EP2092200B1 - Systeme hydraulique a double circuit et ensemble de soupape d'interconnexion - Google Patents

Systeme hydraulique a double circuit et ensemble de soupape d'interconnexion Download PDF

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Publication number
EP2092200B1
EP2092200B1 EP07802290A EP07802290A EP2092200B1 EP 2092200 B1 EP2092200 B1 EP 2092200B1 EP 07802290 A EP07802290 A EP 07802290A EP 07802290 A EP07802290 A EP 07802290A EP 2092200 B1 EP2092200 B1 EP 2092200B1
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EP
European Patent Office
Prior art keywords
circuit
pressure
control
valve
circuit system
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
EP07802290A
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German (de)
English (en)
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EP2092200A1 (fr
Inventor
Thomas Weickert
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2092200A1 publication Critical patent/EP2092200A1/fr
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Publication of EP2092200B1 publication Critical patent/EP2092200B1/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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • 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
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • 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
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • 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
    • E02F9/2239—Control of flow rate; Load sensing arrangements using two or more pumps with cross-assistance
    • 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
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/265—Control of multiple pressure sources
    • 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

Definitions

  • the invention relates to a junction valve arrangement for a hydraulic two-circuit system for controlling consumers of a mobile device, in particular a tracked device according to the patent claim 1, and a two-circuit system with such a switching valve arrangement.
  • the present invention seeks to provide a hydraulic dual-circuit system and a suitable Verschoppelventilan extract with a simple structure.
  • connection valve which is designed with at least four control surfaces, wherein two acting in one direction control surfaces of the highest load pressure in a first circle and the pump pressure in the second circle and acting in the other direction control surfaces of the highest Load pressure in this circuit and the pump pressure in the former circle are acted upon.
  • two pressure ports and one LS circuit associated with the first circuit may then be connected to an LS output port associated with the second circuit for summing, thereby preventing a higher load pressure acting in one of the circuits from occurring at low pressure medium demand the other circuit is reported with lower load pressure and high pressure medium requirement.
  • a valve body of the interconnection valve is biased via a centering spring arrangement into a blocking position.
  • check valves are provided in the load pressure lines.
  • an LS line of a circuit is in each case connected to an LS output connection assigned to the other circuit connected to the switching valve.
  • the acted upon by the pump pressure and the load pressure control surfaces of the valve body are made the same size.
  • connection valve is particularly simple in construction, when the pump pressure and the load pressure of a circle in each case act on a spring chamber defining a rear end face and the pump pressure and the load pressure of the other circle on Ringstim vom the valve body.
  • a valve body of the Verschaltungsventils is preferably carried out with a central control collar on which two control edges are designed to aufsteuem the connection between the two pressure ports.
  • the valve body further has two outer LS control coils, on each of which a control edge for auf excusen the connection between the LS input terminal of the one circuit and the LS output terminal of the other circuit is formed.
  • the spring-chamber-side rear surfaces of the two control collars form the above-mentioned rear end faces.
  • Such a structure makes it possible to form the valve body symmetrical, so that the manufacture and assembly is particularly simple.
  • connection valve is further simplified when the above-described check valves are integrated into the valve housing of the connection valve.
  • FIG. 1 shows a circuit diagram of a hydraulic excavator control 1. This is constructed as a two-circuit system with two hydraulic circuits 2, 4, which are each supplied via a variable displacement pump, not shown, with pressure medium.
  • the one with the in FIG. 1 shown control excavator has a chassis with two chains whose traction drives on the two circles 2, 4 are independently supplied with pressure medium.
  • other consumers of the excavator such as a slewing gear, a stick, a spoon or a boom, are controlled via the two-circuit system.
  • the excavator control according FIG. 1 realizing control block is designed in disc design, the two variable displacement pumps, not shown, are connected to pressure ports P 1 and P 2 of the control block.
  • This also has a tank connection T and working connections A 1 , B 1 and A 2 , B 2 , to which the drive of the right or left chain is connected.
  • the other consumers of the excavator such as the drive of the slewing gear, the hydraulic cylinder for actuating the stem, the spoon or the boom are connected.
  • the illustrated control block also has two Load pressure connections, hereinafter referred to LS 1 and LS 2 , tapped via the load in the respective circuit 2, 4 acting load and the flow control valve (not shown) of the variable displacement, which is thus controlled in response to this highest load pressure.
