EP2171285A1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique

Info

Publication number
EP2171285A1
EP2171285A1 EP08759308A EP08759308A EP2171285A1 EP 2171285 A1 EP2171285 A1 EP 2171285A1 EP 08759308 A EP08759308 A EP 08759308A EP 08759308 A EP08759308 A EP 08759308A EP 2171285 A1 EP2171285 A1 EP 2171285A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
pump
control arrangement
hydraulic control
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
EP08759308A
Other languages
German (de)
English (en)
Other versions
EP2171285B1 (fr
Inventor
Matthieu Desbois-Renaudin
Wolfgang Kauss
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.)
Robert Bosch GmbH
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
Publication of EP2171285A1 publication Critical patent/EP2171285A1/fr
Application granted granted Critical
Publication of EP2171285B1 publication Critical patent/EP2171285B1/fr
Not-in-force 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B11/003—Systems with load-holding 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
    • 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
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • 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
    • F15B2211/20546—Type of pump variable 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
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting 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
    • F15B2211/365—Directional control combined with flow control and pressure 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
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hydraulic control arrangement for pressure medium supply at least one consumer according to the preamble of patent claim 1.
  • Such a control arrangement is known for example from US 5,138,838 A.
  • a consumer for example a differential cylinder
  • a valve device which is provided by a pump.
  • each a continuously adjustable directional control valve is arranged.
  • the directional control valves are biased in their neutral position in a blocking position and can be adjusted via pressure reducing valves in each case in one direction in which the pump with the associated pressure chamber and in another direction, in each of which the associated pressure chamber is connected to the tank.
  • this known control arrangement can be operated by a suitable control of the two-way valves, the consumer with a so-called regeneration circuit.
  • the decreasing annular space is connected via the associated directional control valve to the pressure medium inlet to the enlarging pressure chamber, so that the cylinder is extended in rapid traverse.
  • a disadvantage of the regeneration / differential circuit is that due to the clamping of the load (effective effective area corresponds to the piston rod area at the same pressures in the annulus and in the cylinder chamber) the consumer can not be operated with the maximum power.
  • Such a control arrangement also requires a relatively high device-technical effort, since the directional control valves are designed as 3-position valves and a pressure-reducing valve must be provided for each adjustment.
  • the invention has for its object to provide a hydraulic control arrangement that can be operated with little device complexity in regeneration circuit.
  • the hydraulic control arrangement is designed with a continuously adjustable valve device, via which a supply-side pressure chamber of the at least one consumer with a pump and a return-side pressure chamber of the consumer can be connected to a tank.
  • This valve device has in each case one located in the inlet and / or return Senkbremsventil to which a continuously adjustable directional control valve is associated, however, in contrast to the above-described prior art has two switching positions and is biased in an open neutral position.
  • a proportional solenoid or an electrically pilot-controlled pressure reducing valve is required because in the unactuated state of the associated pressure chamber either with the pump, or - preferably - connected to the tank and when moving the directional control valve in the direction of the other switching position, the pressure medium connection is turned on to the pump.
  • the use of the lowering brake valve prevents the formation of cavitations during a pulling load.
  • the return flow valve located in the return flow is triggered by the pressure in the supply line. If the consumers have no pressure medium requirement, the respective load is supported leak-free via the lowering brake valve.
  • Lowering brake valves are known from the prior art, for example from DE 196 08 801 C2 or from the data sheet VPSO-SEC-42; 04.52.12-X-99-Z of OiI Control, a subsidiary of the Applicant known.
  • a lowering brake valve is in principle a check valve, which can be unlocked by the pressure in the inlet and allows a controlled lowering under pressing load.
  • a respective Senkbremsventil and a continuously adjustable directional control valve are arranged in the flow and in the return.
  • Each lowering brake valve can be bypassed in the forward direction via a bypass line with a check valve.
  • the lowering brake valve is designed with a pressure limiting function, so that this is used as secondary pressure limit valve acts to the pressure in the associated pressure medium flow path to a Senkbremsventi! limit set maximum value.
  • a slide is biased by a spring into a closed position and relieves the spring chamber to the atmosphere.
  • the two 3/2-way valves can be adjusted by means of the control unit in a position in which the flow side and the return side pressure chamber of the consumer are both connected to the pump.
