EP1108895A1 - Valve hydraulique pour la commande d'un consommateur indépendant de la charge - Google Patents

Valve hydraulique pour la commande d'un consommateur indépendant de la charge Download PDF

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Publication number
EP1108895A1
EP1108895A1 EP00124779A EP00124779A EP1108895A1 EP 1108895 A1 EP1108895 A1 EP 1108895A1 EP 00124779 A EP00124779 A EP 00124779A EP 00124779 A EP00124779 A EP 00124779A EP 1108895 A1 EP1108895 A1 EP 1108895A1
Authority
EP
European Patent Office
Prior art keywords
control
consumer
chamber
slide
drain
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
EP00124779A
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German (de)
English (en)
Other versions
EP1108895B1 (fr
Inventor
Peter BÜTTNER
Tatu Miikkulainen
Jukka Pekkanen
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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 Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Publication of EP1108895A1 publication Critical patent/EP1108895A1/fr
Application granted granted Critical
Publication of EP1108895B1 publication Critical patent/EP1108895B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure 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
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B2013/0413—Valve members; Fluid interconnections therefor with four or more positions

Definitions

  • the invention is based on a hydraulic directional valve that is independent of the load Control of a hydraulic consumer, especially a hydraulic one Consumer of a mobile machine, in terms of direction and speed and serves the features from the preamble of the claim 1 has.
  • a hydraulic travel drive known from DE-OS 1 901 762
  • the directional control valve is one with four connections, namely with one the inlet connection connected to the hydraulic pump, with one connected to the tank Drain connection and with two consumer connections, of which lines lead to the two sides of the wheel motors, and with three positions.
  • the two consumer connections are in the middle position of the directional control valve and fluidly connected to the tank, the wheel motors are, so to speak switched off and can e.g. crank when towing the working machine.
  • the wheel motors which is why the corresponding position of a directional valve in the following is also referred to as a swimming function position.
  • the two side Positions of the directional control valve is the one connection of the wheel motors with the Hydraulic pump and the other connection connected to the tank. Depending on The wheel motors rotate which side position the directional valve assumes in a first direction or in the opposite, second direction.
  • a hydraulic travel drive is also known from DE-GM 92 046 646, the hydraulic wheel motors operated in open hydraulic circuits become.
  • a proportional directional control valve is used to control two wheel motors on a first axis used, which in turn has four connections, namely an inlet connection, has a drain connection and two consumer connections, in whose middle position now blocked all four connections against each other are. This middle position is therefore called the locking function position.
  • In her can neither flow pressure medium to the two wheel motors mentioned Flow pressure fluid away from the two wheel motors.
  • In the middle position of the directional valve can the mobile work machine through the wheel motors on the Be held if the machine is on level ground or only has to be stopped briefly.
  • Hydraulic directional control valves are known which assume a total of four positions can. It is expressly pointed out here that with Position not a very specific position of the control spool, but stroke ranges of the control spool are meant, which are characterized by the hydraulic connections the connections of the valve from each other. For example, out DE 35 08 340 A1 a directional control valve with four switching positions known within a throttle control is used. In a spring-centered neutral position of the control spool, the two consumer connections are against each other as well as blocked against the inlet connection and the outlet connection. The neutral position has a locking function. From this blocking function position position Control spools are moved in one direction to the first consumer connection with the tank connection and the second consumer connection with to connect the inlet connection.
  • control spool moves in the other direction, this first comes into a position in which the first consumer connection with the inlet connection and the second consumer connection is connected to the drain connection. Beyond this position, the Control spool in a fourth position, in which the two consumer connections are connected to each other and to the drain connection.
  • This fourth switching position is therefore a floating function position. It lies from seen from the spring-centered locking function position, beyond the one directional function position.
  • the directional valve is used to e.g. the shovel of a wheel loader or the Floating fork of a forklift. Because before swimming the equipment has to be dumped on the floor here anyway if it is not already on the floor. However, in other applications uncontrolled movements by crossing a directional function position of the controlled hydraulic consumer take place, which can be dangerous can.
  • the well-known hydraulic directional valve for load-independent control of a hydraulic consumer is designed to operate in a special way load-independent control, namely a control with a load-independent Flow distribution of the amount of pressure medium to be used. Flows here the pressure medium first by moving the spool in her Flow cross section changeable orifice, then via one of the orifice downstream pressure compensator and only then via the direction control.
  • the pressure compensator is determined in the opening direction by the pressure after the metering orifice and in the closing direction from the highest load pressure and from a weak one Pressurized spring applied.
  • the invention has for its object to provide a hydraulic directional valve load-independent control of a hydraulic consumer, which features from the preamble of claim 1, to further develop that certain hydraulic consumers in different operating modes can be controlled without dangerous movements occurring.
  • This task is performed on a hydraulic directional valve with the features the preamble of claim 1 according to the invention solved in that according to the characterizing part of claim 1, the swimming function position of the control spool between the locking function position and one Directional function position.
