EP3759357B1 - Système de soupape pour l'alimentation en fluide sous pression d'un utilisateur hydraulique - Google Patents

Système de soupape pour l'alimentation en fluide sous pression d'un utilisateur hydraulique Download PDF

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Publication number
EP3759357B1
EP3759357B1 EP19718099.5A EP19718099A EP3759357B1 EP 3759357 B1 EP3759357 B1 EP 3759357B1 EP 19718099 A EP19718099 A EP 19718099A EP 3759357 B1 EP3759357 B1 EP 3759357B1
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EP
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Prior art keywords
valve
control valve
control
supply
consumer
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EP19718099.5A
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German (de)
English (en)
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EP3759357A1 (fr
EP3759357C0 (fr
Inventor
Peter Bruck
Marcus Karl Pfeiffer
Christian Stauch
Philippe Vande Kerckhove
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Hydac Mobilhydraulik GmbH
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Hydac Mobilhydraulik GmbH
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    • 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—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
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/86—Control during or prevention of abnormal conditions
    • F15B2211/8609—Control during or prevention of abnormal conditions the abnormal condition being cavitation

Definitions

  • the invention relates to a valve arrangement for supplying pressure medium to a hydraulic consumer with the features in the preamble of claim 1.
  • Load-sensing systems with upstream and downstream individual pressure compensators which are also known in technical terms as LS or LUDV systems, have proven particularly popular as control concepts for such valve arrangements. Furthermore, throttle controls in open-center circuits with constant or demand-adjusted volume flow supply have become established for certain applications.
  • Known valve arrangements often have the property that the throttle cross-sections that determine the inlet and return flow volume of a consumer are changed together by just one control slide.
  • the associated inlet and return control orifices on the control slide must be provided with specially coordinated control edge geometries, which is complex because the geometries mentioned must be individually adapted to each consumer.
  • unintentional Pressure drops at such modified control edges of the valves, which is accompanied by a corresponding power loss.
  • the WO 2016/091528 A1 A hydraulic valve arrangement for supplying pressure medium to a hydraulic consumer has already been proposed, which has two working connections for connection to the consumer, with a first inlet control orifice, via which a first inlet flow from the first of the working connections to the consumer can be controlled, with a second return control orifice separate from this, via which a first return flow from the consumer can be controlled via the second working connection, and with a second inlet control orifice, via which a second inlet flow from the second working connection to the consumer can be controlled, and a first return control orifice separate from this, via which a second return flow from the consumer can be controlled via the first working connection, wherein two separate pilot valves are provided with the proviso that the first return control orifice can be controlled via the first pilot valve to control the second return flow and with the further proviso that the second inlet control orifice can be controlled simultaneously via the first pilot valve and the second pilot valve to control the second inlet flow.
  • the second inlet flow and the second return flow are controlled independently of each other in this way, which can be done essentially automatically using suitable software, the first inlet flow and the first return flow cannot be controlled separately from each other in such arrangements, so that a pressure drop with corresponding power loss can again occur unintentionally at the control edges of the valves used.
  • the EN 10 2012 006 219 A1 a completely different control approach is used, whereby a consumer with two pressure chambers is controlled digitally hydraulically.
  • the digital hydraulic control arrangement used for this assigns an inlet and outlet valve, each designed as a switching valve, to at least one pressure chamber of the consumer, by means of which this one pressure chamber can be shut off or connected to a pressure medium source or to a pressure medium sink.
  • a control unit for controlling the inlet valve and the outlet valve in such a way that a chamber pressure in this one or in another, further pressure chamber of the consumer or a target consumer position can be adjusted by compressing or decompressing the pressure medium in this other pressure chamber by supplying pressure or releasing a pressure medium volume by means of the inlet valve and outlet valve assigned to one pressure chamber.
  • the known control arrangement uses fast-switching 2/2-way valves for this purpose, which can preferably be controlled using ballistic pulse width modulation (PWM).
  • PWM ballistic pulse width modulation
  • the pressure medium supply to the hydraulic consumer can also be carried out digitally in the form of a hydraulic working cylinder or hydrocylinder according to the so-called meter-in-meter-out (MIMO) method.
  • MIMO meter-in-meter-out
