EP3759357B1 - Valve arrangement for supplying a hydraulic consumer with pressure medium - Google Patents

Valve arrangement for supplying a hydraulic consumer with pressure medium 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
European Patent Office
Prior art keywords
valve
control valve
control
supply
consumer
Prior art date
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Application number
EP19718099.5A
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German (de)
French (fr)
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EP3759357A1 (en
EP3759357C0 (en
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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Publication of EP3759357B1 publication Critical patent/EP3759357B1/en
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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
    • 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)

Description

Die Erfindung betrifft eine Ventilanordnung zur Druckmittelversorgung eines hydraulischen Verbrauchers mit den Merkmalen im Oberbegriff von Anspruch 1.The invention relates to a valve arrangement for supplying pressure medium to a hydraulic consumer with the features in the preamble of claim 1.

Als Steuerkonzepte für solche Ventilanordnungen haben sich insbesondere Load-Sensing-Systeme mit vor- und nachgeschalteten Individualdruckwaagen hervorgetan, die man fachsprachlich auch als LS- bzw. LUDV-Systeme bezeichnet. Ferner haben sich für bestimmte Anwendungen Drosselsteuerungen in Open-Center-Kreisläufen mit konstanter oder bedarfsangepasster Volumenstromversorgung durchgesetzt.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.

Bekannte Ventilanordnungen haben häufig die Eigenschaft, dass den Zu- und Rücklaufvolumenstrom eines Verbrauchers bestimmende Drosselquerschnitte gemeinsam durch nur einen Steuerschieber verändert werden. Um im Betrieb der bekannten Ventilanordnung, beispielsweise bei Verwendung in mobilen Arbeitsmaschinen, unter allen Umständen Kavitation in Zulauf oder Rücklauf zu vermeiden, müssen die zugeordneten Zu- und Rücklaufsteuerblenden am Steuerschieber mit speziell aufeinander abgestimmten Steuerkantengeometrien versehen sein, was aufwändig ist, da die genannten Geometrien an jeden Verbraucher individuell angepasst werden müssen. Auch kommt es im Betrieb derartiger Ventilanordnungen ungewollt zu Druckabfällen an solchen modifizierten Steuerkanten der Ventile, was mit einer entsprechenden Verlustleistung einhergeht.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. In order to avoid cavitation in the inlet or return flow under all circumstances during operation of the known valve arrangement, for example when used in mobile work machines, 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. In addition, unintentional Pressure drops at such modified control edges of the valves, which is accompanied by a corresponding power loss.

Um diesen Nachteilen zu begegnen, ist in der WO 2016/091528 A1 bereits eine hydraulische Ventilanordnung zur Druckmittelversorgung eines hydraulischen Verbrauchers vorgeschlagen worden, die zwei Arbeitsanschlüsse zur Verbindung mit dem Verbraucher hat, mit einer ersten Zulaufsteuerblende, über die ein erster Zulaufstrom vom ersten der Arbeitsanschlüsse hin zum Verbraucher steuerbar ist, mit einer davon gesonderten zweiten Rücklaufsteuerblende, über die ein erster Rücklaufstrom vom Verbraucher über den zweiten Arbeitsanschluss steuerbar ist, und mit einer zweiten Zulaufsteuerblende, über die ein zweiter Zulaufstrom vom zweiten Arbeitsanschluss hin zum Verbraucher steuerbar ist, und einer davon gesonderten ersten Rücklaufsteuerblende, über die ein zweiter Rücklaufstrom vom Verbraucher über den ersten Arbeitsanschluss steuerbar ist, wobei zwei gesonderte Vorsteuerventile vorgesehen sind mit der Maßgabe, dass die erste Rücklaufsteuerblende zur Steuerung des zweiten Rücklaufstroms über das erste Vorsteuerventil steuerbar ist und mit der weiteren Maßgabe, dass die zweite Zulaufsteuerblende zur Steuerung des zweiten Zulaufstroms gleichzeitig über das erste Vorsteuerventil und das zweite Vorsteuerventil steuerbar ist.To counteract these disadvantages, 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.

Obwohl dergestalt der zweite Zulaufstrom und der zweite Rücklaufstrom voneinander unabhängig gesteuert werden, was unter Einsatz geeigneter Software im Wesentlichen automatisch erfolgen kann, sind jedenfalls der erste Zulaufstrom und der erste Rücklaufstrom bei dahingehenden Anordnungen nicht getrennt voneinander steuerbar, so dass es wiederum an den Steuerkanten der eingesetzten Ventile ungewollt zu einem Druckabfall mit entsprechender Verlustleistung kommen kann.Although 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.