  • a hydraulic directional valve according to the invention is particularly suitable for use within a hydraulic travel drive, for controlling a bogie axis and for controlling hydraulic ones Rotary drives suitable for cranes.
  • a bogie axis is an axis that carries two wheels arranged one behind the other in the longitudinal direction of the vehicle and is pivotable about itself.
  • Bogie axes are used especially in forestry machines. In the forest the wheels swing freely, i.e. the bogie axis can swim when driven becomes. When you start working with the forest machine crane, on the other hand, all pivot points should be locked so that the machine has a fixed Stand. In difficult terrain, e.g. however, when driving over a pit a bow wheel must be raised and held up. As a result, it is convenient if with a directional control valve that is used to control a bogie axis is, according to claim 4 predetermined by a spring arrangement Rest position of the control spool is the locking function position. The device is then firmly supported and you can work with the crane.
  • the control spool is in from the rest position moved a floating function position in which the consumer connections with connected to the tank and the bogie axis can swing freely. Do you want one Raise the wheel so that the control spool is brought into a directional function position.
  • the control for the bogie axis is also intrinsically safe. In the event of a failure due to the spring centering, the control slide reaches the locking function position, in which the bogie axis is blocked for movement and the stability of the Vehicle is guaranteed. Only the driving comfort deteriorates.
  • the swimming function position follows as the rest position after each actuation direction of the control slide towards a locking function position.
  • the swimming function position is between a blocking function position and a directional function position if also not immediately next to the latter.
  • a larger part of the Slider strokes can be used to control the speed.
  • this can be of particular advantage since you usually drive forward drives faster than reverse and then in for speed control Forward stroke a large stroke is available.
  • the control slide is slidable in a sliding hole, around which usually spaced apart control chambers run around, the fluidic Connections with each other can be controlled via the control slide.
  • control chambers that are connected to the consumer connections are connected and are called consumer chambers in the following.
  • drainage chambers which are the consumer chambers are adjacent and connected to the drain port of the directional valve are. So to fluid a consumer connection with the drain connection To connect, the spool must have a flow cross-section between one Open the consumer chamber and the neighboring drain chamber.
  • control spool a radially open and axially extending in its longitudinal direction has connection groove limited on both sides, the length of which is greater than the clear distance between the consumer chamber and the drain chamber.
  • This connecting groove can be easily inserted into a slide collar of the control slide.
  • the connection between the consumer chamber and drain chamber more or less throttled.
  • the connection is interrupted as soon as one or the other end of the connecting groove from the web between the consumer chamber and the drain chamber of the valve housing is covered.
  • a locking function position between one Floating function position and a directional function position is obtained one advantageously by means of a configuration according to claim 9.
  • the swimming function position between the blocking function position and a directional function position.
  • an outlet cross-section between the one consumer chamber and a drainage chamber can be opened from zero, if at the transition from a swimming function position to the neighboring directional function position the fluidic connection existing in the floating function position between the consumer chamber and the drain chamber initially is interrupted once. How this can be achieved cheaply is in claim 11 specified.
  • the directional control valve is preferably electrical or electro-hydraulic actuatable.
  • the electrical pilot control given control signals electrically processed and accordingly modified to be given to the electrical actuators.
  • the spool in an outside of the rest position Locking function position or swimming function position with a very specific one Hold as long as the electrical pilot signal within a certain Range.
  • the two proportionally adjustable directional valves shown are intended to around together with a pressure compensator upstream of a metering orifice to control a hydraulic consumer independent of load pressure.
  • Directional control valve and pressure compensator form one Directional valve disc combined with a valve housing 10.
  • a slide bore 11 through which a control slide 12 is axially movable is.
  • the length of the control slide 12 coincides with the length of the slide bore 11 from one end face 13 to the other end face 14 of the valve housing 10 match.
  • the slide bore 11 is axially spaced from five Control chambers surround the inflow of pressure medium to and the outflow pressure medium from a hydraulic consumer, e.g.
  • the central control chamber 15 of the five control chambers is the inlet chamber. This flows pressure medium through a channel 16 from the pressure compensator 17. Is located on both sides of the inlet chamber a consumer chamber 18 or 19, each with one at the end of one Consumer channel lying consumer connection 20 or 21 of the valve disc connected is. An outlet chamber follows each consumer chamber 18 or 19 22 and 23, respectively, which become one of two passing through the valve housing 10 Tank channels 24 is open.
  • the control slide 12 takes due to two centering springs 34 which in the End faces 13 and 14 of the valve housing 10 attached and the slide hole 11 outwardly closing covers 35 are accommodated, a middle position a, from which it can be constantly adjusted in opposite directions can. At maximum stroke, it strikes an adjustable stroke limiter 36 at.
  • the control slide 12 has a slide neck 37 which in the Center position to the inlet chamber 15 is centered.
  • the two tax authorities 38 and 39 on both sides of the slider neck 37 are so long that in the middle position of the Control spool one end face at a distance from the inlet chamber 15 and its other end face is in the drain chamber 22 or 23.
  • Both piston collars have control grooves 40 and 41 on one end face and on the other other end face are axially open.
  • control grooves 40 and 41 In the middle position of the control spool 12 are the control grooves 40 and 41 from those located between the control chambers Housing bars covered so that no open fluidic via the control grooves There is a connection between the individual control chambers. After a short Another neck follows the control collar 39, another slide collar 42, the seals the spring chamber in a cover 35 against the drain chamber 23.
