EP2320094B1 - Bloc de soupape - Google Patents

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Publication number
EP2320094B1
EP2320094B1 EP10188785.9A EP10188785A EP2320094B1 EP 2320094 B1 EP2320094 B1 EP 2320094B1 EP 10188785 A EP10188785 A EP 10188785A EP 2320094 B1 EP2320094 B1 EP 2320094B1
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EP
European Patent Office
Prior art keywords
control
valve
consumer
pressure
valves
Prior art date
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Active
Application number
EP10188785.9A
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German (de)
English (en)
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EP2320094A2 (fr
EP2320094A3 (fr
Inventor
Thomas Dr. Fedde
Sarah Flottmeier
Stephan Berkemann
Justus Rennert
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.)
Claas Industrietechnik GmbH
Original Assignee
Claas Industrietechnik GmbH
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Publication of EP2320094A2 publication Critical patent/EP2320094A2/fr
Publication of EP2320094A3 publication Critical patent/EP2320094A3/fr
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Publication of EP2320094B1 publication Critical patent/EP2320094B1/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
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/30—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves

Definitions

  • the present invention relates to a valve assembly for the - in particular load-independent - control of at least one consumer such as a hydraulic cylinder, a hydraulic motor or the like.
  • Applications for such a valve assembly are particularly in the field of agricultural machinery with hydraulically driven or adjustable units or construction equipment.
  • Such a valve assembly which has two hydraulically controlled control edges between two consumer-side connections, a pump and a tank connection, which connect the pump connection and the tank connection with each of the consumer-side connections.
  • the control edges between the pressure port and the consumer-side ports are arbitrarily controllable. When one of them is opened, high pressure passes through a check valve to a first one of the consumer-side ports.
  • the control edge between the second consumer-side terminal and the tank terminal has a control input which is connected to the output of the first control edge, so that when opening the first control edge at the Output occurring high pressure causes the second control edge also to open.
  • hydraulic oil flows to a first chamber of a double-acting consumer, hydraulic oil flow from a second chamber of the consumer via the second consumer-side terminal and the second control edge to the tank.
  • two check valves are provided between the first and second control edge and the two consumer-side ports. Since the entire influx of hydraulic oil to the load must pass through one of the two check valves, the pressure drop that occurs thereby adversely affects the efficiency of a hydraulic machine using the known valve group.
  • the known valve assembly can be used for load pressure independent supply to a consumer by tapping the load flowing to the load at the input of one of the check valves and a load pressure signaling line a Compensator on the pump side connection of the valve assembly and optionally a regulator of the pump is supplied.
  • a Compensator on the pump side connection of the valve assembly and optionally a regulator of the pump is supplied.
  • the pressure on the load pressure signaling line must be reliably equal to the tank pressure despite possible high pressures in other parts of the valve assembly.
  • the first and second control edges controlling the flow of the pressurized fluid between the pump port and the consumer-side ports are each combined as a main control edge in a directional control valve with an auxiliary control edge, the auxiliary control edge of each directional control valve in the locked state of the main control edge over the load pressure signaling line Leakage oil return connects to the tank.
  • the main control edges of the directional control valves must be generously dimensioned to allow the entire flow of oil between pump and consumer to pass with a slight pressure drop.
  • the integration of the auxiliary control edges in these directional control valves increases their space requirements even further.
  • An object of the invention is to provide a valve assembly for driving at least one consumer, in which internal pressure losses are minimized and thus enables operation of the consumer with high efficiency.
  • a valve assembly having two consumer-side terminals, a pump and a tank connection and four each hydraulically controlled via a control terminal control edges, of which a first pump terminal and the first consumer-side terminal, the second pump terminal and the second consumer-side terminal, the third, the first consumer-side connection and the tank connection and the fourth, the second consumer side Connection and the tank connection connects, a first and a second pilot valve for driving the control terminals of each two of the control edges are provided.