  • LS 1 and LS 2 Load pressure connections
  • the control of the aforementioned consumer takes place in each case via a proportionally adjustable directional control valve 6, which in each case a pressure compensator 8 is connected downstream.
  • the directional control valve 6 has a variable measuring orifice forming a speed part and a directional part, wherein the metering orifice of the pressure compensator 8 is connected upstream and the directional part downstream of the pressure compensator 8 is arranged.
  • Each pressure compensator 8 is beauf beat in the closing direction of the load pressure and in the opening direction of the pressure downstream of the orifice of the directional control valve 6 beiller.
  • the pressure balance piston adjusts depending on the applied control pressures in a control position in which the pressure drop across the metering orifice of the proportionally adjustable directional control valve 6 is kept contant, so that a load pressure independent Volumenstrom horrurtg is possible.
  • Such LS controls are well known, so that can be dispensed with a detailed description of the structure of the directional control valve 6 and the downstream pressure compensator 8.
  • the control of the directional control valve 6 takes place in each case via pilot valves 10, 12, via which a control pressure is applied to the frontal control surfaces of a slide of the directional control valve 6. These pilot valves are actuated, for example, as a function of the actuating movement of a joystick.
  • each directional valve has two working ports, which are each connected via a working line 18 and 20 with the associated load ports A, B.
  • an output connection of the directional control valve 6 is connected via a tank line 22 to the tank connection T of the control block.
  • pressure limiting valves are provided in each case for limiting the maximum pressure supplied to the consumer, the pressure limiting valves with suction function delimiting the pressure at the working ports A 2 , B 2 , B 1 and B 3 and A 4 (not illustrated), so that in a lead of the consumer (negative load) pressure medium can be sucked out of the tank to avoid cavitation phenomena.
  • a respective connected to the load pressure port LS of the two circuits 2, 4 load pressure signaling line 28, 30 is connected via an LS flow control valve 32 and 34 to the common tank line 22.
  • the pressure compensators 8 are designed so that they report in their fully open end position at its input pressure (downstream pressure of the orifice plate) in the load pressure line 28 and 30, so that in this is always the highest load pressure in the respective circuit 2 or 4 ,
  • the above-described directional valves with the associated pressure compensator 8, the pilot valves 10, 12 and the pressure relief valves 24, 25 may each be received in a disk or in a common control block.
  • an interconnecting valve arrangement 38 is provided in an intermediate disc 36, via which the pressure lines 14, 16 of the two hydraulic circuits 2, 4 can be interconnected in certain operating states, so that the actuated consumers of both variable displacement pumps are connected together Pressure medium to be supplied.
  • this has a constructed as a pressure compensating interconnecting valve 40, the pressure compensator slide, hereinafter called valve body 42, with four control surfaces A1, A2, A3, A4 is executed, wherein two acting in one direction control surfaces A1, A2 with the pump pressure of the second circle and the load pressure of the first circle and acting in the other direction control surfaces A3, A4 are applied to the pump pressure of the first circle and the load pressure in the second circle , Accordingly, the control surface A1 via a pressure control line 44 to the pressure line 16 of the second circuit 4 and acting in the same direction control surface A2 via a LS control line 46 to the load pressure signaling line 28 of the first circle.
  • control surfaces A3, A4 are connected via a further pressure control line 48 to the pressure line 14 and another LS control line 50 to the load pressure signaling line 30 of the second circle.
  • the areas of the control surfaces A1, A2, A4 and A3 are the same.
  • the valve body 42 is biased via a Zentrierfederan Aunt 51 in a middle blocking position, in the two connected to the pressure lines 14, 16 pressure ports P1 and P2 and two the first circuit 2 associated ports LS1 and LS1 'and two the second circuit 4 associated ports LS2, LS2 'are shut off.
  • the LS input port LS1 is connected via an LS channel 52 and via a check valve 54, which opens in the direction of the port LS1, to the load pressure signaling line 28 of the first circuit 2, to which the LS output port LS1 'is also connected via an LS branch channel 56 ,
  • the load pressure signaling line 30 of the second circuit 4 is connected via a further LS channel 58 and a further check valve 60 to the LS input connection LS2 and via a further LS channel 62 to the LS output connection LS2 '.
  • the valve body 42 of the Verschschaltventils 40 upwards (see FIG. 2 ) are moved to one of the control positions marked b or down to one of the control positions marked with a.
  • control positions a, b the summed from the circle with the higher pressure level to the other circle Pressure fluid flow rate throttled via the Zuschaltventil 40 to the lower pressure level.
  • the control position is established when the pressure difference between the pump pressure and the load pressure in the first circuit is approximately equal to that in the second circuit.
  • a pressure medium from the second circle 4 is summed to the pressure medium flow rate of the first circle 2, wherein the LS-LS1 and LS2 'are connected to each other, while the two other LS-LS2, LS1' are locked against each other.