  • the lowering brake valve is arranged in the forward direction downstream of the respective directional control valve.
  • the control device can be made particularly compact when it is arranged in the valve device on the housing of the consumer or integrated in this housing.
  • the pump of the control arrangement is preferably made electrically or electro-hydraulically adjustable, wherein a pressure control is provided.
  • the drive signal for a pump controller is a measure of the swivel angle. This requirement is met for example by so-called EP or EK pump controller with electro-proportional swivel angle control.
  • Figure 1 is a circuit diagram of a control arrangement according to the invention for supplying pressure medium to multiple consumers;
  • FIG. 2 shows a detailed view of a directional valve section of the control arrangement assigned to a consumer in a neutral position
  • FIG. 3 shows the control arrangement according to FIG. 2 with the cylinder extended, regeneration and pulling or pushing load
  • FIG. 5 shows the control arrangement according to FIG. 2 with the cylinder being brought in and the load being pulled or pulled
  • FIG. 6 shows a simplified embodiment of the directional control valve section from FIG. 2.
  • a hydraulic control arrangement 1 for supplying pressure medium to two consumers 2, 4 of a mobile implement, such as an excavator, a backhoe loader, a mini and compact excavator or a telehandler.
  • a mobile implement such as an excavator, a backhoe loader, a mini and compact excavator or a telehandler.
  • EFM system electronic flow management
  • the input of the setpoints is carried out via a joystick 8, which is actuated by the operator to control the equipment (for example, boom, bucket) of the implement in terms of speed and position.
  • the two consumers 2, 4 are each designed as a differential cylinder with a bottom-side pressure chamber 10 and 12 and a piston rod side annular space 14 and 16 respectively.
  • These pressure chambers 10, 14; 12, 16 can each be connected via a directional control valve section 18, 20 with a variable displacement pump 22 or a tank 24 to the cylinder on or extend.
  • the variable displacement pump 22 is pressure-controlled via a pump regulator 26, via which, after reaching the predetermined pressure, the delivery flow of the pump is adjusted so that the pressure in the system remains constant independently of the delivery flow. With a pressure medium volume flow change virtually no pressure change should be connected.
  • variable displacement pump 22 is acted upon by a setting cylinder 30 by a spring-loaded return cylinder 28 in the direction of the maximum pressure medium volume flow (pivot angle maximum) and in the direction of reducing the pressure medium volume flow.
  • the acting in the direction of reducing the pressure medium flow rate pressure chamber of the actuating cylinder 30 is acted upon via a running with three connections pump control valve 32 either with the pump pressure or with the tank pressure.
  • the pump control valve 32 is acted upon in the direction of a connection of the pressure chamber of the actuating cylinder 30 with the tank 24 via a control spring and the pressure downstream of a nozzle 34 which is arranged in a control line 36, via which the pressure in a connected to the pressure port of the variable displacement pump 22 Pump line 38 is tapped.
  • This pressure also acts in the direction of a connection of the pressure chamber of the adjusting cylinder 30 with the pump pressure on the pump control valve 32.
  • the downstream of the nozzle 34 located region of the control line 36 is connected via a pressure relief valve 40 to the tank 24.
  • This pressure relief valve 40 is energized electrically via a signal line connected to the control unit 6. In its illustrated, spring-biased home position, the pressure relief valve 40 shuts off the pilot oil connection to the tank 24.
  • the pump controller 26 is adjusted so that an adjustment of the swivel angle is possible only from a stand-by pressure of 20 bar.
  • the pressure chamber of the actuating cylinder 30 is connected via two further nozzles 42, 44 with a leading to the tank 24 tank control line 46.
  • the pressure relief valve 40 of the downstream of the nozzle 34 located part of the control line 36 is connected via the pressure relief valve 40 to the tank control line 46 so that the pump control valve 32 is shifted in the illustration of Figure 1 by the pump pressure to the right and the pressure medium connection of the pressure chamber of Adjusting cylinder 30 is opened to the control line 36.
  • the control oil can then flow via the pump control valve 32 and the nozzle 44 to the actuating cylinder 30, so that the pivot angle is reduced by the pressure build-up in the pressure chamber of the actuating cylinder 30 until the set via the control unit 6 pump pressure.
  • Further explanations on the operation of the pump controller 26 are unnecessary, since the basic structure of such pressure regulator is described for example in the data sheet RD 92 703 Bosch Rexroth AG.
  • a pressure regulator other controllers, such as electro-proportional swivel angle controller (EP or EK) can be used.
  • EP or EK electro-proportional swivel angle controller
  • the pressure in the pump line 38 is detected by a pressure sensor 48 and reported via a signal line to the control unit 6.
  • the suction connection of the variable displacement pump 22 is connected to the tank 24 via a suction line 50 and a filter.