  • the distance between the drain chamber 22 and the end face 13 of the valve housing 10 is greater than the distance between the drain chamber 23 and the End face 14.
  • the entrance to each of the two chambers 43 and 45 is one Pressure relief valve 46 connected.
  • Each of these two pressure relief valves is installed in a bore of the valve housing 10. In the in the FIGS. 3 and 5 of the central position of the control slide 12 shown, a slide collar is sufficient 47 from the end face 13 of the valve housing 10 into the area of the housing web between the chamber 45 and the drain chamber 22.
  • the pressure compensator 17 has a control piston 65, which is in a slide bore 11 running in parallel and from the end face 14 into the valve housing 10 introduced blind hole 66 is inserted.
  • a control piston 65 which is in a slide bore 11 running in parallel and from the end face 14 into the valve housing 10 introduced blind hole 66 is inserted.
  • In the blind bore 66 are axial spaced apart from each other an inlet chamber 67 which is perpendicular to the one Cut plane according to Figures 3 and 5 extending inlet bore 68 cut is formed, and a drain chamber 69, which via the channel 16 with the inlet chamber 15 of the slide bore 11 is connected.
  • the control piston 65 has an opening cross section with a control edge 70 which is provided with fine control grooves to influence between the two chambers 67 and 69.
  • a compression spring 71 whose pressure equivalent is in the range between 10 and 20 bar.
  • control grooves are in the central position of the control slide 12 40 and 41 covered on the tax authorities 38 and 39, so that none of them there is a fluidic connection between the control chambers.
  • the rest are larger in cross section than the control grooves 40, a flow cross section between the other consumer chamber and the corresponding drain chamber 22 or 23 open.
  • a metering orifice is implemented, via which one Pressure difference drops, which is kept constant by the pressure compensator 17 and which corresponds to the force of the compression spring 71.
  • the hydraulic consumer the amount of pressure medium flowing in depends only on the stroke of the spool 12, but not from the load or pump pressure.
  • a spring chamber is used to move the control slide 12 out of its central position acted upon by a control pressure in one of the two covers 35.
  • two electromagnetically actuated pilot valves 72 and 73 which in the a cover 35 are used and the proportionally adjustable pressure reducing valves are trained.
  • a maximum control pressure of e.g. 30 bar the two pilot valves 72 and 73 control oil is limited via a channel 74 in Valve housing 10 supplied, while control oil flow through a channel 75 can.
  • control slide 12 3 and 4 also via the connecting grooves 80 and 81 no fluidic connection between a consumer chamber 18 or 19 and a drain chamber 22 or 23. All control chambers are shut off from each other.
  • the central position of the control slide 12 is therefore the blocking function position.
  • the connecting grooves 80 and 81 of the embodiment according to Figures 3 and 4 and the connecting grooves 82 of the embodiment of Figure 5 are in the longitudinal direction of the Control spool 12 longer than the clear distance between a consumer chamber and the neighboring drain chamber.
  • control grooves 80 and 81 are arranged on the control collars 38 and 39 so that a control groove 80 on one piston collar and a control groove 80 on the other Piston collar and a control groove 81 on a piston collar with a control groove 81 are in alignment with each other on the other piston collar.
  • a connecting groove 82 is aligned on the slide collar 38 with a connecting groove 82 on the slide collar 39
  • the location of the connecting grooves 82 on the control collars 38 and 39 is such that in the centered central position of the control slide 12, the connecting groove 82 of the tax authority 38 to both the consumer chamber 18 and Drain chamber 22 and the connecting groove 82 on the control collar 39 both to the consumer chamber 19 and the drain chamber 23 is open.
  • the two Consumer chambers 18 and 19 fluidly with the drain connection of the directional valve connected.
  • the central position of the control spool corresponds to that Floating function position. If the control slide is now considered, as shown in FIG. 5, moved to the left, the connecting groove 82 in the Control collar 38 to the consumer chamber 18 and the connecting groove 82 in Control collar 39 closed to the drain chamber 23. The spool 12 has then reaches the blocking function position on one side of the middle position. After a further stroke, the control grooves 41 of the control collar open 39 a connection between the consumer chamber 19 and the drain chamber 23 and the control grooves 40 in the control collar 38 a connection between the inlet chamber 15 and the consumer chamber 18. The control slide is located then in one directional function position, whereby by further displacement to the left the quantity of pressure medium supplied to a hydraulic consumer increases.
  • FIG. 1 The circuit diagram of Figure 1 is in accordance with the embodiment of Figure 5 designed. It becomes clear once again that in the middle position of the control spool 12 the consumer chambers 18 and 19 and the chambers 43, 44 and 45 are connected to the drain chambers 22 and 23, and that the inlet chamber 15 is locked.
  • the connection between a consumer chamber and the neighboring one Drain chamber is a throttled connection, which is shown in Figure 1 the chokes formed by the connecting grooves 82 is indicated.
  • the swimming function position is followed in the middle by one Lock function position and then a directional function position.
  • the schematic 2 shows clearly that in the embodiment according to FIGS.
  • a directional control valve with the circuit diagram according to FIG. 1 is preferred for controlling a hydraulic travel drive
  • a directional control valve with the circuit diagram according to FIG. 2 preferably for controlling a bogie axis or a rotary drive for a crane or used a rotator at the free end of a crane.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Sliding Valves (AREA)
EP00124779A 1999-12-02 2000-11-14 Valve hydraulique pour la commande d'un consommateur indépendant de la charge Expired - Lifetime EP1108895B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19957952 1999-12-02
DE19957952A DE19957952A1 (de) 1999-12-02 1999-12-02 Hydraulisches Wegeventil zur lastunabhängigen Steuerung eines hydraulischen Verbrauchers von insbesondere einer mobilen Arbeitsmaschine