  • the document WO 2016/124685 A1 describes a valve arrangement for supplying pressure medium to a hydraulic consumer, which has two working connections (A, B) for fluid connection with the consumer, with a first control valve which has a first inlet via which a first Inflow flow from the first working connection (A) to the consumer can be controlled, and with a first return flow control orifice, via which a first return flow from the consumer can be controlled via the second working connection (B) at the same time as the first inflow, and which has a second inflow, via which a second inflow flow from the second working connection (B) to the consumer can be controlled, and with a second return flow control orifice, via which a second return flow from the consumer can be controlled via the first working connection (A) at the same time as the second inflow, and with a second control valve with an inflow control orifice, with which the respective inflow of the first control valve can be controlled, wherein a third control valve, preferably in the form of a pressure compensator, is connected in a connection
  • the invention is based on the object of further improving the known solutions in such a way that power losses during operation of such valve arrangements for a pressure supply to a hydraulic consumer are avoided in a cost-effective and space-saving manner as well as in a technically reliable manner.
  • the corresponding control edges are implemented in a "dissolved design", i.e. the first control valve specifically controls the return flow of fluid from the consumer via one of the two working connections via the respective return control orifice, whereas the second control valve upstream of the first control valve specifically controls or regulates the inflow flow via an inflow control orifice to the consumer via one of the assignable working connections.
  • the inlet control orifice of the second control valve can be designed as any means for narrowing the flow cross-section in the inlet, for example as a throttle.
  • valve slide of a control valve is designed for a defined operating point in relation to a specific consumer, for example with the proviso that the valve arrangement should be particularly suitable for so-called pushing loads on the consumer, changing load conditions on the consumer, for example in the context of constantly changing or pulling loads, lead to a strong flow throttling, which in turn results in high power losses. This is avoided in a functionally reliable and cost-effective manner with the valve arrangement according to the invention.
  • the valve arrangement according to the invention prevents cavitation from occurring in the inlet chamber of the hydraulic consumer when pulling loads are present, which, in addition to malfunctions, can lead to can also lead to damage to the entire hydraulic system. If there are pressing loads on the consumer, the valve arrangement according to the invention prevents an unnecessary pressure drop at the so-called discharge edge of the control valve, since the "dissolved" control concept with at least two control valves connected in series keeps the pressure drop at the discharge edge of the valve that is connected upstream of the consumer very low, so that no undesirably high pressure drop with corresponding power loss occurs at the discharge edge of this control valve. This has no equivalent in the state of the art.
  • the pressure difference at the subsequent second control valve is regulated via the third control valve, so that an inlet volume flow control is implemented overall, i.e. regardless of the load situation at the consumer, a defined inlet volume flow can always be set in the direction of the second control valve and thus to the hydraulic consumer.
  • the inlet control orifice of the third control valve can be designed as any means for narrowing the flow cross-section in the inlet, for example as a throttle. With a maximum of just three control valves, a separated control edge concept for the hydraulic consumer can be achieved in a space-saving manner with low power loss.
  • the first and/or the second inlet of the first control valve is each designed free of means for narrowing the flow cross-section, in particular free of orifices or throttles.
  • valve arrangement according to the invention is explained in more detail below using an embodiment according to the drawing.
  • the only figure of the application shows the essential components of the valve arrangement with its individual control valves and with an electronic control option (ECU) in a basic and not to scale representation in the form of a hydraulic circuit diagram.
  • ECU electronice control option
  • the valve arrangement shown in the figure serves to supply pressure medium to a hydraulic consumer 10, here in the form of a hydraulic working cylinder, whose piston rod unit 12 divides the cylinder into two working chambers, in the form of a piston chamber 14 and a rod chamber 16.
  • the piston chamber 14 is connected to a working connection A and the rod chamber 16 to a working connection B of the hydraulic valve arrangement.
  • a hydraulic working cylinder another consumer can also be used, for example a hydraulic motor (not shown).
  • a pressure sensor 18 is connected to the fluid connection between the working connection A and the piston chamber 14 and between the working connection B and the rod chamber 16, each of which supplies its measured value results to a central control or computer unit ECU (Electronic Control Unit) for further processing.
  • ECU Electronic Control Unit
  • valve arrangement has a first control valve 20 which, in one of its valve positions 22, controls a first inlet flow from the first working connection A to the consumer 10 via a first inlet 24. Furthermore, in this valve position 22, by means of a first return flow control orifice 26, a first return flow 28 is guided from the consumer 10 via the second working connection B in the direction of the tank T at the same time as the first inlet 24.
  • the first control valve 20 is shown in its locked neutral position 30 and with appropriate actuation of the first control valve 20, it can be brought into a further valve position 32 according to the left switching position as viewed in the direction of the figure.
