EP2542788B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP2542788B1
EP2542788B1 EP10798271.2A EP10798271A EP2542788B1 EP 2542788 B1 EP2542788 B1 EP 2542788B1 EP 10798271 A EP10798271 A EP 10798271A EP 2542788 B1 EP2542788 B1 EP 2542788B1
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EP
European Patent Office
Prior art keywords
control
pressure
valve
control block
block
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
EP10798271.2A
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German (de)
English (en)
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EP2542788A1 (fr
Inventor
Wolfgang Kauss
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2542788A1 publication Critical patent/EP2542788A1/fr
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Publication of EP2542788B1 publication Critical patent/EP2542788B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or 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
    • 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
    • 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
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/85978—With pump
    • Y10T137/85986—Pumped fluid control
    • Y10T137/86002—Fluid pressure responsive
    • Y10T137/86019—Direct response valve

Definitions

  • the invention relates to a hydraulic control arrangement for pressure medium supply of two consumer groups according to the preamble of claim 1.
  • LS Load Sensing
  • throttle systems For pressure medium supply of hydraulic consumers of mobile equipment, such as excavators, tractors, backhoe loaders LS (Load Sensing) or throttle systems are often used.
  • the pump pressure is regulated as a function of the highest load pressure of the consumers.
  • LS control blocks To be able to set the pressure medium volume flow to each consumer independent of the load pressure, in the case of so-called LS control blocks, each of the consumers is assigned an adjustable measuring orifice and a pressure compensator which keep the pressure medium volume flow constant and independent of the load pressure.
  • LUDV systems a subgroup of LS systems - the pressure balance is acted upon in the closing direction by the highest load pressure of all consumers and in the opening direction by the pressure downstream of the metering orifice.
  • the available volume flow in these LUDV systems is proportionally divided in the ratio of the opened metering orifice cross sections.
  • the pump flow rate is thus adapted to the respective requirements.
  • the pump in a load pressure-dependent throttle system, the pump always promotes the maximum possible or constant flow rate.
  • the pump can be designed as a constant or variable.
  • These throttle control systems use so-called open-center control blocks, as described, for example, in data sheet RD 64 266 or RD 64 122 of Bosch Rexroth AG.
  • These throttle control blocks have a multiplicity of directional control valve elements, which in their basic position lead the pump volume flow with low pressure loss via a circulation channel back to the tank.
  • the volume flow to the individual consumers is divided depending on the respective load pressure, the pressure medium preferably flows to the consumer with the lowest load pressure.
  • a pump pressure sets in that corresponds approximately to the highest load pressure of the consumer plus a predetermined pressure difference. Accordingly, the pump pressure must be throttled accordingly to actuate the load-lowest consumer, so that considerable throttle losses occur.
  • a backhoe loader has a loading shovel on its front and excavator equipment on the rear, so the backhoe loader combines the functions of a wheel loader and an excavator.
  • the control of the front attachments and the rear attachments usually takes place via a respective control block, for cost reasons, often a throttle control block is used for the excavator function, which allows a relatively sensitive control of the attachment with little effort, but has said throttling losses.
  • Another problem is that the rear-side hydraulic consumers and the front hydraulic consumers are often operated at different load pressure level, so that with a common pump setting to the highest load pressure and the load pressures must be throttled to other consumers considerably.
  • DE 43 22 127 B4 and DE 44 17 962 A1 discloses a hydraulic control arrangement with two control blocks, one of which is designed as a LS control block and another control block as a throttle control block with an open-center directional control valve. Both the LS control block and the throttle control block are supplied by a common variable displacement pump with pressure medium, which is controlled in response to the highest load pressure of both control blocks, so that the pump pressure is always a predetermined pressure difference above the highest load pressure of the system.
  • the directional valve of the throttle control block is one of the pump pressure leading pump line branching LS control line through the open center of the directional control valve relieved to the tank so that is throttled by adjusting the directional control valve volume flow and increases according to the reported to the variable control pressure.
