EP1629156B1 - Ensemble commande hydraulique - Google Patents

Ensemble commande hydraulique Download PDF

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Publication number
EP1629156B1
EP1629156B1 EP04739453A EP04739453A EP1629156B1 EP 1629156 B1 EP1629156 B1 EP 1629156B1 EP 04739453 A EP04739453 A EP 04739453A EP 04739453 A EP04739453 A EP 04739453A EP 1629156 B1 EP1629156 B1 EP 1629156B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
valve
pressure compensator
pump
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.)
Expired - Lifetime
Application number
EP04739453A
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German (de)
English (en)
Other versions
EP1629156A1 (fr
Inventor
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.)
Bosch Rexroth AG
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Bosch Rexroth AG
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Filing date
Publication date
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Publication of EP1629156A1 publication Critical patent/EP1629156A1/fr
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Publication of EP1629156B1 publication Critical patent/EP1629156B1/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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/226—Safety arrangements, e.g. hydraulic driven fans, preventing cavitation, leakage, overheating
    • 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
    • F15B20/00—Safety arrangements for fluid actuator systems; Applications of safety devices in fluid actuator systems; Emergency measures for fluid actuator systems
    • 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
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the directional control valve
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31541—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and multiple output members
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line

Definitions

  • the invention relates to a hydraulic control arrangement for load-independent control of a consumer according to the preamble of patent claim 1.
  • Mobile implements such as mini excavators and compact excavators are increasingly equipped with hydraulic control arrangements, which distribute the pressure medium volume flow of a single pump load-independent on the connected consumers.
  • the control of these consumers is carried out, for example, via a LUDV control block, which has a plurality of each one of the consumer associated valve discs.
  • a continuously adjustable directional control valve is accommodated, to which a pressure-compensating LUDV pressure compensator is assigned.
  • the pressure medium flowing to the consumer first flows through a metering orifice formed by the continuously adjustable directional control valve and then through the pressure compensator.
  • the control piston of this pressure compensator is acted upon at its front by the pressure prevailing between the metering orifice and the pressure compensator.
  • This pressure is reduced compared to the pump pressure by the largely load pressure and pump pressure-independent pressure drop across the metering orifice.
  • In the closing direction of the control piston of the pressure compensator is acted upon by the highest load pressure of all simultaneously operated hydraulic consumers. This means that there is also the highest load pressure between the metering orifice and the pressure compensator, and that the pressure medium partial quantities flowing to all hydraulic actuators operated simultaneously are independent of the individual load pressures Consumers are reduced in the same ratio, if at an increase in the opening cross-sections of the metering orifice, the maximum flow of the associated pump is achieved.
  • the invention has for its object to provide a hydraulic control arrangement in which the locking of the mechanically actuated load is simplified.
  • the LUDV pressure compensators associated with the mechanically operated directional control valves are acted on by a spring acting in the closing direction.
  • the load pressure signaling line common to all consumers is connected to the tank via a current regulator, so that a small amount of control oil always flows to the tank.
  • a safety valve is arranged, via which the connection of the load pressure signaling line to the current regulator can be shut off.
  • An area upstream of the switching valve is connected via a nozzle to a portion of the pressure medium flow path between the pump and the LUDV pressure compensator.
  • the connection of the load pressure signaling line is shut off to the tank and the tapped through the nozzle pressure in a connected to the load pressure signaling line rear control chamber effective, so that the LUDV pressure compensator is brought into its closed position.
  • the load pressure sensing line is connected downstream of the flow regulator to a pump control. After shutting off the load pressure signaling line, the control pressure at the pump control then drops towards the tank so that the pump can only generate the standby pressure.
  • the solution according to the invention is characterized by a very simple structure and a good response.
  • the upstream of the safety valve disposed nozzle is either integrated into the pressure balance, which is reported via this nozzle the voltage applied to the pressure compensator input pressure in the rear control chamber, so that the pressure compensator piston is pressure balanced and is closed by the force of the additional spring ,
  • this nozzle is provided in a branch line which extends from an area upstream of the directional control valve to an area upstream of the safety valve.
  • the pump pressure applied upstream of the directional control valve is reported to the rear pressure chamber.
  • the consumer supplying pump is designed as a fixed displacement pump, which is associated with a differential pressure regulator, which is controlled in response to the load pressure in the load pressure signaling line.