Demgegenüber liegt der DE 10 2012 006 219 A1 ein völlig anderer Steueransatz zugrunde, indem ein Verbraucher mit zwei Druckräumen digitalhydraulisch angesteuert wird. Die hierfür eingesetzte digitalhydraulische Steueranordnung ordnet dabei zumindest einem Druckraum des Verbrauchers ein jeweils als Schaltventil ausgebildetes Einlass- und Auslassventil zu, mittels deren dieser eine Druckraum absperrbar oder mit einer Druckmittelquelle oder mit einer Druckmittelsenke verbindbar ist. Ferner ist eine Steuereinheit vorgesehen zum Ansteuern des Einlassventils und des Auslassventils derart, dass ein Kammerdruck in diesem einen oder in einem anderen, weiteren Druckraum des Verbrauchers oder eine Soll-Verbraucherposition durch Kompression oder Dekompression des Druckmittels in diesem anderen Druckraum durch Druckzufuhr oder Ablassen eines Druckmittelvolumens mittels des dem einen Druckraum zugeordneten Einlassventils und Auslassventils einstellbar ist. Die bekannte Steueranordnung setzt hierfür schnellschaltende 2/2-Wege-Ventile ein, die vorzugsweise unter Einsatz einer ballistischen Pulsweitenmodulation (PWM) steuerbar sind. Auch dergestalt lässt sich die Druckmittelversorgung des hydraulischen Verbrauchers regelmäßig in Form eines hydraulischen Arbeitszylinders oder Hydrozylinders nach dem sogenannten Meter-In-Meter-Out-(MIMO)-Verfahren in digitaler Weise durchführen.In contrast, 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. Furthermore, a control unit is provided 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). In this way, 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.

Nachteile bei dieser bekannten Lösung könnten darin gesehen werden, dass für die Ansteuerung der Vielzahl von Schaltventilen mittels Pulsweitenmodulation ein erhöhter Steuerungsaufwand erforderlich ist und die heute zur Verfügung stehenden Schaltventile bei kostengünstiger Auslegung regelmäßig nicht derart schnell betätigbar sind, um die Steuerungsaufgabe für die Druckmittelversorgung zufriedenstellend erfüllen zu können.Disadvantages of this known solution could be seen in the fact that an increased control effort is required for the control of the large number of switching valves by means of pulse width modulation and the switching valves available today, even with a cost-effective design, cannot usually be actuated quickly enough to satisfactorily fulfill the control task for the pressure medium supply.

Das Dokument WO 2016/124685 A1 beschreibt eine Ventilanordnung zur Druckmittelversorgung eines hydraulischen Verbrauchers, die zwei Arbeitsanschlüsse (A, B) zur Fluidverbindung mit dem Verbraucher hat, mit einem ersten Steuerventil, das einen ersten Zulauf aufweist, über den ein erster Zulaufstrom vom ersten Arbeitsanschluss (A) zum Verbraucher steuerbar ist, und mit einer ersten Rücklaufsteuerblende, über die gleichzeitig mit dem ersten Zulauf ein erster Rücklaufstrom vom Verbraucher über den zweiten Arbeitsanschluss (B) steuerbar ist, und das einen zweiten Zulauf aufweist, über den ein zweiter Zulaufstrom vom zweiten Arbeitsanschluss (B) zum Verbraucher steuerbar ist, und mit einer zweiten Rücklaufsteuerblende, über die gleichzeitig mit dem zweiten Zulauf ein zweiter Rücklaufstrom vom Verbraucher über den ersten Arbeitsanschluss (A) steuerbar ist und mit einem zweiten Steuerventil mit einer Zulaufsteuerblende, mit der der jeweilige Zulauf des ersten Steuerventils steuerbar ist, wobei ein drittes Steuerventil, vorzugsweise in Form einer Druckwaage, in eine Verbindung zwischen einer Druckversorgung (P) und dem zweiten Steuerventil geschaltet ist, wobei das dritte Steuerventil als 2/2-Wege-Druckwaage in einer seiner Stellungen mit seiner Zulaufsteuerblende einen Zulauf zwischen der Druckversorgung (P) und dem zweiten Steuerventil steuert und in einer anderen Stellung diesen Zulauf sperrt, wobei seiner Sperrstellung zugewandt, ein Steuerdruck anliegt, der einer Verbindungsleitung zwischen dem zweiten und dem dritten Steuerventil entnommen ist.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 between a pressure supply (P) and the second control valve, wherein the third control valve as a 2/2-way pressure compensator controls an inflow between the pressure supply (P) and the second control valve in one of its positions with its inflow control orifice and blocks this inflow in another position, wherein facing its blocking position, a Control pressure is applied which is taken from a connecting line between the second and the third control valve.