  • the maximum control pressure at the throttle control block is limited by a pressure relief valve.
  • variable displacement pump When controlling different consumer groups with different load pressure levels, the variable displacement pump must be adjusted for the highest load pressure and this high load pressure must be throttled to the control block with lower load pressure level - the throttle losses are significant.
  • the invention has for its object to provide a hydraulic control arrangement, with the two consumer groups with different load levels can be controlled with reduced losses.
  • the hydraulic control arrangement has a variable depending on a load pressure or control variable variable pump for pressure medium supply two consumer groups, each of which a control block is assigned, wherein the tapped in one of the control blocks control pressure is limited by a pressure relief valve.
  • a pressure limiting valve assigned to the other control block is provided for limiting the control pressure levels at a pressure different from the first pressure limiting valve.
  • the control pressure applied in the respective control block which can correspond to the maximum load pressure of the consumer controlled by the control block, is limited to different levels be so throttling losses are limited in the control block with lower control pressure level. Due to this lower control pressure level, the losses compared to the conventional solution are significantly reduced, since only a limited control oil flow rate flows through the control block - this is accompanied by an improvement of the response and controllability, especially in mechanical operation.
  • the control arrangement according to the invention thus takes place practically a decoupling of the maximum control pressures in both control blocks - this is the case of the prior art without a model.
  • control blocks are designed either identically or differently, wherein in principle throttle control blocks, LUDV control blocks or LS control blocks can be used.
  • this is preferably designed in the open-center design, wherein the control line is connected in the basic position in circulation to the tank.
  • control blocks are connected in series with their control lines, wherein the load pressure is limited in the adjacent to the variable displacement pump in the flow direction control block to a higher value than the load pressure of the other control block.
  • control lines are preferably connected to each other via a check valve which opens in the direction of the downstream control block.
  • control lines of the control blocks are connected in parallel.
  • control line is tapped in a designed as a throttle control block control block via a flow control valve from a pump pressure leading feed line.
  • control block is designed with a lower control pressure level than the throttle control block and the control pressure with a higher control pressure level than LUDV or LS control block, wherein downstream of said flow control valve, a LS-switching valve is provided, which in the closing direction of the control pressure in the other control block with higher control pressure level and is acted upon in the opening direction by the control pressure in the throttle block.
  • a LS-switching valve downstream of said flow control valve, a LS-switching valve is provided, which in the closing direction of the control pressure in the other control block with higher control pressure level and is acted upon in the opening direction by the control pressure in the throttle block.
  • the higher control pressure level control block provides steering via a priority valve.
  • variable displacement pump is preferably driven depending on the higher of the load / control pressures in the steering, in the primary control block (higher control pressure level) or in the secondary control block (lower control pressure level).
  • FIG. 1 shows a circuit diagram of a hydraulic control assembly of a backhoe loader, the rear side has an excavator and front loading shovel.
  • the control arrangement is designed with two control blocks 2, 4, the latter being assigned to the rear-side dredger and the control block 2 of the front-side loading shovel.
  • a steering 6 of the backhoe loader is supplied with pressure medium.
  • the control arrangement further has an in FIG. 1 only schematically illustrated variable displacement pump 10, which is adjusted in response to the highest load pressure of the driven loads so that the pump pressure is a predetermined pressure difference above this highest load pressure.
  • variable displacement pump 10 can be designed, for example, as an axial piston pump, which draws in pressure medium from a tank 11 and conveys it into a pump line 12.
  • swash plate 13 can be pivoted in conjunction with two actuating cylinders 14, 15.
  • Both actuating cylinders are differential cylinders, which have a piston 16, 17 and in each case a piston rod 18, with which they engage the swash plate 13.
  • the piston surface of the piston 17 of the actuating cylinder 15 is smaller than the piston area of the piston 16 of the other actuating cylinder.
  • Extending the piston rod 18 of the adjusting cylinder 14 causes a reduction and extension of the piston rod 18 of the adjusting cylinder 15, an increase in the swivel angle of the swash plate and thus the delivery volume of the variable 10.
