EP2171285B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP2171285B1
EP2171285B1 EP08759308A EP08759308A EP2171285B1 EP 2171285 B1 EP2171285 B1 EP 2171285B1 EP 08759308 A EP08759308 A EP 08759308A EP 08759308 A EP08759308 A EP 08759308A EP 2171285 B1 EP2171285 B1 EP 2171285B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
pump
consumer
control arrangement
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.)
Not-in-force
Application number
EP08759308A
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German (de)
English (en)
Other versions
EP2171285A1 (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
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Filing date
Publication date
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Publication of EP2171285A1 publication Critical patent/EP2171285A1/fr
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Publication of EP2171285B1 publication Critical patent/EP2171285B1/fr
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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
    • 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 supplying pressure medium to at least one consumer according to the preamble of patent claim 1.
  • Such a control arrangement is for example from the US 5 138 838 A known.
  • a consumer for example, a differential cylinder is supplied via a valve means with pressure medium, 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 consumer (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 each pressure adjustment valve must be provided for each adjustment.
  • a hydraulic control arrangement for pressure medium supply at least one consumer is known, which has an electro-hydraulically continuously adjustable directional control valve, which has three switching positions and a flow-side pressure chamber of a hydraulic consumer with a pump and a return-side pressure chamber of the consumer is connected to a tank.
  • a lowering brake valve In one of the two lines leading from the directional control valve to the load, a lowering brake valve is arranged, which is the pressure in the other line in Direction of its open position is acted upon. In a middle position of the directional valve whose two consumer connections are relieved to the tank.
  • 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 a lowering brake valve in the inlet and in the return, wherein the lowering brake valve located in the return is acted upon by the respective pressure in the flow in the direction of its open position.
  • the valve device has arranged in the return and in the flow, continuously adjustable directional control valves with only two switching positions, one of which is an open neutral position in which a pressure fluid connection to the tank is open.
  • the directional control valve only a proportional solenoid or an electrically piloted pressure reducing valve is required because in the unactuated state of the associated pressure chamber is connected to the tank and when moving the directional control valve in the direction of the other switching position, the pressure medium connection is opened 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 the DE 196 08 801 C2 or from the data sheet VPSO-SEC-42; 04.52.12-X-99-Z of the company Oil Control, a subsidiary of the applicant, known.
  • a lowering brake valve is in Principle a shut-off valve, which can be unlocked by the pressure in the inlet and allows for pushing load a controlled lowering.
  • 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 acts as a secondary pressure limiting valve in order to limit the pressure in the associated pressure medium flow path to a maximum value set on the lowering brake valve.
  • limit valve acts to limit the pressure in the associated pressure fluid flow path to a maximum value set at the lowering brake valve.
  • a slide is biased by a spring into a closed position and the spring chamber relieved 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.
  • FIG. 1 shows a hydraulic control arrangement 1 for pressure medium supply 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.
  • This is a so-called EFM system (electronic flow management), in which the control of the pressure medium volume flow and the pressure fluid flow direction determining valve elements electrically or electro-hydraulically depending on, stored in a control unit 6, characteristic fields.
  • 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 limiting 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 in the illustration FIG. 1 is shifted by the pump pressure to the right and the pressure medium connection of the pressure chamber of the 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 pressure medium conveyed by the variable displacement pump 22 flows via the pump line 38 and the two directional control valve sections 18, 20, the structure of which is described below FIG. 2 is explained to the consumers 2, 4.
  • the pressure medium flows from the back of the consumers 2, 4 via the associated directional control valve sections 18, 20 and a tank line 52 to the tank 24, wherein in the end portion of the tank line 52, a further filter is provided over a pressure relief valve is bypassed and that opens when the filter clogging and thus the increase in pressure drop 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.
  • FIG. 2 shows the basic structure of the two-way valve sections 18, 20, wherein for example the directional control valve segment 18 is shown 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 via a feed line 56, 58 to the pump line 38.
  • 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.
  • In the pressure medium flow path between the ports P, T and the associated working ports A, B are each a continuously variable 3-way valve 68, 70 arranged with two switching positions 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, such as, for example, from the aforementioned DE 196 08 801 C2 or the publication of the company Oil Control is known.
  • 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 bias 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.
  • connection channel 76, 78 acts, which is tapped, as it were, "crosswise" by means of control lines 92, 94.
  • load acting on the consumer 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 takes place in each case via a bypass channel 96, 98, the connecting channel 76, 78 with 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.
  • a pulling load F acts on the cylinder 2 and that it acts according to the illustration in FIG FIG. 3 to be extended (movement to the right). This extension should be at maximum speed (rapid traverse).
  • the two-way valves 68, 70 in the direction of in FIG. 3 shown position in which a regeneration takes place. That is, the consumer 2 is driven via a differential circuit, in which both the annular space 14 and the bottom-side pressure chamber 10 are connected to the pump 22.
  • the directional control valves via the two proportional magnets 80, 82 from the neutral position ( Fig. 2 ) are shifted to the left, so that both pressure ports P of the directional valve section 18 with the connecting channels 76, 78 are connected.
  • 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 in the increasing bottom pressure chamber 10.
  • the displaced from the annular space 14 pressure fluid flows through the return line 66 and the pressure in the connecting channel 76 in the pressure limiting function fully controlled Senkbremsventil 74, 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 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 annulus 14 minus the load divided by the area ratio of the differential cylinder (for example 2), so that at 250 bar in the annulus 14 and a load of 50 bar a pressure of about 100 bar in the pressure chamber 10 results.
  • the directional control valve section 18 When the cylinder and pulling or pushing load, the directional control valve section 18 is in the in FIG. 5 shown switched position in which the directional control valve 68 controls the pressure medium connection to the tank 24 and via the directional control valve 70 pressure medium from the pump 22 is conveyed into the annular space 14. The pressure in the inlet to the annular space 14 then depends on the load, the opening cross section of the directional control valve 70 and the set pump pressure.
  • 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 is a simplified embodiment of the control arrangement 1 according to FIG. 2 shown.
  • the only difference from the above-described embodiment according to FIG. 2 is that in which there with return line 66 designated, connected to the consumer 2 line no Senkbremsventil and this associated directional control valve with two so-called “switch positions" but a single continuously adjustable directional control valve 104 is provided, which via a Zentrierfederan extract 105 in a basic position ( 0) is biased and by actuation of two pilot valves 108, 83 in the direction of in FIG. 6 shown positions (a) and (b) is adjustable.
  • the two pilot valves 83, 108 are - as in the above-described embodiment - designed as pressure reducing valves, which are each controlled by 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 control valve 68 which is adjustable only in one direction via a single pilot valve 81 and the pressure medium supply correspond to the above-described embodiment, so that respect Explanations are dispensable.
  • 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 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 adjusted to its open position, so that, for example cavitations are prevented 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 a great- ⁇ er 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 supplying pressure medium 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)