  • the hydraulically operated consumers are each driven by means of a pilot control device, which is assigned its own control oil supply.
  • a shut-off valve is provided, via which the control oil supply of the pilot control device is interrupted to shut off the hydraulically actuated consumers, so that their Valve spool are moved back to the spring-biased home position. According to the invention then takes place via the switching of this shut-off valve and an actuation of the safety valve.
  • valve discs 2, 4 consumers of the mobile implement, such as a wheeled excavator can be controlled.
  • a consumer such as a hydraulic motor 6 of a traction drive mechanically via a lever
  • the function of another consumer for example, a hydraulic cylinder actuating the boom 8 is actuated hydraulically.
  • the pressure medium supply of the control block 1 takes place in the illustrated embodiment via a constant displacement pump 10 whose flow is controlled by a differential pressure regulator 12 in response to the highest load pressure of the actuated consumers.
  • This load pressure is via an LS line 14 to a in Closing direction effective control surface of the differential pressure regulator 12 out, while acting in the opening direction control surface is acted upon by the pump pressure.
  • Each of the valve disks 2, 4 has a continuously adjustable directional control valve 16, which in each case has directional parts 20, 22 and a speed part 18.
  • the direction parts 20, 22 control the pressure medium flow to and from the consumer and the speed part 18 determines the pressure medium volume flow, which is adjustable by controlling a metering orifice. Downstream of this metering orifice, in each case a LUDV pressure compensator 24 is provided which, as described at the outset, keeps the pressure drop across the metering orifice constant regardless of the load.
  • Each pressure compensator 24 is acted upon in the control position in the opening direction of the individual load pressure of the associated load and in the closing direction of the highest load pressure, which is tapped via the LS line 14.
  • the directional control valve 16 of the valve disc 2 is mechanically operated, for example via a lever, while the directional valve 16 of the valve disc 4 is actuated via a pilot valve 26, which consists in principle of pressure reducing valves, at the input of a control oil supply 28 is applied pressure applied and at whose output in response to the adjustment of the pilot control device 26, a control pressure is generated, which is applied to actuate the directional control valve 16 to control chambers 31, 33 of the directional control valve 16 of the valve disk 4.
  • an electrically operated shut-off valve 30 is provided, via which the control oil supply 28 with a tank T is connectable. In the operating position, this shut-off valve 30 is switched so that the pilot control device 26 is supplied with control oil.
  • the area downstream of the shut-off valve 30 is connected via a control line 32 to a control chamber of a safety valve 34, which is designed as a 2/2 way valve.
  • the safety valve 34 is biased by a spring into a switching position in which the LS line 14 is shut off.
  • the control oil supply pressure provided by the control oil supply 28 acts in the control space of the safety valve 34, so that it is brought into a passage position against the force of the spring.
  • a current regulator 36 is arranged, via which the LS line 14 is connected to the tank T. That through the LS line flows in the open position of the safety valve 34 from a constant control oil volume flow to the tank T from down, the size of which depends on the setting of the flow control valve 36.
  • the pressure in the LS line 14 is limited by a pressure limiting valve 37, which is arranged between the flow control valve 36 and the safety valve 34.
  • valve disc 2 A structure of the valve disc 2 will be explained below with reference to the enlarged view in FIG.
  • Each of the above-described valve discs 2,4 has a pressure port P to which the pump pressure is applied, a tank port S connected to the tank, an LS port LS connected to the LS port 14, and two with the consumer, in the present case the hydraulic motor 6 connected working ports A, B.
  • a valve spool 38 of the directional valve 16 of the valve disc 2 is biased via a centering spring assembly 40 in its illustrated basic position.
  • valve spool 38 is guided in a valve bore 44, which in the radial direction to a pressure chamber 46, an inlet chamber 48, two approximately symmetrically to the pressure chamber 20 disposed drain chambers 50, 52, two on both sides thereof arranged working chambers 54, 56 and two adjacent thereto tank chambers 58, 60 is extended.
  • the valve spool 16 has a central measuring diaphragm collar 62 which, together with the remaining annular web between the pressure chamber 46 and the inlet chamber 48, determines a measuring diaphragm forming the speed part 18.
  • a measuring diaphragm collar 62 On both sides of this measuring diaphragm collar 62, two control collars 64, 66 and two tank collars 68, 70 of the directional part 20, 22 are arranged on the valve slide 38.
  • the pressure chamber 46 is connected to the pressure port P and the two tank chambers 58, 60 are connected to the tank port S.
  • the inlet chamber 48 is connected via an inlet channel 72 to the inlet of the pressure compensator 24. Their output is connected via two drainage channels 74, 76 with the discharge chamber 50, 52 and the two working chambers 54, 56 via working channels 78, 80 to the working port A and B respectively.
  • the pressure compensator 24 is shown in its closed position. It has a pressure compensator piston 84, which is guided axially displaceably in a pressure balance bore 82.
  • the pressure balance piston 84 is designed as a stepped piston, wherein the smaller piston surface is supported in the closed position on a shoulder 86 of the inlet channel 72.