  • a float position of the consumer in which it is movable under a force acting on it from the outside, can be realized by respectively assigning a first and a second switching valve to the first and second control edges
  • the second control edge connects optionally with the first and second pilot valve or with the tank connection.
  • the switching valves are designed as directional control valves, in particular the first directional control valve can selectively connect to one of the control terminals of its two associated control edges, in particular the first and third control edge, while the second directional control valve, the second pilot valve with either one of the control terminals of its two associated control edges, in particular the second and fourth control edge connects.
  • a pressure output by the first pilot valve can be forwarded via the first directional control valve on the one hand to the third control edge to allow hydraulic fluid to drain from the first consumer-side connection to the tank connection, and at the same time set the second directional control valve in a position in which there is a at the output of the second pilot valve existing pressure to the control input of the second control edge passes, so as to allow an inflow of hydraulic fluid to the consumer via the second consumer-side connection.
  • control edges are parallel with an output of the first pilot valve and the control connections of the second and third Control edge connected in parallel with an output of the second pilot valve to simultaneously open the first and fourth control edge and so to drive a double-acting consumer in a first direction, or to open the second and third control edge and drive the consumer in the opposite direction.
  • a required for switching the first and second switching valve output pressure of the pilot valves is preferably lower than the output pressure required to open the control edges.
  • the two switching valves each have a second control input to which one of its outputs is returned, so that the pressure prevailing at the output counteracts the pressure applied to the first control input pressure.
  • This recirculated at the second control input pressure can secure the switching valve in the position which it assumes even in a depressurized state, despite a pressure applied to the first control input, so that at the same time pressurizing both switching valves that do not change their switching position.
  • the pilot valves are preferably designed as proportional pressure reducing valves.
  • an individual pressure compensator controlled by the pressure prevailing at one of the consumer-side connections is preferably inserted between the pump connection and the first and second control edges.
  • the highest pressure applied to the consumer-side connections can be forwarded to the individual pressure balance, without thereby changing the pressure present at the other consumer-side connection.
  • the check valves prevent a flow of pressurized fluid from one consumer-side port to the other via the load pressure signaling line and thus an unwilling yielding of the consumer under an external load. Unlocking one of the check valve makes it possible to transmit a decreasing pressure correctly from a consumer-side port to the individual pressure compensator.
  • the unlockable check valves are advantageously arranged to connect the control port of the individual pressure compensator with the tank connection in the locked state. Since the pilot-operated check valves only have to cope with a small fraction of the throughput that runs over the first to fourth control edges, these pilot-operated check valves can be dimensioned small, and correspondingly little space requires the implementation of a connection of the control terminal of the individual pressure compensator with the tank connection via the unlockable check valves.
  • a check valve integrated in the individual pressure compensator makes it possible, in the event of a failure of the pump, to avoid a sudden drop in pressure at the connections on the consumer side and thus an uncontrolled movement of the load under load.
  • Subject of the invention is also a tractor with a valve assembly of the type described above, to which a hydraulically adjustable or driven unit such as a plow or a mower can be connected.
  • Fig. 1 shows a hydraulic diagram of a valve assembly according to a first embodiment of the invention, which may be attached to the front or rear of a tractor, for example, as consumer a control cylinder or a hydraulic motor of a replaceable front or rear aggregate such as a sweeping broom, a snow blade, a plow to connect a multi-part mower or the like.
  • the valve assembly shown in the figure is connected to four lines shown in the lower part of the figure as parallel lines, namely a coming from a pump not shown here high pressure line P, leading to a tank unpressurised line T, a control pressure line Px and a load pressure signaling line LS ,
  • Several copies of the valve assembly can be connected in parallel to the four lines P, T. Px, LS, possibly to several consumers of a connected unit to supply or drive the unit in several degrees of freedom or control.