Claims (9)

  1. Agencement de commande hydraulique pour l'alimentation en fluide sous pression d'au moins un consommateur (2, 4) avec un système de soupapes (18, 20) réglable en continu électriquement ou électrohydrauliquement, par le biais duquel un espace de pression du consommateur (2, 4), côté aller, peut être connecté à une pompe (22) et un espace de pression du consommateur (2, 4), côté retour, peut être connecté à un réservoir (24), caractérisé en ce que dans l'aller et le retour est à chaque fois disposée une soupape de freinage d'abaissement (72, 74), la soupape de freinage d'abaissement (72, 74) placée dans le retour étant sollicitée par la pression respective dans l'aller dans la direction de sa position d'ouverture, et le système de soupapes (18, 20) présentant des distributeurs (68, 70) réglables en continu, disposés dans le retour et dans l'aller, avec seulement deux positions de commutation, dont l'une est une position neutre ouverte dans laquelle une liaison de fluide sous pression au réservoir (24) est ouverte.
  2. Agencement de commande hydraulique selon la revendication 1, dans lequel la soupape de freinage d'abaissement (72, 74) est réalisée avec une fonction de limitation de la pression.
  3. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, comprenant un canal de dérivation (96) contournant la soupape de freinage d'abaissement (72, 74), dans lequel est disposé un clapet anti-retour (100, 102) s'ouvrant vers le consommateur (2, 4).
  4. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel un corps de soupape de la soupape de freinage d'abaissement (72, 74) est précontraint par le biais d'un ressort (84, 86) dans une position de fermeture, dont l'espace de ressort est détendu par rapport à l'atmosphère.
  5. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, comprenant une unité de commande (6) par le biais de laquelle deux distributeurs (68, 70) peuvent être réglés simultanément dans une position dans laquelle les deux espaces de pression du consommateur (10, 14 ; 12, 16) sont connectés à la pompe (22).
  6. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel la soupape de freinage d'abaissement (72, 74) est disposée dans la direction aller en aval du distributeur respectif (68, 70).
  7. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel le système de soupapes (18, 20) est disposé sur le boîtier du consommateur (2, 4).
  8. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel la pompe (22) est réalisée de manière réglable électriquement ou électrohydrauliquement et la pression de la pompe est réglable par le biais d'un circuit de réglage avec un régulateur de pompe.
  9. Agencement de commande hydraulique selon la revendication 8, dans lequel le signal de commande pour la pompe (22) est une mesure de son angle de pivotement.
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)

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

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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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DE102012203386A1 (de) 2012-03-05 2013-09-05 Robert Bosch Gmbh Steueranordnung
EP2669528A2 (fr) 2012-05-29 2013-12-04 Robert Bosch Gmbh Agencement de soupapes hydrostatique et agencement de commande hydrostatique doté de l'agencement de soupapes
DE102012220863A1 (de) 2012-11-15 2014-05-15 Robert Bosch Gmbh Steueranordnung
DE102013206973A1 (de) 2013-04-18 2014-10-23 Robert Bosch Gmbh Steueranordnung
DE102013224322A1 (de) 2013-11-28 2015-05-28 Robert Bosch Gmbh Hydraulische Steueranordnung

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Cited By (7)

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Publication number Priority date Publication date Assignee Title
DE102012203386A1 (de) 2012-03-05 2013-09-05 Robert Bosch Gmbh Steueranordnung
EP2636908A2 (fr) 2012-03-05 2013-09-11 Robert Bosch Gmbh Agencement de commande
EP2669528A2 (fr) 2012-05-29 2013-12-04 Robert Bosch Gmbh Agencement de soupapes hydrostatique et agencement de commande hydrostatique doté de l'agencement de soupapes
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
DE102013224322A1 (de) 2013-11-28 2015-05-28 Robert Bosch Gmbh Hydraulische Steueranordnung

Also Published As

Publication number Publication date
JP5340278B2 (ja) 2013-11-13
WO2009000471A1 (fr) 2008-12-31
EP2171285A1 (fr) 2010-04-07
DE102007029355A1 (de) 2009-01-02
JP2010531419A (ja) 2010-09-24
US20100180761A1 (en) 2010-07-22
US8671824B2 (en) 2014-03-18
ATE535717T1 (de) 2011-12-15

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