  • the first control valve 20 has a second inlet 34, via which a second inlet flow from the second working connection B to the consumer 10 can be controlled.
  • a second return flow control orifice 36 via which a second return flow 38 from the consumer 10 via the first working connection A to the tank T can be controlled at the same time as the second inlet 34.
  • the first and second inlets 24, 34 of the first control valve are each designed free of means for narrowing the flow cross-section, in particular without orifices or throttles.
  • valve arrangement has a second control valve 40 with an inlet control orifice 42 with which the respective inlet 24, 34 of the first control valve 20 can be controlled.
  • the first control valve 20 is an electromagnetically actuated 4/4-way proportional valve which, in a fourth valve position 44 (shown on the far right), allows a floating position for the connected consumer 10, i.e. in order to compensate for a pendulum volume, the piston chamber 14 is directly connected to the rod chamber 16 in the fourth valve position 44, with further control fluid being able to be supplied from the second control valve 40.
  • a return connection 46 connected to the inlet side of the first control valve 20 with a connecting line 47 to the tank T is blocked in this case. Since the floating position or valve position 44 mentioned is not absolutely necessary, the valve arrangement according to the invention can also be implemented using an electromagnetically actuated 3/4-way proportional valve without this function.
  • the first control valve 20 is held in its neutral position 30 in the de-energized state by means of two opposing compression springs.
  • a proportional magnet acts on the valve on opposite control sides, which can be controlled, i.e. energized, by the central control unit ECU.
  • the output side of the first control valve 20 is connected to the two working connections A, B in a fluid-carrying manner, on the input side, in addition to the connecting line 47 leading to the first control valve 20, another connecting line 48 is provided which leads to the output of the second control valve 40.
  • the second control valve 40 is in turn formed from an electromagnetically actuated 2/2-way proportional valve and in its actuated position the inlet control orifice 42 is activated. In its non-actuated position, shown in the figure, however, a possible backflow from the first 24 and the second 34 inlet of the first control valve 20 is prevented by a check valve 49 integrated in the second control valve 40, which in its closed position prevents the corresponding backflow from the outlet of the second control valve 40 in the direction of its fluid inlet.
  • the blocking of the corresponding return medium is preferably carried out by means of the check valve 49 in a seat-tight manner.
  • the second control valve 40 is also held in its locked position shown when de-energized by a compression spring and only when appropriate current is applied, triggered by the central control unit ECU, is the inflow controlled or regulated via the inflow control orifice 42 from the inlet side of the second control valve 40 to its outlet via the proportional magnet arranged opposite the compression spring.
  • proportional magnets for the first or second control valve 20 or 40 barometric pilot controls with pilot pressure regulators can be used, particularly with relatively large fluid cross-sections.
  • valve arrangement has a third control valve 50, designed in the form of a pressure compensator, which is connected between a pressure supply P and the second control valve 40.
  • the third control valve 50 is designed as a 2/2-way pressure compensator and in its neutral position shown, the inflow between a pressure supply P and the second control valve 40 is controlled with its inflow control orifice 52. In the other position of this pressure compensator 50, the inflow in question is blocked.
  • a load sensing pressure LS acts, which is taken from the connecting line 48 between the first 20 and the second 40 control valve.
  • a control pressure is present, which is taken from a connecting line 54 between the second 40 and the third control valve 50.
  • the output of the third control valve 50 is therefore permanently connected to the input side of the second control valve 40 via the line 54.
  • the load sensing pressure LS acts on the control side of the third valve 50, this action is supported by a compression spring on the third control valve 50.
  • the load sensing pressure LS originating from the connecting line 48 can be passed on to other valve sections (not shown) via a connection point 56 if necessary.
  • the load sensing pressure LS is available at an interface 58 of the valve unit 60, consisting of the first, second and third control valves 20, 40 and 50.
  • a load sensing pressure LS for example, a swivel angle pump 62 serving the pressure supply P can be controlled, which, however, in the case shown here is controlled exclusively electrically by the central control unit ECU.
  • control or computer unit ECU shown can, as shown with arrows, receive operating commands on the input side and control additional valve sections on the output side that are not shown in detail.
  • a resolution of control edges is realized via a first control valve 20 and a second control valve 40, wherein the first control valve 20 has the respective return control orifices 26 and 36 for controlling the return from the consumer 10 and the second control valve 40 has the inlet control orifice 42 for controlling the inlet to the first control valve 20 and thus to the consumer 10.
  • a third control valve 50 within the valve unit 60 which is exchangeable as a whole and is also available as a retrofit kit, is designed in the manner of a pressure compensator and allows overall inlet volume flow control for the consumer 10.