Weitere Ventilanordnungen gehen aus der EP 1 076 183 A1 , der EP 1 281 872 A1 und der DE 10 2009 047 035 A1 hervor.Further valve arrangements are available from the EP 1 076 183 A1 , the EP 1 281 872 A1 and the EN 10 2009 047 035 A1 out.

Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, die bekannten Lösungen dahingehend weiter zu verbessern, dass in kostengünstiger Weise und bauraumsparend sowie technisch verlässlich Verlustleistungen im Betrieb solcher Ventilanordnungen für eine Druckversorgung eines hydraulischen Verbrauchers vermieden sind.Based on this state of the art, 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.

Eine dahingehende Aufgabe löst eine Ventilanordnung mit den Merkmalen des Patentanspruchs 1.A valve arrangement having the features of patent claim 1 solves this problem.

Die erfindungsgemäße Ventilanordnung zur Druckmittelversorgung eines hydraulischen Verbrauchers, die zwei Arbeitsanschlüsse zur Fluidverbindung mit dem Verbraucher hat, weist

  • ein erstes Steuerventil,
    • das einen ersten Zulauf aufweist, über den ein erster Zulaufstrom vom ersten Arbeitsanschluss zum Verbraucher steuerbar ist, und mit einer ersten Rücklaufsteuerblende, über die gleichzeitig mit dem ersten Zulauf ein erster Rücklaufstrom vom Verbraucher über den zweiten Arbeitsanschluss steuerbar ist; und
    • das einen zweiten Zulauf aufweist, über den ein zweiter Zulaufstrom vom zweiten Arbeitsanschluss zum Verbraucher steuerbar ist, und mit einer zweiten Rücklaufsteuerblende, über die gleichzeitig mit dem zweiten Zulauf ein zweiter Rücklaufstrom vom Verbraucher über den ersten Arbeitsanschluss steuerbar ist, und
  • ein zweites Steuerventil mit einer Zulaufsteuerblende auf, mit der der jeweilige Zulauf des ersten Steuerventils steuerbar ist, wobei ein drittes Steuerventil in Form einer Druckwaage in eineVerbindung zwischen einer Druckversorgung (P) und dem zweiten Steuerventil geschaltet ist, wobei das dritte Steuerventil als 2/2-Wege-Druckwaage in einer seiner Stellungen mit seiner Zulaufsteuerblende einen Zulauf zwischen der Druckversorgung (P) und dem zweiten Steuerventil steuert und in einer anderen Stellung diesen Zulauf sperrt, wobei auf seinen gegenüberliegenden Steuerseiten seiner Zulaufsteuerblende zugewandt zumindest ein Load-Sensing (LS)-Druck angreift, der einer Verbindungsleitung zwischen dem ersten und dem zweiten Steuerventil entnommen ist und, seiner Sperrstellung zugewandt, ein Steuerdruck anliegt, der einer Verbindungsleitung zwischen dem zweiten und dem dritten Steuerventil entnommen ist, und wobei das zweite Steuerventil in seiner unbetätigten Stellung einen möglichen, von dem ersten und dem zweiten Zulauf des ersten Steuerventils stammenden Rückstrom durch ein in das zweite Steuerventil integriertes Rückschlagventil verhindert, das in seiner Schließstellung den Rücklauf vom Ausgang des zweiten Steuerventiles in Richtung seines Fluideingangs verhindert.
The valve arrangement according to the invention for supplying pressure medium to a hydraulic consumer, which has two working connections for fluid connection with the consumer, has
  • a first control valve,
    • which has a first inlet via which a first inlet flow from the first working connection to the consumer can be controlled, and with a first return flow control orifice via which a first return flow from the consumer via the second working connection can be controlled simultaneously with the first inlet; and
    • which has a second inlet via which a second inlet flow from the second working connection to the consumer can be controlled, and with a second return flow control orifice via which a second return flow from the consumer via the first working connection can be controlled simultaneously with the second inlet, and
  • a second control valve with an inlet control orifice with which the respective inlet of the first control valve can be controlled, wherein a third control valve in the form of a pressure compensator is connected in a connection between a pressure supply (P) and the second control valve, wherein the third control valve as a 2/2-way pressure compensator in one of its positions controls an inlet between the pressure supply (P) and the second control valve with its inlet control orifice and in another position blocks this inlet, wherein on its opposite control sides facing its inlet control orifice at least one load sensing (LS) pressure acts, which is taken from a connecting line between the first and the second control valve and, facing its blocking position, a control pressure is applied, which is taken from a connecting line between the second and the third control valve, and wherein the second control valve in its unactuated position controls a possible backflow originating from the first and the second inlet of the first control valve by a check valve integrated in the second control valve, which in its closed position prevents the backflow from the outlet of the second control valve towards its fluid inlet.