  • the shoulder surface 86 of the pressure compensator piston 84 facing this shoulder 86 is in the control position with the pressure in the drainage channels 74, 76, i. applied to the load pressure on the associated consumer.
  • the larger diameter (top of Figure 2) of the pressure compensator piston 84 immersed in a rear control chamber 88 which is connected via an LS channel 90 to the LS port.
  • the pressure compensator piston 84 has an axial bore 92 which opens out in the stepped-back end face and opens out via a load-indicating nozzle 94 in a transverse bore 96 passing through the pressure compensator piston 84 in the transverse direction.
  • the latter is shut off in the closing and control position of the pressure compensator piston 84 by the peripheral walls of the pressure compensator bore 86 and is only opened when the pressure compensator 24 is fully open.
  • the control oil then flows from the input of the pressure compensator via the load indicator in the control chamber 88 and thus in the LS line 14, so that substantially the load pressure of the consumer as the highest load pressure in the LS line 14 is applied.
  • an additional nozzle 98 is provided in extension of the axial bore 92 beyond the transverse bore 96 through which the axial bore 92 is always connected to the control chamber 88.
  • the pressure compensator piston 84 is further biased by a spring 100 against the shoulder 62 in its closed position in which the outer peripheral edge 102 of the gradation of the pressure compensator piston 84, the connection between the inlet channel 72 and the drainage channels 74, 76 has been controlled.
  • the spring 100 is supported on a screwed into the pressure balance bore 82 screw plug 104.
  • the valve disk 4 assigned to the hydraulic function has, in principle, the same structure, although the pressure compensator piston 106 is not formed with a nozzle 98 and thus there is no permanent connection between the axial bore 108 and the control chamber 110. Furthermore, the pressure compensator piston 106 is not biased by a spring into its closed position.
  • the valve slide 16 When the hydraulic motor 6 is actuated, the valve slide 16 is moved by hand via the adjusting lever into an open position, so that the measuring diaphragm of the speed part 18 is opened.
  • the pump pressure which acts against the effective in the closing direction of the load pressure.
  • the pump pressure increases until the pressure compensator piston 84 opens the connection to the drainage channels 74, 76.
  • the pressure medium can then flow via the direction parts 20, 22 to the hydraulic motor 6 and from this back to the tank. If only the hydraulic motor 6 is actuated, the pressure compensator 24 is brought by the load pressure on the hydraulic motor 6 in the fully open position, so that this load pressure is reported in the LS line.
  • shut-off valve 30 the control oil supply of the pilot control device 26 is shut off, so that the directional control valve 16 of the valve disk 4 is moved back to its basic position and correspondingly no activation of the hydraulic cylinder 8 takes place.
  • the shut-off valve 30 is in the control line 32 also the tank pressure, so that the opened safety valve 34 is brought into its closed position.
  • the spring chamber of the differential pressure regulator 12 is relieved via the flow regulator 36 to the tank T out, so that the differential pressure regulator 12 can only generate the standby pressure.
  • control oil volume flow is interrupted by the safety valve 34 of the pressure compensator 24 of the valve disc 2 via the axial bore 82, the transverse bore 96, the nozzle 98 and the LS line 14 and thus no pressure drop across the pressure compensator 24 more arises due to this control oil flow is the pressure compensator piston 84 pressure balanced and by the force of the spring 100 in its closed position pushed back and thus shut off the connection to the hydraulic motor 6.
  • shut-off valve 30 all mechanically operated functions are thus locked by actuation of the shut-off valve 30.
  • the dimensioning of the spring 100 and the cross section of the nozzle 98 is selected so that on the one hand a secure locking of the mechanically actuated valve discs 2 is possible, but on the other hand, the above-described LUDV function is only slightly affected.
  • FIG. 1 shows a variant of the invention, according to which the nozzle 98 'is not arranged in the pressure compensator piston 84 but in a branch line 112, via which the pressure medium flow path downstream of the pump 10 and upstream of the metering orifice with a portion of the LS line 14 upstream of Safety valve 34 is connected.
  • a control oil volume flow constantly flows via the flow regulator 36 to the tank T via this nozzle 98 '.
  • the safety valve 34 acts on the nozzle 98 ', the pressure at the output of the pump in the load-sensing line 14 and thus in the control chamber 88, so that the pressure compensator 24 is also returned to its closed position.
  • a hydraulic control arrangement for controlling a consumer, with at least one mechanically actuated, continuously adjustable directional control valve, which is followed by a LUDV pressure compensator.
  • the control arrangement is designed with a spring acting on the pressure compensator piston in a closed position.
  • a highest load pressure of all consumers leading LS line is connected via a current regulator to a tank, with the current regulator and a pump control in the sense of reducing the delivery volume is relieved.
  • the LUDV pressure compensator is pressure compensated via a nozzle via which a connection between the LS line and a portion of the Druckstoffströmungspfades downstream of the pump and upstream of the output of the pressure compensator is made.
  • this nozzle is integrated into the pressure compensator piston.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (7)