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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)

Claims (7)

  1. Système de soupape pour l'alimentation en fluide sous pression d'un utilisateur hydraulique, qui a deux raccords (A, B) de travail pour la communication fluidique avec l'utilisateur,
    comprenant une première soupape de commande,
    - qui a une première arrivée (24), en passant par laquelle un premier courant d'arrivée du premier raccord (A) de travail à l'utilisateur (10) peut être commandé, et comprenant un premier diaphragme (26) de commande de retour, en passant par lequel, en même temps que la première arrivée (24), un premier courant (28) de retour de l'utilisateur (10) peut être commandé en passant par le deuxième raccord (B) de travail ; et
    - qui a une deuxième arrivée (34), en passant par laquelle un deuxième courant d'arrivée du deuxième raccord (B) de travail à l'utilisateur (10) peut être commandé, et comprenant un deuxième diaphragme (36) de commande de retour, en passant par lequel, en même que la deuxième arrivée (34), un deuxième courant (38) de retour de l'utilisateur (10) peut être commandé en passant par le premier raccord (A) de travail ; et
    comprenant une deuxième soupape (40) de commande ayant un diaphragme (42) de commande d'arrivée, par lequel l'arrivée (24, 34) respective de la première soupape (20) de commande peut être commandée,
    dans lequel une troisième soupape (50) de commande, sous la forme d'une balance manométrique, est montée dans une liaison entre une alimentation (P) en pression et la deuxième soupape (40) de commande,
    dans lequel la troisième soupape (50) de commande, sous la forme d'une balance manométrique à 2/2 voies, commande dans l'une de ses positions par son diaphragme (52) de commande d'arrivée, une arrivée entre l'alimentation (P) en pression et la deuxième soupape (40) de commande et dans une autre position bloque cette arrivée, et
    dans lequel, tourné vers sa position de blocage, applique une pression de commande, qui est prélevée d'un conduit (54) de liaison entre la deuxième (40) et la troisième (50) soupape de commande,
    caractérisé
    en ce que, tourné vers son côté de commande opposé à son diaphragme (52) de commande d'arrivée, attaque au moins une pression load sensing (LS), qui est prélevée d'un conduit (48) de liaison entre la première (20) et la deuxième (40) soupapes de commande, et
    en ce que la deuxième soupape (40) de commande empêche, dans sa position inactivée, un courant de retour éventuel provenant de la première (24) et de la deuxième (34) arrivées de la première soupape (20) de commande par un clapet antiretour (49) intégré dans la deuxième soupape (40) de commande, qui, dans sa position de fermeture, empêche le retour de la sortie de la deuxième soupape (40) de commande en direction de son entrée de fluide.
  2. Système de soupape suivant la revendication 1, caractérisé en ce que la première (24) et/ou la deuxième (34) arrivées de la première soupape de commande sont chacune sans moyen de rétrécissement de la section transversale d'écoulement, en particulier sans diaphragme ou sans étranglement.