Im Gegensatz zu Lösungen im Stand der Technik, bei denen die sog. Zu- und Ablaufkanten eines Steuerventils im Steuerschieber fest miteinander gekoppelt sind, sind bei der erfindungsgemäßen Ventilanordnung die entsprechenden Steuerkanten in "aufgelöster Bauweise" realisiert, d.h. das erste Steuerventil steuert gezielt über die jeweilige Rücklaufsteuerblende den Rücklauf von Fluid aus dem Verbraucher über jeweils einen der beiden Arbeitsanschlüsse, wohingegen das dem ersten Steuerventil vorgeschaltete, zweite Steuerventil den Zulaufstrom gezielt über eine Zulaufsteuerblende zum Verbraucher über einen der zuordenbaren Arbeitsanschlüsse steuert respektive regelt.In contrast to solutions in the prior art, in which the so-called inlet and outlet edges of a control valve in the control slide are firmly coupled to one another, in the valve arrangement according to the invention 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.

Die Zulaufsteuerblende des zweiten Steuerventils kann als ein beliebiges Mittel zur Verengung des Strömungsquerschnitts im Zulauf ausgebildet sein, beispielsweise als eine Drossel.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.

Während bei den bekannten Lösungen der Ventilschieber eines Steuerventils bezogen auf einen bestimmten Verbraucher auf einen definierten Arbeitspunkt ausgelegt ist, beispielsweise mit der Maßgabe, dass die Ventilanordnung besonders für sogenannte drückende Lasten am Verbraucher geeignet sein soll, kommt es bei sich ändernden Lastverhältnissen am Verbraucher, beispielsweise im Rahmen von ständig wechselnden oder ziehenden Lasten, zu einer starken Ablaufdrosselung, was wiederum hohe Verlustleistungen mit sich bringt. Dies ist mit der erfindungsgemäßen Ventilanordnung in funktionssicherer und kostengünstiger Weise vermieden.While in the known solutions the 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.

Insbesondere ist mit der erfindungsgemäßen Ventilanordnung vermieden, dass bei ziehenden Lasten in einer Zulaufkammer des hydraulischen Verbrauchers Kavitation entsteht, was neben Funktionsstörungen langfristig auch zu Beschädigungen an der gesamthydraulischen Anlage führen kann. Kommt es am Verbraucher zu drückenden Lasten, ist mit der erfindungsgemäßen Ventilanordnung vermieden, dass ein unnötiger Druckabfall an der sog. Ablaufkante des Steuerventils entsteht, da durch das "aufgelöste" Steuerungskonzept mit zumindest zwei hintereinander geschalteten Steuerventilen der Druckabfall an der Ablaufkante des Ventils, das dem Verbraucher vorgeschaltet ist sehr gering gehalten wird, so dass kein unerwünscht hoher Druckabfall mit entsprechender Verlustleistung an der Ablaufkante dieses Steuerventils entsteht. Dies hat so keine Entsprechung im Stand der Technik.In particular, 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.

Über das dritte Steuerventil ist die Druckdifferenz an dem nachfolgenden zweiten Steuerventil geregelt, so dass insgesamt eine Zulaufvolumenstromregelung realisiert ist, d.h. unabhängig von der Lastsituation am Verbraucher ist immer ein definierter Zulaufvolumenstrom in Richtung des zweiten Steuerventils und mithin zu dem hydraulischen Verbraucher einstellbar. Die Zulaufsteuerblende des dritten Steuerventils kann als ein beliebiges Mittel zur Verengung des Strömungsquerschnitts im Zulauf ausgebildet sein, beispielsweise als Drossel.Mit nur maximal drei Steuerventilen lässt sich in bauraumsparender Weise ein aufgelöstes Steuerkantenkonzept für den hydraulischen Verbraucher erreichen bei geringer Verlustleistung.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.