  • the pressure in the actuating cylinder 15 exerts a spring 19 on the swash plate 13 a force in the direction of increasing the pivot angle.
  • the pressure chamber of the actuating cylinder 15 is constantly connected to the supply line 12.
  • the inflow and outflow of pressure medium to and from the pressure chamber of the adjusting cylinder 14 is controlled by a pump control unit 25 which is constructed on the variable displacement pump 10 and which has a connection LS to which a load-signaling line 26 is connected.
  • the pump control unit 25 has an LS pump control valve 27 and a pressure regulating valve 28 which is set to a pressure occurring in the usual way load pressures.
  • the pressure control valve 28 has a first port which is connectable via a discharge line 29 to the tank 11.
  • a second connection of the pressure regulating valve 28 is located on the pump line 12.
  • a third connection, which can be connected to the first or the second connection, is connected to the pressure chamber of the adjusting cylinder 14.
  • a connection of the LS pump control valve 27 is located on the discharge line 29, a second connection on the supply line 12.
  • a third connection of the pump control valve 27 can be connected to its first or second connection and permanently connected to the first connection of the pressure regulating valve 28.
  • a slider of the pressure control valve 28 is acted upon by a compression spring 30 in the sense of increasing the pivot angle and the inlet pressure in the sense of a reduction of the pivot angle of the variable displacement pump 10.
  • a slide of the LS-pump control valve 27 is acted upon in the sense of increasing the pivot angle of the variable displacement pump 10 by a compression spring 31 and prevailing in the load-sensing line 26 pressure and in the sense of reducing the pivot angle of the inlet pressure.
  • the two control blocks 2, 4 are each designed as throttle control blocks.
  • a lifting cylinder 32 and a bucket cylinder 34 of the front loading bucket are operated in addition to the steering 6.
  • a further control block 4 is the front-side equipment with two parallel swivel cylinders 36, a boom cylinder 38, a dipper arm 40 and a bucket cylinder 42 driven.
  • the control block 2 designed as a throttle control block essentially consists of an input section 44 and two substantially identically constructed directional control valve sections 46, 48 and an output section 50.
  • a tank connection T a pressure connection P connected to the pump line 12
  • a pressure connection P connected to the pump line 12
  • the load pressure Steering 6 leading load signaling connection DLS connected to the load sensing line 26 LS connection, connected to the steering 6 working port D, two connected to the lifting cylinder 32 working ports LA1, LB1, two connected to the blade cylinders 34 working ports LA2, LB2 and another LS Connection provided.
  • the tank connection T is connected to the tank 11 via a tank channel 52.
  • a biasing valve 54 is provided which opens the pressure medium connection to the tank 11 when the pressure applied in the tank line 52 pressure is greater than the equivalent of a closing spring of the biasing valve 54.
  • the rear-side dredger associated control block 4 has four directional control valve sections 56, 58, 60, 62, whose structure corresponds to the directional control valve sections 46, 48 of the control block 2. Furthermore, the control block 4 is designed with an input section 64 and an output section 66. At the input section 64, a pressure port P connected to the pump line 12, a further LS port connected to the LS port of the control block 2 and a tank port T connected to the tank passage 52 are formed.
  • the two control blocks 2, 4 are thus connected in parallel with respect to a pressure medium supply via the pump line 12, while they are connected in terms of a load pressure or a corresponding pressure leading control line via the two terminals LS-LS in series. This is further illustrated by the following figures.
  • FIG. 3 shows an enlarged view of the input section 44 and the directional valve section 46.
  • This is biased by a spring and the voltage applied to the steering 6 load pressure, which is tapped from the terminal DLS, in a basic position in which the pump line 12 is connected via a steering channel 70 to the working port D, to which the steering 6 is connected.
  • the priority valve 68 In the opposite direction acts on a slide of the priority valve 68, the pressure in the steering channel 70, so that with increasing pressure in this steering channel 70, the priority valve 68 is moved to a position in which a pressure medium connection is opened to an inlet channel 72.