  1. Ensemble de commande hydraulique destiné au pilotage d'un consommateur (6, 8), avec au moins un distributeur (16) actionné mécaniquement et réglable en continu, en aval duquel est montée une balance de pression (24) qui peut être alimentée par la pression de charge du consommateur associé (6) dans le sens d'ouverture et par une pression de charge maximale de tous les consommateurs pilotés, présente dans un espace de commande (88) arrière, dans le sens de fermeture, cette pression de charge pouvant être conduite par une ligne de détection de charge ou ligne LS (14) vers un dispositif de régulation (12) d'une pompe (10), et avec une soupape de sûreté (34) à l'actionnement de laquelle la balance de pression peut être amenée dans une position de fermeture pour la liaison avec le consommateur (6), caractérisé en ce qu'un piston de balance de pression (84) peut être soumis à un ressort (100) dans sa position de fermeture, la ligne LS (14) est reliée au réservoir par une soupape de régulation de débit (36), la soupape de sûreté (34) est disposée dans la ligne LS (14) entre le régulateur de débit(12) et la balance de pression(24) et une pression agissant dans l'espace de commande (88) lors de la commutation de la soupape de commande est prélevée par une buse (98) sur une section d'écoulement du moyen de pression en aval de la pompe (10) et en amont d'une sortie (74, 76) de la balance de pression (24).
  2. Ensemble de commande selon la revendication 1, dans lequel la buse (98) est intégrée dans le piston de balance de pression (84) et relie l'espace de commande arrière (88) à l'entrée de la balance de pression.
  3. Ensemble de commande selon la revendication 1, dans lequel la buse (98') est disposée dans une ligne de dérivation (112) qui s'étend entre la sortie de la pompe (10) et une zone de la ligne LS (14) en amont de la soupape de sûreté (34).
  4. Ensemble de commande selon l'une quelconque des revendications précédentes, le régulateur de pompe étant un régulateur de pression différentielle (12) et la pompe étant une pompe à cylindrée constante.
  5. Ensemble de commande selon l'une quelconque des revendications précédentes, la fonction d'un autre consommateur (8) étant commandée hydrauliquement par un appareil pilote (26) qui est raccordé à une alimentation en huile de commande (28) pouvant être coupée de l'appareil pilote (26) par une soupape d'arrêt (30), la soupape d'arrêt (30) pouvant amener la soupape de sûreté (34) dans sa position de blocage.
  6. Ensemble de commande selon la revendication 2, le piston de balance de pression (84) ayant un orifice axial (92) qui, par le biais d'une buse de signalisation de charge (94), débouche sur un orifice transversal (96) dont l'ouverture est commandée lorsque la balance de pression (24) est grande ouverte, la buse (98) reliant l'orifice transversal (96) à l'espace de commande arrière (88).
  7. Ensemble de commande selon l'une quelconque des revendications précédentes, la buse (98, 98') ayant une section plus petite qu'une buse de signalisation de charge (96) du piston de balance de pression (84).
EP04739453A 2003-06-04 2004-05-28 Ensemble commande hydraulique Expired - Lifetime EP1629156B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10325295A DE10325295A1 (de) 2003-06-04 2003-06-04 Hydraulische Steueranordnung
PCT/EP2004/005835 WO2004109019A1 (fr) 2003-06-04 2004-05-28 Ensemble commande hydraulique

