'étage principal, au moins une soupape de commutation est montée en parallèle au distributeur de l'étage préliminaire. Cette soupape de commutation est d'un coût particuièrement avantageux et robuste, et présente un faible temps de commutation, et permet d'augmenter le débit de fluide sous pression à travers l'étage préliminaire.
PCT/EP2010/003851 2009-06-29 2010-06-29 Ensemble à soupape WO2011000515A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201080033573.4A CN102472299B (zh) 2009-06-29 2010-06-29 阀门装置
EP10739848A EP2449268B1 (fr) 2009-06-29 2010-06-29 Ensemble à soupape

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009030888A DE102009030888A1 (de) 2009-06-29 2009-06-29 Ventilanordnung
DE102009030888.1 2009-06-29

Publications (1)

Publication Number Publication Date
WO2011000515A1 true WO2011000515A1 (fr) 2011-01-06

Family

ID=42767971

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/003851 WO2011000515A1 (fr) 2009-06-29 2010-06-29 Ensemble à soupape

Country Status (4)

Country Link
EP (1) EP2449268B1 (fr)
CN (1) CN102472299B (fr)
DE (1) DE102009030888A1 (fr)
WO (1) WO2011000515A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012016838B4 (de) 2012-08-27 2023-12-28 Robert Bosch Gmbh Hydraulische Steuerschaltung für eine hydraulisch betätigte Gießeinheit
DE102012020066A1 (de) * 2012-10-12 2014-04-17 Robert Bosch Gmbh Ventilanordnung
CN111550465B (zh) * 2020-05-15 2022-05-20 北京林克富华技术开发有限公司 控制阀组
DE102022113397A1 (de) 2022-05-27 2023-11-30 Festo Se & Co. Kg Steuerung eines Volumenstroms eines Fluids mittels einer Ventilanordnung

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4405143A1 (de) * 1994-02-18 1995-08-24 Bosch Gmbh Robert Elektrohydraulisches Proportionalwegeventil
US6318234B1 (en) * 2000-06-30 2001-11-20 Caterpillar Inc. Line vent arrangement for electro-hydraulic circuit
DE102004048689B3 (de) * 2004-10-06 2005-10-20 Siemens Ag Zweistufiges Servoventil

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4753158A (en) * 1985-09-06 1988-06-28 Hitachi, Construction Machinery Co., Ltd. Pilot hydraulic system for operating directional control valve
EP0281635B1 (fr) * 1986-09-09 1991-02-27 Hitachi Construction Machinery Co., Ltd. Soupape
CN101203681A (zh) * 2005-03-31 2008-06-18 独立行政法人科学技术振兴机构 使用流体缸的促动器及其控制方法

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4405143A1 (de) * 1994-02-18 1995-08-24 Bosch Gmbh Robert Elektrohydraulisches Proportionalwegeventil
DE4405143C2 (de) 1994-02-18 2002-03-14 Bosch Gmbh Robert Elektrohydraulisches Proportionalwegeventil
US6318234B1 (en) * 2000-06-30 2001-11-20 Caterpillar Inc. Line vent arrangement for electro-hydraulic circuit
DE102004048689B3 (de) * 2004-10-06 2005-10-20 Siemens Ag Zweistufiges Servoventil

Also Published As

Publication number Publication date
EP2449268B1 (fr) 2013-01-23
EP2449268A1 (fr) 2012-05-09
DE102009030888A1 (de) 2010-12-30
CN102472299A (zh) 2012-05-23
CN102472299B (zh) 2015-07-08

Similar Documents

Publication Publication Date Title
EP2638297B1 (fr) Entraînement hydraulique ou pneumatique pour l'actionnement d'un appareil de robinetterie comportant une soupape de réglage ou de commande
EP1598560B1 (fr) Dispositif de soupape hydraulique
EP2425159B1 (fr) Soupape d'étranglement proportionelle
DE102011120767A1 (de) Elektrohydraulische Steuereinrichtung
EP1710445A2 (fr) Dispositif de contrôle hydraulique
EP2449268B1 (fr) Ensemble à soupape
EP1875084B1 (fr) Soupape a tiroirs et dispositif de commande equipe de ladite soupape
EP3230618B1 (fr) Dispositif formant vanne d'amortissement réglable
EP2669528A2 (fr) Agencement de soupapes hydrostatique et agencement de commande hydrostatique doté de l'agencement de soupapes
EP2642132B1 (fr) Agencement de soupape hydraulique avec un agencement de soupape pilote hydraulique
DE4028887C2 (de) Hydraulische Steuereinrichtung
EP2891805B1 (fr) Système de commande et soupape de commande pour un tel système de commande
EP2767719B1 (fr) Soupape
EP2452078B1 (fr) Dispositif constituant une restriction variable pour un écoulement fluidique
WO2016030260A1 (fr) Circuit régulateur de pression
DE19909745A1 (de) Hydrostatisches Antriebssystem
WO2016091528A1 (fr) Agencement de soupapes hydraulique, bloc de soupapes hydraulique ayant un tel agencement de soupapes, et mécanisme d'entraînement hydraulique ayant un tel bloc de soupapes hydraulique
EP1369596B1 (fr) Agencement de distributeur hydraulique
DE4410156B4 (de) Steuereinrichtung für eine Verstellpumpe
DE10033757A1 (de) Steuereinrichtung für einen hydraulischen Verbraucher
DE102009019068B4 (de) Drucküberwachungsschaltung
DE102012220865A1 (de) Stetig verstellbares Ventil und hydraulische Steueranordnung mit einem derartigen Ventil
DE102016209509A1 (de) Hydraulisches Antriebssystem für Gabelstapler
EP2921925A1 (fr) Soupape de réduction de pression
WO2019134832A1 (fr) Agencement de soupape hydraulique

Legal Events

Date Code Title Description
WWE Wipo information: entry into national phase

Ref document number: 201080033573.4

Country of ref document: CN

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 10739848

Country of ref document: EP

Kind code of ref document: A1

WWE Wipo information: entry into national phase

Ref document number: 2010739848

Country of ref document: EP