  • a branch P1 originating from the high-pressure line P extends via an individual pressure compensator C5 controlled by the pressure present on the load pressure signaling line LS to two hydraulically piloted directional valves C1 and C2 reset by a spring.
  • Two consumer-side ports A, B are connected to outputs of the two-way valves C1, C2.
  • the directional control valves are designed in seat construction and arranged so that their valve body is pressed in each case by an overpressure on the consumer-side connection against its seat.
  • the directional control valves C1, C2 are therefore absolutely tight against a high pressure at one of the consumer-side ports, which may occur when an external load acts on a connected consumer, e.g. to a hydraulic cylinder that holds a plow connected to the tractor for road or shunting in a raised position from the ground or presses it against the ground to keep the ploughshare at a desired depth when plowing.
  • Two further directional control valves C3, C4 connect the consumer-side ports A, B with the unpressurized line T.
  • the directional valves C1 to C4 are in Fig. 1 all shown closed.
  • a chamber of a double-acting consumer connected to the connection point A, B can be supplied with hydraulic fluid at the connection A. while from a second chamber of the consumer, the corresponding amount flows through the port B.
  • the directional control valves C2, C3 are open, hydraulic fluid flows via the connection B to the consumer, and via the connection A, it flows back to the tank.
  • the passage area of the directional control valves C1 to C4 is a continuous function of a control pressure applied to a control port c1 to c4 of each directional control valve.
  • Two proportional pressure reducing valves Y1, Y2 serve as pilot valves for generating this control pressure.
  • the pressure reducing valves Y1, Y2 are connected to the control pressure line Px and the unpressurized line T and each have a controlled connection y1, y2, the pressure of which is continuously adjustable electrically between the pressures of the lines Px and T.
  • the pressure reducing valve Y1 controls the pressure on a pilot line 1 connecting control ports c1, c4 of the valves C1, and C4; the pressure reducing valve Y2 controls in an analogous manner via a pilot control line 2, the valves C2 and C3.
  • Unlockable check valves R1, R2 each have a control port r1 and r2, respectively, connected to the pilot control line 1 and 2, an inlet connected to the fuel-side port A and B, and two outlets connected to the unpressurized line T or via line branches LS1 and LS2 and a shuttle valve W1 are connected to the load pressure signaling line LS.
  • a second change-over valve W2 inserted in the load-pressure signaling line LS allows either the pressure shown in the figure at the control port c5 of the individual pressure compensator C5 or that connected to the lines P, T, Px, LS shown in parallel in FIG Switch valve assembly for controlling an external pump supplying the line P.
  • the pressure on the pilot control line 1 increases, and the directional control valves C1, C4 open in proportion to this pressure.
  • the output pressure of the pressure compensator C5 is therefore at the port A, while via the port B pressurized fluid can flow to the tank.
  • the high pressure on the pilot control line 1 leads to switching of the directional control valve R1 into a position in which it connects the connection A to the branch LS1 and at the same time interrupts the connection of the branch LS1 to the unpressurized line T.
  • the load pressure signaling line LS thus carries the pressure prevailing at port A.
  • the pressure compensator C5 regulates in a conventional manner that through them from the pump to the port A running fluid flow such that there is a constant pressure difference between the output of the pressure compensator C5 and its connected to the load pressure signaling line LS control input.
  • This pressure difference is substantially equal to the pressure drop at the control edge of the directional control valve C1, and there is a direct linear relationship between the opening cross section at the control edge of the directional control valve C1 and the volume flow supplied to the consumer via the connection A.
  • Fig. 2 shows a schematic section through the pilot-operated check valve R1 or R2 according to a preferred embodiment.
  • a hole is formed with multi-stepped diameter.
  • a movable piston 11 is housed in a large part of this hole, on the right side of the Fig. 2 .
  • a rear side 12 of the piston 11 is exposed to the pressure of the control pressure line Px; a front side 13 of the piston defines a chamber 14 connected to the non-pressurized line T.
  • An insert 15 screwed into the bore of the housing 10 has a recess 16 of the piston front side 13 engaging projection 17.
  • the projection 17 centers a coil spring 18 which drives the piston 11 against the control pressure acting on its rear side 12 to the right.
  • the insert 15 comprises an axial bore 19 and at least three radial bores 20, 21, 22 intersecting the axial bore 19.
  • the bore 20 opens into the chamber 14, the bore 21 is connected to one of the branches LS1 or LS2 of the load pressure signaling line LS, and the bore 22 with one of the consumer-side terminals A and B in the bore 19, a mandrel 23 is axially displaceable.