  3. Système de soupape suivant la revendication 1 ou 2, caractérisé en ce que la première soupape (20) de commande est une vanne proportionnelle à 3/4 voies pouvant être actionnée par des régleurs de pression pilotes, de préférence une soupape proportionnelle à 4/4 voies, qui, dans une position (44) de la soupape, autorise une position flottante pour l'utilisateur (10) raccordé.
  4. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que la deuxième soupape (40) de commande est une vanne proportionnelle à 2/2 voies pouvant être actionnée par un régleur de pression pilote, et en ce que, dans une position actionnée, le diaphragme (42) de commande d'arrivée est activé et, dans une position inactionnée, empêche un courant de retour, provenant de la première (24) et de la deuxième (34) arrivées de la première soupape (20) de commande.
  5. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que la pression de fluide en cours pour les deux raccords (A, B) d'utilisateur est prélevée au moyen d'un dispositif (18) de valeur de mesure et est acheminée à une unité (ECU) centrale de commande ou de calcul, qui provoque l'actionnement de la première (20) et de la deuxième (40) soupapes de commande et qui commande l'alimentation (P) en pression pourvue d'une pompe (62) à angle de pivotement.
  6. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que la première soupape (20) de commande est raccordée, du côté de l'entrée, à la deuxième soupape (40) de commande, ainsi qu'à, du côté de l'entrée, un raccord (46) de retour menant, de préférence au réservoir (T).
  7. Système de soupape suivant l'une des revendications précédentes, caractérisé en ce que l'utilisateur (10) hydraulique pouvant être raccordé est un vérin de travail hydraulique à surfaces de tige et piston différentes ou un moteur hydraulique.
EP19718099.5A 2018-05-07 2019-04-09 Système de soupape pour l'alimentation en fluide sous pression d'un utilisateur hydraulique Active EP3759357B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018003728.3A DE102018003728A1 (de) 2018-05-07 2018-05-07 Ventilanordnung zur Druckmittelversorgung eines hydraulischen Verbrauchers
PCT/EP2019/058885 WO2019214887A1 (fr) 2018-05-07 2019-04-09 Système de soupape pour l'alimentation en fluide sous pression d'un utilisateur hydraulique

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CN112714831B (zh) * 2018-06-13 2023-07-14 派克汉尼汾(欧洲、中东和非洲)公司 液压阀装置
DE102021108081B4 (de) 2021-03-30 2023-02-02 Andreas Lupold Hydrotechnik Gmbh Vorrichtung zum Regeln einer Hydraulikpumpe oder eines Hydraulikmotors
CN113833701A (zh) * 2021-09-07 2021-12-24 徐州徐工挖掘机械有限公司 一种旋转机具液压系统
CN114165495B (zh) * 2021-11-23 2022-10-18 江苏汇智高端工程机械创新中心有限公司 工作联、阀口独立控制型多路阀及工程机械
DE102022111288A1 (de) 2022-05-06 2023-11-09 Jungheinrich Aktiengesellschaft Hydrauliksystem für ein Flurförderzeug und Flurförderzeug
IT202200026805A1 (it) * 2022-12-23 2024-06-23 Cnh Ind Italia Spa Veicolo sollevatore telescopico

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US11168713B2 (en) 2021-11-09
US20210062832A1 (en) 2021-03-04
EP3759357A1 (fr) 2021-01-06
EP3759357C0 (fr) 2024-06-05
DE102018003728A1 (de) 2019-11-07
WO2019214887A1 (fr) 2019-11-14

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