  • the check valve 54 prevents that at a lower load pressure in the first circuit 2, the higher load pressure of the second circuit 4 is reported in the first circle, so that in accordance with the first circle associated variable displacement pump is not raised in this case. In the case in which the higher load pressure in the first circuit 2 is applied, it is reported via the opening check valve 54 and the two connected LS connections LS1 and LS2 'to the variable displacement pump of the second circuit and this raised accordingly.
  • the pressure ports P1 and P2 are connected to one another so that pressure medium from the first circuit is summed to the pressure medium volume flow of the second circuit and the LS ports LS2 and LS1 'are connected to one another, wherein the non-return valve 60 prevents a lower load pressure in the first circuit 2 (in the load pressure signaling line 28) is reported to the load pressure signaling line 30 of the second circuit 4.
  • FIG. 3 is a concrete embodiment of a Verschschaltventilan extract 38 according to FIG. 2 shown.
  • FIG. 3 shows a longitudinal section through the valve disc 36 or by a the Verschschaltventilan Aunt 38 receiving valve housing.
  • a valve bore 64 is formed, in the pressure compensator valve or valve body 42 is guided axially displaceable.
  • the valve bore 64 is extended in its central region to two pressure chambers 66, 68, which are separated from one another by a housing web 70.
  • the pressure chamber 66 is connected to the pressure port P1 and the pressure chamber 68 to the pressure port P2.
  • the valve bore is widened in the radial direction in each case to form LS annular spaces 70, 72 and 74, 76, wherein the outer annular spaces 70, 76 are connected to the load pressure signaling channel 30 and thus in these spaces the h O Last load pressure of the second circle 4 is applied.
  • the two inner annular spaces 72, 74 are acted upon in accordance with the load pressure signaling line 28 and thus with the highest load pressure of the first circuit 2.
  • the connection of the two other annular spaces 70, 76 to the load pressure signaling line 30 via corresponding channels with integrated check valve 60 (in Fig. 3 not shown).
  • the valve body 42 has a central control collar 78 on which two control edges 80, 82 designed with fine control notches are formed. Upon axial displacement of the valve body 42 via one of the control edges 80, 82, the connection between the two pressure chambers 66, 68 opened, which - as mentioned above - are connected to the pressure lines 14 and 16 respectively.
  • the pressure chamber 66 is connected to the port P1 and the pressure chamber 68 to the port P2 - for ease of understanding, the terminal designations in the illustration according to FIG. 3 added in parentheses.
  • the valve body 42 has on both sides two collars 84, 86 which are each connected via a radially recessed piston neck to an external control collar 88 or 90.
  • Each control collar 88, 90 is in one Reduction sleeve 92 and 94 out, respectively, which are inserted into an end-side, step-shaped enlarged end portion of the valve bore 64 and thus reduce the effective guide diameter for the valve body 42 and create a surface difference.
  • the control surface A3 limited with the adjacent end face of the Reduzierbuchse 92 a space 96 in which the pressure of the pressure line 14 and thus at the pressure port P1 is applied.
  • the two outer control collars 88, 90 are each slightly downgraded by a piston neck 100, 102 in the middle, so that in each case a control edge 104, 106 is formed.
  • the two end surfaces of the valve body 42 form the control surfaces A1 and A4 (see FIG. 2 ), which are acted upon by the pressure in the pressure line 16 of the second circle or with the highest load pressure of the second circle.
  • end surfaces A1, A4 and the annular end faces A2, A3 are each designed with the same area.
  • the valve body 42 is biased by the Zentrierfederan effet 51 in its illustrated mid-position.
  • This Zentrierfederan effet 51 also acts as a control spring arrangement, and is the concrete Embodiment with two control springs 108, 110 executed, the spring constant is designed so that it is slightly below the pump Ap.
  • the spring force of a control spring 108, 110 corresponds approximately to a pressure of delta-p difference: 3 to 6 bar (determined from experiment).
  • the two control springs 108, 110 are each supported on a spring bushing 112, 114 screwed into the valve bore 64 and each engage via a spring plate 116, 118 on the end faces A1, A4 of the valve body 42.
  • the control spring 108, 110 assigning, radially enlarged Ringstim lake the Reduzierbuchsen 92, 94 serve as an end stop for the spring plates 116, 118. Through these two end stops and the illustrated center position of the valve body 42 is determined.
  • the operating according to the Druckwaagenpririzip interconnecting valve 40 thereby adjusts itself to a control position, so that the funded by the variable displacement pump of the second circuit 4 pressure medium is throttled to the pressure level in the first circuit 2 and the pressure differences (pump pressure-load pressure) in both circuits are approximately equal ,
  • the solution according to the invention is characterized by an extremely compact design, which can be realized with little device complexity.
  • the interposing valve arrangement has a connection valve with two pressure connections, two LS input and two LS output connections, wherein a valve body of the interposing valve is designed with four control surfaces, two of which act in one direction control surfaces from the highest load pressure in the first circuit and the pump pressure in second circuit and acting in the other direction control surfaces of the highest load pressure in the second circuit and the pump pressure in the first circuit are acted upon.