  • a mandrel 23 is axially displaceable.
  • In the in Fig. 2 shown position is a narrow tip 24 of the mandrel in a bore 20, 21 connecting portion of the axial bore 19, so that the load pressure signaling line LS is connected to the chamber 14 and is held at tank pressure.
  • the ball 26 and the valve seat 27 thus form a check valve capable of maintaining a high pressure at port A or B, even when the load pressure sensing line LS and with it the bore 21 is depressurized.
  • the cross-section of the piston 11 is many times greater than the diameter of the ball 26, so that a relatively low control pressure on the piston rear side 12 is sufficient to release the ball 26 from its seat 27, even if this by a high Pressure on the device-side connection against the seat 27 is pressed.
  • Fig. 3 shows a valve assembly according to a second embodiment of the invention.
  • the lines P, T, Px, Ls, the valves C1 to C4, Y1, Y2 and R1, R2 and the individual pressure compensator C5 are the same as in Fig. 1 and will not be explained again.
  • a major difference between the design of the Fig. 3 and those of Fig. 1 are additional directional valves V1, V2.
  • the directional control valve V1 connects the controlled port y1 of the pressure reducing valve Y1 with control terminals c3, v2 of the directional control valves C3 and V2 and the control terminals c1, r1 of the directional control valves C1, R1 with the unpressurized line T.
  • the directional control valve V1 is switchable to a position in which it Control terminals c1, r1 with the pressure reducing valve Y1 and the control terminals c3, v2 with the non-pressurized line T connects.
  • both pressure-reducing valves Y1, Y2 are closed, the directional control valves C1 to C4 are also blocked.
  • the pressure reducing valve Y1 is opened and the pressure at its controlled port y1 rises, this first leads to the opening of C3 so that pressurized fluid can flow away from the consumer via the consumer side port A and to switch from V2 to its high pressure state.
  • the pressure reducing valve Y2 is opened, this leads to the opening of C2, so that high pressure appears on the consumer side port B.
  • R2 switches, so that this high pressure spreads to the load pressure signaling line LS and controls the operation of the individual pressure compensator C5.
  • a load-independent regulated pressure fluid flow over port B to the consumer, and a complementary current returns from the consumer via port A to the tank.
  • the Fig. 3 shows two control inputs to the directional valves V1, V2, an input v1 and v2, which, as mentioned above, is connected to an output of the respective other directional valve V2 or V1, and an input v1 'or v2', via which Output pressure of each directional valve V1, V2 is returned to it itself.
  • both pressure reducing valves Y1, Y2 are simultaneously opened, the influences of the pressures at these two control ports v1 and v1 'and v2 and v2' cancel each other, and the directional valves V1, V2 remain in the in Fig. 3 shown rest position.
  • valves C3, C4 open valves C1, C2 remain closed.
  • valve assembly of the Fig. 3 To operate a double-acting consumer, which is connected to both consumer-side terminals A, B, there is the ability to independently control two single-acting consumers when the required to switch the directional control valve V1 and V2 control pressure is lower than that for opening the directional valves C1 to C4 required.
  • the control pressure required for switching over the directional control valves V1, V2 can amount to approximately 3 bar, while the directional control valves C1 to C4 only start to open at a control pressure of 5 bar or above and are completely open at a control pressure of approximately 20 bar.
  • Fig. 4 shows a third embodiment of the valve assembly, which differs from that of Fig. 1 by the addition of two hydraulically controlled shuttle valves F1, F2 different.
  • the shuttle valves F1, F2 are respectively connected upstream of the control ports c1, c2 of the directional control valves C1 and C2, controlled by the pressure reducing valve Y2 either with the controlled port y1 of Y1 or with the unpressurized line T or c2 controlled by Y1 with y2 or to connect with the non-pressurized line T.
  • the shuttle valves F1, F2 serve as the directional valves V1, V2 of Fig. 3 to allow opening of both the flow control valves C3, C4 controlling the drain, while at the same time keeping closed the directional control valves C1, C2 controlling the inlet to the consumer, thus bringing about a floating state of the consumer.
  • the shuttle valve F1 controlled via this port connects the control port c1 to y1.
  • the pressure reducing valve Y1 is opened while Y2 is closed, it rises as in the embodiment of Fig. 1 the pressure at the control terminals c1 and c4, and a double-acting consumer connected to the terminals A, B are driven in a first direction.
  • the directional control valves C2, C3 open, and the consumer is driven in the opposite direction.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Multiple-Way Valves (AREA)
  • Valve Housings (AREA)