  • the priority valve 68 is adjusted by the pressure in the steering channel 70 so that the pressure medium connection to the steering channel 70 is completely closed, so that the pressure medium flows through the priority valve 68 into the inlet channel 72.
  • a control line 74 From the inlet channel 72 branches off a control line 74, in which a flow control valve 76 is provided, via which a control oil volume flow is diverted from the inlet channel 72.
  • the pressure downstream of the flow control valve 76 is limited via a pressure limiting valve 78 to a predetermined control pressure level.
  • the output of the pressure relief valve 78 opens into a drain channel 72, which is connected to the tank port T of the input section 44 and thus connected to the tank line 52.
  • the pressure downstream of the flow control valve 76 is reported to the input of a shuttle valve 80. Its other input terminal is acted upon by the pressure at the terminal DLS, so that the higher of these pressures is reported via the LS port in the LS line 26 and the variable displacement pump 10 is adjusted in response to this pressure.
  • the directional control valve section 46 has an open-center directional control valve 82, which - as shown - by hand or hydraulically or electro-hydraulically adjustable.
  • the basic structure of the directional control valve 82 is described in the aforementioned data sheets RD 64 266 or RD 64 122, so that in terms of details on the relevant embodiments Reference is made and only the essential components for understanding the invention will be explained.
  • the OC directional control valve 82 has a pressure port P connected to the intake passage 72, a tank port T connected to the drain passage 84, a control port D connected to the control line 74, two output ports A, B connected to the working ports LA1, LB1, as well as a control output D ', which opens in a further section of the control line 74, which according to FIG. 1 both control blocks 2, 4 interspersed. For clarity, it is omitted to provide the individual sections of the control line 74 upstream and downstream of the individual valves with separate reference numerals.
  • the ports P, T, A, B of the OC-way valve 82 are shut off, but the control oil connections D, D 'are connected to each other, so that the control oil 82 can flow through the directional control valve substantially without pressure.
  • the two working ports A, B of the OC-way valve 82 are connected via working channels 86, 88 with the working ports LA1, LB1. These working channels 86, 88 act depending on the adjustment of the OC-way valve 82 as a supply or return line.
  • a combined Nachsaug- / pressure relief valve 90, 92 is provided, on the one hand, the pressure in the working lines 88, 86 is limited and, second, in the case of a pulling load pressure fluid from the tank 11 in the be sucked magnifying pressure space.
  • valve sections 56, 58, 60, 62 of the control blocks 2, 4 have the same structure as that of FIG. 3 described directional valve section 46, so that further explanations are unnecessary.
  • control line 74 is connected to the LS connection of the input section 64 of the control block 4, so that this control line 74 also continues in the control block 4.
  • a deflection 94 is provided, via which the control line 74 are connected to a all sections 64, 56, 58, 60, 62 common drain line 96 which is connected via the tank port T of the input section 64 to the tank line 52 is.
  • the pump line 12 is connected to the pressure port P of the input section 64 and opens into a common all sections of the control block 4 supply line 98.
  • a check valve 100 is arranged, the control oil flow to the directional valve sections 56, 58, 60th , 62 permits and locks in the opposite direction.
  • the check valve 100 allows a control oil flow to the control block 4, when the control pressure / load pressure in the region of the control block 2 is greater than in the control block 4th
  • the pressure downstream of the check valve 100 is limited via a further pressure relief valve 102 to a pressure level which is below the pressure level limited by the pressure limiting valve 78.
  • the control oil flows through all OC-way valves 82 almost without pressure in circulation to the tank 11th
  • the control oil volume flow is limited via the peripheral edges of the directional control valves 82 of the control block 4 and thus reduces the throttle losses. That is, via the two pressure relief valves 78, 102, the load pressure level is every Control block 2, 4 limited to an optimal level in terms of minimizing the Steueröldrosselmanne, the pressure level in the control block 4 is below that of the control block 2.