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

Claims (12)

  1. Ensemble de soupape d'interconnexion (38) pour un système à double circuit hydraulique, comprenant une soupape d'interconnexion unique (40), qui présente deux raccords de pression (P1, P2), deux raccords LS d'entrée et deux raccords LS de sortie (LS1, LS2 ; LS1', LS2') ainsi qu'un corps de soupape unique (42), qui peut être sollicité dans une direction par la pression de charge maximale dans le premier circuit (2) et par la pression de pompe dans le deuxième circuit (4), et dans l'autre direction par la pression de charge maximale dans le deuxième circuit (4) et par la pression de pompe dans le premier circuit (2), de sorte qu'en fonction de la différence de pression de commande résultante, agissant sur le corps de soupape (42), les deux raccords de pression (P1, P2) et un raccord d'entrée LS (LS1, LS2) associé à un circuit puissent être connectés à un raccord de sortie LS (LS1', LS2') associé à l'autre circuit.
  2. Système à double circuit hydraulique pour la commande de consommateurs d'un appareil mobile, notamment d'un engin sur chenilles, chaque circuit hydraulique (2, 4) présentant une pompe à cylindrée variable, par le biais de laquelle les consommateurs associés peuvent être alimentés en fluide sous pression, comprenant un ensemble de soupape d'interconnexion (38) selon la revendication 1, les deux circuits (2, 4) pouvant être reliés l'un à l'autre par le biais de l'ensemble de soupapes d'interconnexion (38) de telle sorte que la pompe à cylindrée variable de l'un des circuits (2, 4) transporte du fluide sous pression dans l'autre circuit (4, 2), les pompes à cylindrée variable pouvant être commandées respectivement en fonction de la pression de charge dans chaque circuit associé (2, 4).
  3. Système à double circuit selon la revendication 2, dans lequel le corps de soupape (42) est précontraint par le biais d'un agencement de ressort de centrage (51) dans une position de verrouillage.
  4. Système à double circuit selon l'une quelconque des revendications précédentes 2 ou 3, dans lequel à chaque fois dans une conduite LS (52, 62) conduisant au raccord d'entrée LS (LS1, LS2), est disposé un clapet anti-retour (54, 60) s'ouvrant vers ce raccord.
  5. Système à double circuit selon la revendication 4, dans lequel la conduite LS (52, 62) d'un circuit (2, 4) peut être connectée à chaque fois à un raccord de sortie LS (LS1', LS2') associé à l'autre circuit (2, 4).
  6. Système à double circuit selon l'une quelconque des revendications précédentes 2 à 5, dans lequel les surfaces de commande (A1, A2, A3, A4) du corps de soupape (42) sollicitées par les pressions de pompe et les pressions de charge sont identiques.
  7. Système à double circuit selon la revendication 6, dans lequel la pression de pompe et la pression de charge d'un circuit (2) agissent à chaque fois sur une surface frontale (A1, A4) du côté arrière limitant un espace de ressort et la pression de pompe et la pression de charge de l'autre circuit (4) agissent à chaque fois sur une surface frontale annulaire (A2, A3) du corps de soupape (86).
  8. Système à double circuit selon la revendication 7, comprenant un épaulement de commande central (78), sur lequel sont réalisées deux arêtes de commande (80, 82) pour commander la connexion entre les deux raccords de pression (P1, P2), et comprenant deux épaulements de commande LS extérieurs (88, 90) sur lesquels est à chaque fois réalisée une arête de commande (104, 106) pour la commande de la connexion entre un raccord d'entrée LS (LS1, LS2) d'un circuit (2, 4) et le raccord de sortie LS (LS1', LS2') de l'autre circuit (2, 4), et dont les faces arrière du côté de l'espace de ressort constituent les faces frontales (A1, A4).
  9. Système à double circuit selon la revendication 8, dans lequel un épaulement (84, 86) est réalisé à chaque fois entre l'épaulement de commande (78) et un épaulement de commande LS (90, 92), sur lequel est prévue la surface frontale annulaire (A2, A3).
  10. Système à double circuit selon l'une quelconque des revendications 8 ou 9, dans lequel le corps de soupape (42) est réalisé sous forme symétrique par rapport à l'épaulement de commande central (78).
  11. Système à double circuit selon l'une quelconque des revendications se rapportant à la revendication 4, dans lequel les clapets anti-retour (54, 60) sont disposés dans un boîtier de soupape de la soupape d'interconnexion (40).
  12. Système à double circuit selon l'une quelconque des revendications se rapportant à la revendication 3, dans lequel l'agencement de ressort de centrage (51) présente des ressorts de réglage (108, 110) dont l'équivalent pression est quelque peu inférieur au Δp de la pompe.
EP07802290A 2006-11-15 2007-09-13 Systeme hydraulique a double circuit et ensemble de soupape d'interconnexion Not-in-force EP2092200B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006053897A DE102006053897A1 (de) 2006-11-15 2006-11-15 Hydraulisches Zweikreissystem und Zusammenschaltventilanordnung
PCT/EP2007/007962 WO2008058584A1 (fr) 2006-11-15 2007-09-13 Système hydraulique à double circuit et ensemble de soupape d'interconnexion