Claims (12)

  1. Ensemble de valves pour la commande d'au moins un organe utilisateur, comprenant deux raccords côté organe utilisateur (A, B), un raccord de pompe et un raccord de réservoir (P, T), comprenant quatre rampes de distribution (C1-C4) qui sont chacune commandées hydrauliquement par l'intermédiaire d'un raccord de commande et dont une première (C1) relie le raccord de pompe (P) et le premier raccord côté organe utilisateur (A), la seconde (C2) relie le raccord de pompe et le second raccord côté organe utilisateur (B), la troisième (C3) relie le premier raccord côté organe utilisateur (A) et le raccord de réservoir (T), et la quatrième (C4) relie le second raccord côté organe utilisateur (B) et le raccord de pompe (T), comportant une première valve pilote (Y1) et une seconde valve pilote (Y2) pour commander les raccords de commande (c1-c4) de deux des rampes de distribution (C1-C4), caractérisé en ce qu'à la première et à la deuxième rampe de distribution (C1, C2) est associée une première et, respectivement, une seconde valve de commande (F1, F2 ; V1, V2) appartenant à l'ensemble de valves, la première valve de commande (F1, V1) reliant sélectivement un raccord de commande (c1) de la première rampe de distribution (C1) à la première valve pilote (Y1), respectivement au raccord de réservoir (T), et la seconde valve de commande (F2, V2) reliant sélectivement un raccord de commande (c2) de la deuxième rampe de distribution (C2) à la seconde valve pilote (Y2), respectivement au raccord de réservoir (T) afin de permettre une ouverture des deux rampes de distribution (C3, C4) commandant le flux de sortie à partir de l'organe utilisateur, tandis que simultanément les rampes de distribution (C1, C2) commandant le flux d'entrée vers l'organe utilisateur restent fermées et provoquent ainsi un état flottant de l'organe utilisateur, la première valve de commande étant une première valve directionnelle (V1) qui relie sélectivement la première valve pilote (Y1) avec un des raccords de commande (c1, c3) de ses deux rampes de distribution associées, en particulier des première et troisième rampes de distribution (C1, C3), et en ce que la seconde valve de commande est une seconde valve directionnelle (V2) qui relie sélectivement la seconde valve pilote (Y2) avec un des raccords de commande (c2, c4) de ses deux rampes de distribution associées, en particulier des deuxième et quatrième rampes de distribution (C2, C4), ou la première valve de commande (F1, V1) comprenant une première entrée de commande (v1) reliée à la seconde valve pilote (Y2), et la seconde valve de commande (F2, V2) comprenant une première entrée de commande (v1) reliée à la première valve pilote (Y1).
  2. Ensemble de valves selon la revendication 1, caractérisé en ce que les raccords de commande (c1, c4) d'une paire de rampes de distribution, en particulier des première et quatrième rampes de distribution (C1 ; C4), sont reliés en parallèle à une sortie (y1) de la première valve pilote (Y1), et les raccords de commande (c2, c3) d'une autre paire de rampes de distribution, en particulier des deuxième et troisième rampes de distribution (C2 ; C3), sont reliés en parallèle à une sortie (y2) de la seconde valve pilote (Y2).