  • OC-way valves 82 allow with minimal effort a very sensitive control of the individual hydraulic consumers - but there are still throttle losses.
  • another control block for example a LUDV control block, may also be used. Such an embodiment is based on FIG. 4 explained.
  • control of the hydraulic load of the excavator device also takes place again via a throttle control block 4, which only in the construction of the input section 64 of the embodiment according to FIG. 1 differs so that only the differences are explained below.
  • the control block assigned to the loading shovel is embodied as a LUDV control block 2 'with an input section 104 and two identically designed LUDV sections 106, 108 and an end plate 110.
  • the variable displacement pump 10 has the same construction as in the previously described embodiment.
  • the structure of the LUDV control block 2 ' is based on FIG. 5 explained.
  • the supply of the steering 6 takes place in the same manner as in the embodiment described above via a priority valve 68, in the sense of a pressure medium supply of the steering 6 of the voltage applied to the terminal DLS load pressure of the steering and in terms of a pressure medium supply of the LUDV sections 106, 108 through the Pressure downstream of the priority valve 68, that is acted upon by the pressure in the steering channel 70.
  • a priority valve 68 To a second output port of the priority valve 68 is as previously described Embodiment of the inlet channel 72 connected, via which the pressure medium flows to the LUDV sections 106, 108.
  • the LUDV section 106 has a structure as in the aforementioned DE 199 30 618 A1 or in data sheet RD 64 122 of Bosch Rexroth AG.
  • Such a LUDV section 106 has a continuously adjustable LUDV directional control valve 112 which has a speed part formed by a metering orifice 114 and a directional part 116, via which the pressure medium flow direction to and from the associated consumer, in this case the lifting cylinder 32, is determined.
  • a pressure port P of the directional control valve 112 is connected to the inlet channel 72.
  • a discharge port T is in fluid communication with the drain port 84 connected to the tank port T, two output ports A, B are connected to the two working ports LA1, LB1 via the working ports 86, 88, and a pressure compensator port C is connected to the input of a LUDV pressure compensator 118 , which in the closing direction of the pressure in a load-sensing line 120 and in the direction of increasing a throttle cross-section of the pressure at the pressure compensator port C, ie from the pressure downstream of the metering orifice 114 is acted upon.
  • the LUDV pressure compensator is fully opened, the pressure downstream of the metering orifice 114 is reported to the load indicator line 120.
  • the pressure drop across the metering orifice 114 is held constant load pressure independent and throttled at the entrance of the LUDV pressure compensator 118 applied maximum load pressure to the individual load pressure.
  • the throttled to the individual load pressure pressure fluid then flows from the output of the pressure compensator 118 via a port P 'of LUDV-way valve 112 and the direction portion 116 and the corresponding working channel 86, 88 in the increasing pressure chamber of the lifting cylinder 32 and from the decreasing pressure chamber via the corresponding working line 88, 86, the directional part 116 and the drainage channel 84 to the tank 11 from.
  • the working channels 86, 88 is - as in the embodiment described above - each a combined Nachsaug- / pressure relief valve 90, 92 arranged.
  • the load sensing line 120 is connected to the LS port of the input section 104 and connected via another check valve 122 to the steering load pressure leading terminal DLS.
  • the check valve 122 opens, so that then the steering load pressure is reported in the LS line 26.
  • the pressure in the load-signaling line 120 is also applied to the LS line 26.
  • the pressure in the load-signaling line 120 is in turn limited via a pressure-limiting valve 78 to a pressure level which is above the pressure level of the throttle control block 4.
  • a small flow control valve 124 is provided parallel to the pressure limiting valve 78, via which a continuous control oil volume flow to the outlet channel 84 is made possible.
  • the load pressure in the LS line 26 is also applied to the connection LS of the input section 64.
  • the drain port T of the input section 64 is in fluid communication with the tank passage 52.
  • a feed line 98 for supplying pressure medium to the directional control valve sections 56, 58, 60, 62 is connected to the pressure connection P.