Publications (2)

Publication Number Publication Date
EP2092200A1 EP2092200A1 (fr) 2009-08-26
EP2092200B1 true EP2092200B1 (fr) 2011-11-09

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP07802290A Not-in-force EP2092200B1 (fr) 2006-11-15 2007-09-13 Systeme hydraulique a double circuit et ensemble de soupape d'interconnexion

Country Status (8)

Country Link
US (1) US8347617B2 (fr)
EP (1) EP2092200B1 (fr)
JP (1) JP5156754B2 (fr)
KR (1) KR101432564B1 (fr)
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US20130098011A1 (en) * 2011-10-21 2013-04-25 Michael L. Knussman Hydraulic system having multiple closed-loop circuits
CN102588373B (zh) * 2012-03-08 2015-02-18 长沙中联消防机械有限公司 工程机械及其支腿液压控制装置
DE102012022018A1 (de) * 2012-11-12 2014-05-15 Grimme Landmaschinenfabrik Gmbh & Co. Kg Hydraulische Steueranordnung an Arbeitsorganen einer landwirtschaftlichen Maschine
DE102013223288A1 (de) * 2013-11-15 2015-05-21 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102017200418A1 (de) 2017-01-12 2018-07-12 Robert Bosch Gmbh Ventilbaugruppe zur Zweikreis-Summierung
CN112555299B (zh) * 2020-12-02 2022-06-14 安徽江淮汽车集团股份有限公司 双控电磁阀以及液压离合系统

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DE102020200412A1 (de) * 2020-01-15 2021-07-15 Robert Bosch Gesellschaft mit beschränkter Haftung Hydrostatisches Antriebssystem mit einer Druckwaage die zwei parallel wirkende Steuerflächen aufweist

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JP5156754B2 (ja) 2013-03-06
DE102006053897A1 (de) 2008-05-21
WO2008058584A8 (fr) 2009-09-11
CN101542133A (zh) 2009-09-23
KR101432564B1 (ko) 2014-08-22
EP2092200A1 (fr) 2009-08-26
US8347617B2 (en) 2013-01-08
ATE532968T1 (de) 2011-11-15
KR20090108587A (ko) 2009-10-15
JP2010509552A (ja) 2010-03-25
WO2008058584A1 (fr) 2008-05-22
US20100037603A1 (en) 2010-02-18
CN101542133B (zh) 2013-05-22

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