Publications (2)

Publication Number Publication Date
EP1629156A1 EP1629156A1 (fr) 2006-03-01
EP1629156B1 true EP1629156B1 (fr) 2006-10-25

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP04739453A Expired - Lifetime EP1629156B1 (fr) 2003-06-04 2004-05-28 Ensemble commande hydraulique

Country Status (6)

Country Link
US (1) US7395662B2 (fr)
EP (1) EP1629156B1 (fr)
JP (1) JP5081447B2 (fr)
AT (1) ATE343687T1 (fr)
DE (2) DE10325295A1 (fr)
WO (1) WO2004109019A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013224655A1 (de) * 2013-12-02 2015-06-03 Robert Bosch Gmbh Steueranordnung und Steuerventil für eine derartige Steueranordnung

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10325296A1 (de) * 2003-06-04 2004-12-23 Bosch Rexroth Ag Hydraulische Steueranordnung
DE102007028864A1 (de) * 2007-03-27 2008-10-02 Robert Bosch Gmbh Hydraulische Steueranordnung
WO2011096001A1 (fr) * 2010-02-02 2011-08-11 Bucher Hydraulics S.P.A. Section hydraulique pour applications de détection de charge et distributeur hydraulique multiple
DE102010009704A1 (de) * 2010-03-01 2011-09-01 Robert Bosch Gmbh Hydraulischer Fahrantrieb und Verfahren zum Steuern eines derartigen Fahrantriebs
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DE502004001862D1 (de) 2006-12-07
US20060218914A1 (en) 2006-10-05
WO2004109019A1 (fr) 2004-12-16
US7395662B2 (en) 2008-07-08
DE10325295A1 (de) 2004-12-23
EP1629156A1 (fr) 2006-03-01
JP2006526744A (ja) 2006-11-24
JP5081447B2 (ja) 2012-11-28
ATE343687T1 (de) 2006-11-15

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