  3. Ensemble de valves selon la revendication 1, caractérisé en ce qu'une pression de sortie des valves pilotes (Y1, Y2), nécessaire à la commutation des première et seconde valves de commande (V1, V2 ; F1, F2), est inférieure à la pression de sortie nécessaire à l'ouverture des rampes de distribution (C1-C4).
  4. Ensemble de valves selon la revendication 3, caractérisé en ce que les deux valves pilotes (Y1, Y2) sont commandables simultanément.
  5. Ensemble de valves selon la revendication 4, caractérisé en ce que, sur les première et seconde valves de commande (V1, V2), une sortie revient à une seconde entrée de commande (v1', v2'), de sorte que la pression régnant à la sortie s'oppose à la pression appliquée à la première entrée de commande (v1, v2).
  6. Ensemble de valves selon une des revendications précédentes, caractérisé en ce que les valves pilotes (Y1, Y2) sont des réducteurs de pression proportionnels.
  7. Ensemble de valves selon la revendication selon une des revendications précédentes, caractérisé en ce qu'une balance de pression individuelle (C5) commandée par la pression régnant au niveau d'un des raccords côté organe utilisateur est introduite entre le raccord de pompe (P) et la première et seconde rampe de distribution (C1, C2).
  8. Ensemble de valves selon la revendication 7, caractérisé en ce qu'une valve anti-retour déblocable (R1, R2) est prévue entre une entrée de commande de la balance de pression individuelle (C5) et chaque raccord côté organe utilisateur (A, B).
  9. Ensemble de valves selon la revendication 8, caractérisé en ce que les valves anti-retour déblocables (R1, R2) sont chacune déblocables par l'intermédiaire d'une des valves pilotes (Y1, Y2).
  10. Ensemble de valves selon la revendication 8 ou 9, caractérisé en ce que les valves anti-retour déblocables (R1, R2) sont conçues pour, à l'état bloqué, relier le raccord de commande de la balance de pression individuelle (C5) au raccord de réservoir (T).
  11. Ensemble de valves selon une des revendications 7 à 10, caractérisé en ce qu'une valve anti-retour (3) est intégrée à la balance de pression individuelle (C5).
  12. Tracteur comprenant un ensemble de valves selon une des revendications précédentes, caractérisé en ce qu'à l'ensemble de valves peut être relié un équipement réglable ou entraîné hydrauliquement, en particulier une charrue ou un mécanisme de coupe.
EP10188785.9A 2009-11-06 2010-10-26 Bloc de soupape Active EP2320094B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009052257A DE102009052257A1 (de) 2009-11-06 2009-11-06 Ventilbaugruppe

Publications (3)

Publication Number Publication Date
EP2320094A2 EP2320094A2 (fr) 2011-05-11
EP2320094A3 EP2320094A3 (fr) 2014-08-06
EP2320094B1 true EP2320094B1 (fr) 2017-04-19

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EP10188785.9A Active EP2320094B1 (fr) 2009-11-06 2010-10-26 Bloc de soupape

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Country Link
EP (1) EP2320094B1 (fr)
DE (1) DE102009052257A1 (fr)
RU (1) RU2529543C2 (fr)

Cited By (1)

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EP2320094A2 (fr) 2011-05-11
DE102009052257A1 (de) 2011-05-12
EP2320094A3 (fr) 2014-08-06
RU2529543C2 (ru) 2014-09-27

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