Publications (2)

Publication Number Publication Date
EP1108895A1 true EP1108895A1 (fr) 2001-06-20
EP1108895B1 EP1108895B1 (fr) 2003-07-23

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EP00124779A Expired - Lifetime EP1108895B1 (fr) 1999-12-02 2000-11-14 Valve hydraulique pour la commande d'un consommateur indépendant de la charge

Country Status (4)

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EP (1) EP1108895B1 (fr)
AT (1) ATE245771T1 (fr)
DE (2) DE19957952A1 (fr)
DK (1) DK1108895T3 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002066842A1 (fr) * 2001-02-17 2002-08-29 Bosch Rexroth Ag Distributeur pour la commande independante de la charge d'un consommateur hydraulique en ce qui concerne la direction et la vitesse
CN102398866A (zh) * 2011-10-26 2012-04-04 徐州重型机械有限公司 一种起重机变幅控制阀及起重机变幅液压系统
DE102010053805A1 (de) * 2010-12-08 2012-06-14 Robert Bosch Gmbh Wegeventil zur insebondere lastunabhängigen Steuerung eines hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit
CN105201943A (zh) * 2015-01-23 2015-12-30 徐州重型机械有限公司 换向阀、油缸下落控制阀以及起重机变幅系统
US9255587B2 (en) 2011-12-03 2016-02-09 Robert Bosch Gmbh Hydraulic two-way valve for the lifting mechanism of an agricultural vehicle
EP2985470A1 (fr) * 2014-08-12 2016-02-17 Hydac Fluidtechnik GmbH Dispositif de commande pour un cylindre de travail actionné par un fluide ayant au moins une fonction de levage et d'abaissement
EP3020983A1 (fr) * 2014-11-14 2016-05-18 Danfoss Power Solutions Aps Groupe de valves et module d'entrée d'un groupe de valves
EP3553324A1 (fr) * 2018-04-13 2019-10-16 Danfoss Power Solutions (Zhejiang) Co. Ltd Soupape et système hydraulique équipé de celle-ci
WO2019219491A1 (fr) * 2018-05-18 2019-11-21 Hydac Systems & Services Gmbh Soupape
WO2022165116A1 (fr) * 2021-02-01 2022-08-04 Caterpillar Inc. Soupape de levage à centre fermé à freinage