  • the pumped by the variable displacement pump 22 pressure fluid flows through the pump line 38 and the two-way valve sections 18, 20, whose structure will be explained below with reference to Figure 2, to the consumers 2, 4.
  • the pressure fluid flows on the return side of the consumers 2, 4 on the associated Directional control valve sections 18, 20 and a tank line 52 from the tank 24, wherein in the end portion of the tank line 52, a further filter is provided which is bypassed via a pressure relief valve and which opens when the filter is added and thus the pressure loss across the filter.
  • the temperature of the pressure medium received in the tank 24 is detected by a temperature sensor 54 and reported to the control unit 6 via a signal line.
  • a purge valve 57 is provided between the tank line 52 and the pump line 38. This purge valve 57 also has a pressure limiting function, so that the pressure in the pump line 38 can be limited to a maximum pressure.
  • the control of the flushing valve 57 is also carried out electrically in response to a signal of the control unit 6.
  • Figure 2 shows the basic structure of the two-way valve sections 18, 20, wherein the directional control valve segment 18 is shown as an example and the variable displacement pump 22 and the tank 24 are shown in simplified form.
  • the directional valve section 18 has two pressure ports P, which are each connected to the pump line 38 via a supply line 56, 58.
  • Two tank connections T of the directional valve section 18 are connected to the tank line 52 via discharge lines 60, 62.
  • Each connection pair P, T of the directional control valve section 18 is associated with a working port A and B, which is connected via a flow line 64 and a return line 66 to the pressure chamber 10 and the annular space 14 of the consumer 2.
  • the pressure medium flow path between the Conclusions P, T and the associated working ports A, B are each a continuously variable 3-way valve 68, 70 arranged with two Schaitsteliieux and three terminals and a lowering brake valve 72 and 74 respectively.
  • Each directional control valve 68,70 is biased via a control spring in its neutral position shown, in which the drain line 60, 62 is in fluid communication with a connecting channel 76, 78, which extends in each case to the adjacent lowering brake valve 72, 74.
  • the two-way valves 68, 70 with their open to the tank 24 neutral position an extremely simple structure, wherein the adjustment - in contrast to the prior art described above - only a pilot valve and a proportional solenoid 80, 82 is required, while in the known Solutions with closed center position, two expensive proportional solenoids and two pilot valves must be used.
  • the directional control valves 68, 70 can also be controlled directly via the proportional solenoids.
  • the two Senkbremsventile 72, 74 have a known structure, as it is known for example from the aforementioned DE 196 08 801 C2 or the publication of the company OiI Control.
  • Such lowering brake valves allow the controlled lowering of a load and simultaneously act as a secondary pressure relief valve.
  • the lowering brake valves are biased by an adjustable biasing spring 84, 86 in a locking position.
  • the spring chambers of the two biasing springs 84, 86 are vented to the atmosphere. In the opening direction of the respective pressure acts on the associated working port A, B, which is tapped in each case via a pressure limiting control line 88, 90.
  • the pressure in the respective other connection channel 76, 78 acts, which is tapped, as it were, "crosswise” by means of control lines 92, 94.
  • the loads acting on the load 2 can be supported without leakage via the two lowering brake valves 72, 74.
  • the pressure medium supply from the directional control valve 68, 70 to the respective pressure chamber of the consumer 2 is in each case via a bypass channel 96, 98, the connecting channel 76, 78 with the each
  • the respective supply line 64, 66 connects, wherein in each bypass channel 96, 98 in the direction of the consumer 2 opening check valve 100, 102 is arranged.
  • the two pressure chambers of each consumer 2, 4 are connected to the tank 24.
  • the load F acting on the load 2 is supported leak-free by the lowering brake valve 72, 74 designed as a seat valve.
  • the load F can be designed as a pulling or pushing load.
  • About the pressure limiting function of the two lowering brake valves 72, 74 ensures that a maximum pressure in the lines 64, 66 can not be exceeded.
  • the pressure medium is pumped by the pump 22 via the pressure port P, the directional control valve 68, the connecting line 76, the bypass channel 96, the check valve 100 and the supply line 64 into the increasing bottom-side pressure chamber 10.
  • the pressure medium displaced from the annular space 14 flows via the return line 66 and the counterbalancing valve 74, which is completely opened by the pressure in the connecting channel 76 in the pressure limiting function, the connecting channel 78 and the directional control valve 70 to the inlet line 56 and from there into the pump line 38, so that the pressure from the Consumables running pressure fluid flow is summed to the funded by the pump 22 pressure fluid flow.
  • a pressure should be set which is the difference between the pressure in the annular space 14 minus the load divided by the ratio of the differential cylinder (for example 2), so that at 250 bar in the annular space 14 and a load of 50 bar, a pressure of about 100 bar in the pressure chamber 10 results.