  • the discharge port T is located on the drain line 96, which is connected via the deflection 94 of the output section 64 with the control block 4 passing through the control line 74. This can be connected via a switching valve 124 and a flow control valve 126 with the supply line 98.
  • control oil volume flow in the control line 74 can be adjusted via the flow control valve 126.
  • the switching valve 124 is acted upon in the closed position by the load pressure in the LS line 26 and in the opening direction by the pressure in the control line 74 and the force of a comparatively weak spring.
  • a control oil supply of the control line 74 is accordingly only when the load pressure to the pressure equivalent of this spring is greater than the control pressure in the control line 74, which adjusts when throttling the cross sections of the respective OC-way valves 82.
  • control line 74 is connected via a check valve 128 to the LS line 26, said check valve 128 opens in the direction of the LS line 26 when the pressure in the control line 74 is greater than the load pressure in the LS line 26. That is, in this case, the higher control pressure in the throttle control block 4 is reported to the pump control unit 25 in the LS line 26 and the pump adjusted according to this higher control pressure.
  • the pressure in the control line 74 is limited as in the embodiment described above by the pressure relief valve 102 to a lower pressure level than in the LUDV control block 2 '.
  • the embodiment corresponds to FIG. 4 the embodiment according to FIG. 1 , so that further explanations are dispensable.
  • a hydraulic control arrangement for supplying pressure medium to two consumer groups via a common variable displacement pump.
  • the pressure level of a control block assigned to one consumer group is set to a different pressure level than that of another control block assigned to the other consumer group.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)

Claims (11)

  1. Dispositif de commande hydraulique comprenant une pompe à débit variable (10) pouvant être réglée en fonction d'une pression de commande pour l'alimentation en fluide sous pression de deux groupes de consommateurs (6, 32, 34 ; 36, 38, 40, 42), auxquels est à chaque fois associé un bloc de commande (2, 4), le niveau de pression de commande dans l'un des blocs de commande (2) étant limité par une soupape de limitation de pression (78), caractérisé par une soupape de limitation de pression (102) associée à l'autre bloc de commande (4) pour limiter le niveau de pression de commande à une valeur différente de celle de la première soupape de limitation de pression (78).
  2. Dispositif de commande selon la revendication 1, les blocs de commande (2, 4) étant une paire quelconque de blocs de commande de même type ou de types différents dans le groupe des blocs de commande à étranglement, des blocs de commande LUDV et des blocs de commande LS.
  3. Dispositif de commande selon la revendication 2, dans lequel le bloc de commande à étranglement (2, 4) est réalisé suivant une construction à centre ouvert, une conduite de commande (74) étant connectée à un réservoir (11) dans une position de base.
  4. Dispositif de commande selon l'une quelconque des revendications précédentes, dans lequel les blocs de commande (2, 4) sont montés en série avec leurs conduites de commande (74), la pression de commande dans le bloc de commande (2) adjacent à la pompe à débit variable (10) dans la direction de l'écoulement étant limitée à une valeur supérieure à la pression de commande de l'autre bloc de commande (4).
  5. Dispositif de commande selon l'une quelconque des revendications précédentes, dans lequel les conduites de commande (74) des blocs de commande (2, 4) sont connectées les unes aux autres par le biais d'un clapet anti-retour (100).
  6. Dispositif de commande selon l'une quelconque des revendications 1 à 3, dans lequel les blocs de commande (2, 4) sont montés en parallèle avec leurs conduites de commande (74, 120).
  7. Dispositif de commande selon les revendications 2 et 6, dans lequel le débit volumique d'huile de commande dans la conduite de commande (74) est prélevé dans un bloc de commande (4) réalisé sous forme de bloc de commande à étranglement par le biais d'une soupape de régulation de débit (76, 126) par une conduite d'amenée (98) conduisant la pression de la pompe.