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10135298A1 (de) * 2001-07-24 2003-02-13 Bosch Rexroth Ag Ventilanordnung
DE102008018546A1 (de) 2008-04-12 2009-10-15 Robert Bosch Gmbh Ventilanordnung, insbesondere für ein mobiles Arbeitsgerät
DE102013014671A1 (de) * 2013-09-03 2015-03-05 Hydac Technology Gmbh Ventilbaukomponenten
DE102014209277A1 (de) * 2014-05-16 2015-11-19 Robert Bosch Gmbh Anti-Pendel-Ventil für einen hydraulischen Drehantrieb

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DE3508340A1 (de) * 1985-03-08 1986-09-11 Mannesmann Rexroth GmbH, 8770 Lohr Mehrwegeventil
US5992454A (en) * 1998-07-21 1999-11-30 Eaton Corporation Lower and float capability in four position control valve

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Publication number Priority date Publication date Assignee Title
DE2231217A1 (de) * 1971-06-29 1973-01-11 Appingedammer Bronsmotor Steuervorrichtung fuer hydraulisch betriebene einrichtungen
US4355660A (en) * 1980-04-15 1982-10-26 General Signal Corporation Pneumatically controlled, four position hydraulic valve
DE3508340A1 (de) * 1985-03-08 1986-09-11 Mannesmann Rexroth GmbH, 8770 Lohr Mehrwegeventil
US5992454A (en) * 1998-07-21 1999-11-30 Eaton Corporation Lower and float capability in four position control valve

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6994116B2 (en) 2001-02-17 2006-02-07 Bosch Rexroth Ag Distributing valve for the load-independent control of a hydraulic consumer in terms of direction and speed
WO2002066842A1 (fr) * 2001-02-17 2002-08-29 Bosch Rexroth Ag Distributeur pour la commande independante de la charge d'un consommateur hydraulique en ce qui concerne la direction et la vitesse
DE102010053805A1 (de) * 2010-12-08 2012-06-14 Robert Bosch Gmbh Wegeventil zur insebondere lastunabhängigen Steuerung eines hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit
CN102398866A (zh) * 2011-10-26 2012-04-04 徐州重型机械有限公司 一种起重机变幅控制阀及起重机变幅液压系统
US9255587B2 (en) 2011-12-03 2016-02-09 Robert Bosch Gmbh Hydraulic two-way valve for the lifting mechanism of an agricultural vehicle
EP2985470A1 (fr) * 2014-08-12 2016-02-17 Hydac Fluidtechnik GmbH Dispositif de commande pour un cylindre de travail actionné par un fluide ayant au moins une fonction de levage et d'abaissement
EP3020983A1 (fr) * 2014-11-14 2016-05-18 Danfoss Power Solutions Aps Groupe de valves et module d'entrée d'un groupe de valves
CN105605021A (zh) * 2014-11-14 2016-05-25 丹佛斯动力系统有限公司 阀组以及阀组的入口模块
US9810329B2 (en) 2014-11-14 2017-11-07 Danfoss Power Solutions Aps Valve group and inlet module of a valve group
CN105201943A (zh) * 2015-01-23 2015-12-30 徐州重型机械有限公司 换向阀、油缸下落控制阀以及起重机变幅系统
CN105201943B (zh) * 2015-01-23 2017-05-03 徐州重型机械有限公司 换向阀、油缸下落控制阀以及起重机变幅系统
EP3553324A1 (fr) * 2018-04-13 2019-10-16 Danfoss Power Solutions (Zhejiang) Co. Ltd Soupape et système hydraulique équipé de celle-ci
WO2019219491A1 (fr) * 2018-05-18 2019-11-21 Hydac Systems & Services Gmbh Soupape
US11378192B2 (en) 2018-05-18 2022-07-05 Hydac Systems & Services Gmbh Valve
WO2022165116A1 (fr) * 2021-02-01 2022-08-04 Caterpillar Inc. Soupape de levage à centre fermé à freinage

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Publication number Publication date
DK1108895T3 (da) 2003-11-03
EP1108895B1 (fr) 2003-07-23
DE19957952A1 (de) 2001-06-07
DE50002982D1 (de) 2003-08-28
ATE245771T1 (de) 2003-08-15

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