  • the function is corresponding, wherein the pressure in the supply-side feed line 64 is limited by the pressure-limiting function of the lowering brake valve 72.
  • the pressure medium is conveyed via the bypass channel 98 and the opening check valve 102 and the return line 66 into the annular space 14 and flows from the decreasing pressure chamber 10 via the feed line 64 and the pressure in the inlet (connecting channel 78) open lowering brake valve 72 and the in the direction of its neutral position adjusted directional valve 68 and the drain line 62 to the tank 24 from.
  • the pressure level in the process is limited by the lowering brake valve 72.
  • the pressure level in the inlet is between the maximum pump pressure and 0 bar (pushing load, minimum retraction speed).
  • FIG. 6 shows a simplified exemplary embodiment of the control arrangement 1 according to FIG.
  • the only difference from the above-described embodiment according to Figure 2 is that in the designated there with return line 66, connected to the consumer 2 line no lowering brake valve and associated therewith directional control valve with two so-called “switching positions” but a single continuously adjustable directional control valve 104 is provided , which is biased by a centering spring assembly 105 in a basic position (0) and which is adjustable by operating two pilot valves 108, 83 in the direction of the positions (a) and (b) shown in Figure 6.
  • the two pilot valves 83, 108 are - as in the above-described embodiment - designed as a pressure reducing valves, which are each controlled via a proportional solenoid 82, 106.
  • the structure of the formed in the flow line 64 valves, with the lowering brake valve 72, the check valve 100 and the biased in an open position directional valve 68, the only in a R direction over a single pilot valve 81 is adjustable and the pressure medium supply correspond to the above-described embodiment, so that explanations are unnecessary in this regard.
  • the corresponding hydraulic components are provided with the same reference numerals as in the embodiment described above and referred to the relevant description.
  • the pressure medium connection between the drain line 60, the supply line 56 and the return line 66 is shut off.
  • the proportional magnet 106 can be adjusted via the pressure reducing valve 108, a control pressure, so that the valve spool of the directional control valve 104 is adjusted to the right in the direction of (a) marked positions in which the connection between the return line 66 and the drain line 60 is turned on.
  • the pressure medium connection to the supply line 56 remains blocked.
  • the valve slide of the directional control valve 104 is adjusted in the direction (b), so that the pressure medium connection between the supply line 56 and the return line 66 acting as a supply line is correspondingly opened, and the pressure medium connection between the return line 66 and the discharge line 60 is controlled.
  • the directional control valve 104 can also be integrated into the supply line 64, so that then the lowering brake valve 74 and the directional control valve 70 from FIG. 2 remain arranged in the return line 66.
  • the directional control valve 104 For retracting the hydraulic cylinder (consumer 2), the directional control valve 104 is adjusted in the direction of its position (b), so that pressure medium of variable displacement pump 22 via the pump line 38, the supply line 56, the directional control valve 104 and then acting as a supply line return line 66 for Annular space 14 of the consumer is promoted. About the directional control valve 104 is then set according to the pressure medium flow rate and the effective pressure in the annular space 14. Due to the pressure in the return line 66, the lowering brake valve 72 is stiffened in its open position, so that cavitations are prevented, for example, at a pressing load, since then the consumer 2 remains clamped. In the case of a pulling load, the lowering brake valve 72 is completely or almost completely opened by the preselected pressure via the control line 92, so that the pressure medium can flow to the tank 24 via the lowering brake valve 72 and the corresponding directional control valve 68.
  • the control arrangement can also be operated again in the regeneration mode, in which case the directional control valve 68 is switched over the pilot valve 81 and the directional valve 104 is adjusted via the pilot valve 83 in the direction of its position (b), so that Pressure fluid from the annular space 14 via the directional control valve 104 in the supply line 58 and from there via the directional control valve 68 and the check valve 100, the bypass channel 96 and the supply line 64 flows to the pressure chamber 10, so that the consumer 2 is extended at high speed.
  • the directional control valve 104 is adjusted in the direction of its positions (a), so that the pressure medium flows from the annular space 14 to the tank 24.
  • variable displacement pump 22 may be designed with a swivel angle sensor.
  • a hydraulic control arrangement for pressure medium supply at least one consumer wherein in the flow and / or return of the consumer, a continuously adjustable directional control valve with two switching positions and a lowering brake valve are arranged, the latter of the pressure in the inlet can be brought into an open position.
  • the directional control valve is designed with an open neutral position and can be moved electrically or electro-hydraulically from this neutral position in the direction of its second switching position.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Abstract