  8. Dispositif de commande selon la revendication 7, dans lequel le bloc de commande à étranglement (4) est réalisé à un niveau de pression de commande inférieur et le bloc de commande limité à un niveau de pression de commande supérieur est réalisé sous forme de bloc de commande LUDV ou LS, une soupape de commutation (124) étant prévue en aval de la soupape de régulation de débit (126), laquelle est sollicitée dans la direction de fermeture par la pression de commande dans le bloc de commande (2') avec un niveau de pression de commande supérieur et dans la direction d'ouverture par la pression de commande dans le bloc de commande (4) avec un niveau de pression de commande inférieur.
  9. Dispositif de commande selon l'une quelconque des revendications précédentes, dans lequel le bloc de commande (2) avec un niveau de pression de commande supérieur alimente une direction (6) par le biais d'une soupape de priorité (68).
  10. Dispositif de commande selon les revendications 10 et 7, ou selon l'une quelconque des revendications s'y rapportant, dans lequel la soupape de régulation de débit (76) est disposée en aval de la soupape de priorité (68).
  11. Dispositif de commande selon la revendication 9 ou 10, dans lequel la pompe à débit variable (11) est commandée en fonction de la plus haute des pressions de commande/charge de la direction (6), du premier bloc de commande (2) ou du deuxième bloc de commande (4).
EP10798271.2A 2010-03-01 2010-12-22 Dispositif de commande hydraulique Not-in-force EP2542788B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010009705 DE102010009705A1 (de) 2010-03-01 2010-03-01 Hydraulische Steueranordnung
PCT/EP2010/007883 WO2011107134A1 (fr) 2010-03-01 2010-12-22 Dispositif de commande hydraulique

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EP2542788A1 EP2542788A1 (fr) 2013-01-09
EP2542788B1 true EP2542788B1 (fr) 2014-03-05

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EP (1) EP2542788B1 (fr)
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WO (1) WO2011107134A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012001874A1 (de) 2012-02-01 2013-08-01 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102013220750A1 (de) * 2013-10-15 2015-04-16 Robert Bosch Gmbh Ventilblock mit einer Ventilanordnung
US20170274930A1 (en) * 2014-11-24 2017-09-28 Parker-Hannifin Corporation System architectures for steering and work functions in a wheel
CN104895139B (zh) * 2015-06-12 2018-01-16 圣邦集团有限公司 装载机定量泵和变量泵复合控制系统

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2800814A1 (de) * 1978-01-10 1979-07-12 Bosch Gmbh Robert Hydraulische steuereinrichtung
US4343151A (en) * 1980-05-16 1982-08-10 Caterpillar Tractor Co. Series - parallel selector for steering and implement
US5333449A (en) * 1991-09-02 1994-08-02 Hitachi Construction Machinery Co., Ltd. Pressure compensating valve assembly
FR2693241B1 (fr) 1992-07-03 1994-09-30 Rexroth Sigma Circuit hydraulique de commande en pression d'un distributeur hydraulique du type à centre ouvert.
DE4417962A1 (de) * 1994-05-21 1995-11-23 Rexroth Mannesmann Gmbh Steueranordnung für wenigstens zwei hydraulische Verbraucher
GB2324575B (en) * 1997-04-24 2000-08-09 Caterpillar Inc Load sense hydraulic system
DE19930618A1 (de) 1999-07-02 2001-01-04 Mannesmann Rexroth Ag Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
DE10216119A1 (de) * 2002-04-12 2003-10-23 Bosch Rexroth Ag Hydraulische Steueranordnung in Load-Sensing Technik
EP1676963A3 (fr) * 2004-12-30 2008-12-31 Doosan Infracore Co., Ltd. Dispositif de commande pour les pompes hydrauliques d'excavatrices
US9133605B2 (en) * 2012-02-27 2015-09-15 Husco International, Inc. Flow sensing based variable pump control technique in a hydraulic system with open center control valves

Also Published As

Publication number Publication date
US9404483B2 (en) 2016-08-02
EP2542788A1 (fr) 2013-01-09
WO2011107134A1 (fr) 2011-09-09
US20130213503A1 (en) 2013-08-22
DE102010009705A1 (de) 2011-09-01

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