L'invention concerne un dispositif de commande hydraulique destiné à l'alimentation en fluide de pression d'au moins un récepteur, la conduite montante et/ou la conduite de reflux du récepteur contenant un distributeur pouvant être réglé en continu, présentant deux positions de commutation, et une soupape de frein de descente, cette dernière pouvant être amenée dans une position d'ouverture sous l'effet de la pression dans la conduite d'amenée. Le distributeur dispose d'une position neutre ouverte et peut être déplacé, de façon électrique ou électrohydraulique, vers sa deuxième position de commutation, à partir de la position neutre.
EP08759308A 2007-06-26 2008-06-20 Dispositif de commande hydraulique Not-in-force EP2171285B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007029355A DE102007029355A1 (de) 2007-06-26 2007-06-26 Hydraulische Steueranordnung
PCT/EP2008/004989 WO2009000471A1 (fr) 2007-06-26 2008-06-20 Dispositif de commande hydraulique

Publications (2)

Publication Number Publication Date
EP2171285A1 true EP2171285A1 (fr) 2010-04-07
EP2171285B1 EP2171285B1 (fr) 2011-11-30

Family

ID=39768596

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08759308A Not-in-force EP2171285B1 (fr) 2007-06-26 2008-06-20 Dispositif de commande hydraulique

Country Status (6)

Country Link
US (1) US8671824B2 (fr)
EP (1) EP2171285B1 (fr)
JP (1) JP5340278B2 (fr)
AT (1) ATE535717T1 (fr)
DE (1) DE102007029355A1 (fr)
WO (1) WO2009000471A1 (fr)

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DE102013224322A1 (de) 2013-11-28 2015-05-28 Robert Bosch Gmbh Hydraulische Steueranordnung

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DE102008064064A1 (de) 2008-12-19 2010-06-24 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102008064139A1 (de) 2008-12-19 2010-07-01 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102008064138A1 (de) 2008-12-19 2010-07-01 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102008064136A1 (de) 2008-12-19 2010-07-01 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102012203386A1 (de) 2012-03-05 2013-09-05 Robert Bosch Gmbh Steueranordnung
DE102012208944A1 (de) 2012-05-29 2013-12-05 Robert Bosch Gmbh Hydrostatische Ventilanordnung und hydrostatische Steueranordnung mit der Ventilanordnung
DE102012220863A1 (de) 2012-11-15 2014-05-15 Robert Bosch Gmbh Steueranordnung
DE102013206973A1 (de) 2013-04-18 2014-10-23 Robert Bosch Gmbh Steueranordnung
US9611871B2 (en) * 2013-09-13 2017-04-04 Norbert J. Kot Pneumatic valve assembly and method
DE102014102336A1 (de) * 2014-02-24 2015-08-27 Linde Hydraulics Gmbh & Co. Kg Steuerventileinrichtung mit einer Schwimmstellung
CN104154059B (zh) * 2014-06-19 2017-01-25 长沙中联消防机械有限公司 伸缩装置的液压系统和伸缩装置
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JP2010531419A (ja) 2010-09-24
US20100180761A1 (en) 2010-07-22
ATE535717T1 (de) 2011-12-15
JP5340278B2 (ja) 2013-11-13
WO2009000471A1 (fr) 2008-12-31
EP2171285B1 (fr) 2011-11-30
US8671824B2 (en) 2014-03-18

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