Bei einer besonders bevorzugten Ausführungsform der erfindungsgemäßen Ventilanordnung ist der erste und/oder der zweite Zulauf des ersten Steuerventils jeweils frei von Mitteln zur Verengung des Strömungsquerschnitts, insbesondere blenden- oder drosselfrei, ausgebildet.In a particularly preferred embodiment of the valve arrangement according to the invention, 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.

Vorteilhafte Ausführungsformen der erfindungsgemäßen Ventilanordnung sind Gegenstand der Unteransprüche 2 bis 7.Advantageous embodiments of the valve arrangement according to the invention are the subject of subclaims 2 to 7.

Im Folgenden wird die erfindungsgemäße Ventilanordnung anhand eines Ausführungsbeispiels nach der Zeichnung näher erläutert. Dabei zeigt in prinzipieller und nicht maßstäblicher Darstellung die einzige Figur der Anmeldung in der Art eines hydraulischen Schaltplans die wesentlichen Komponenten der Ventilanordnung mit ihren einzelnen Steuerventilen und mit einer elektronischen Ansteuermöglichkeit (ECU).The 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.

Die in der Figur gezeigte Ventilanordnung dient der Druckmittelversorgung eines hydraulischen Verbrauchers 10, hier in Form eines hydraulischen Arbeitszylinders, dessen Kolbenstangeneinheit 12 den Zylinder in zwei Arbeitsräume unterteilt, in Form eines Kolbenraumes 14 und eines Stangenraumes 16. Der Kolbenraum 14 ist an einem Arbeitsanschluss A und der Stangenraum 16 an einen Arbeitsanschluss B der hydraulischen Ventilanordnung angeschlossen. Anstelle eines hydraulischen Arbeitszylinders kann auch ein anderer Verbraucher treten, beispielsweise ein Hydromotor (nicht dargestellt). In die Fluidverbindung zwischen dem Arbeitsanschluss A und dem Kolbenraum 14 sowie dem Arbeitsanschluss B und dem Stangenraum 16 ist jeweils ein Druckmesswertaufnehmer 18 geschaltet, der jeweils seine Messwertergebnisse an eine zentrale Steuer- oder Rechnereinheit ECU (Electronic Control Unit) zur weiteren Verarbeitung liefert.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. Instead of 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.

Ferner weist die Ventilanordnung ein erstes Steuerventil 20 auf, das in einer seiner Ventilstellungen 22, über einen ersten Zulauf 24 einen ersten Zulaufstrom vom ersten Arbeitsanschluss A zum Verbraucher 10 steuert. Ferner ist in dieser Ventilstellung 22 mittels einer ersten Rücklaufsteuerblende 26 gleichzeitig mit dem ersten Zulauf 24 ein erster Rücklaufstrom 28 vom Verbraucher 10 über den zweiten Arbeitsanschluss B in Richtung Tank T geführt.Furthermore, the 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.

In der Figur ist das erste Steuerventil 20 in seiner gesperrten Neutralstellung 30 gezeigt und bei entsprechender Betätigung des ersten Steuerventils 20 ist dieses in eine weitere Ventilstellung 32 gemäß der in Blickrichtung auf die Figur gesehen linken Schaltstellung bringbar. In dieser dritten Ventilstellung 32 weist das erste Steuerventil 20 einen zweiten Zulauf 34 auf, über den ein zweiter Zulaufstrom vom zweiten Arbeitsanschluss B zum Verbraucher 10 steuerbar ist. Ferner ist eine zweite Rücklaufsteuerblende 36 vorhanden, über die gleichzeitig mit dem zweiten Zulauf 34 ein zweiter Rücklaufstrom 38 vom Verbraucher 10 über den ersten Arbeitsanschluss A zum Tank T hin steuerbar ist.In the figure, 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. In this third valve position 32, 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. Furthermore, there is 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.

Der erste und der zweite Zulauf 24, 34 des ersten Steuerventils sind jeweils frei von Mitteln zur Verengung des Strömungsquerschnitts, insbesondere blenden- oder drosselfrei, ausgebildet.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.

Des Weiteren weist die Ventilanordnung ein zweites Steuerventil 40 auf, mit einer Zulaufsteuerblende 42 mit der der jeweilige Zulauf 24, 34 des ersten Steuerventiles 20 steuerbar ist.Furthermore, the 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.

Das erste Steuerventil 20 ist ein elektromagnetisch betätigbares 4/4-Wege-Proportionalventil, das in einer vierten Ventilposition 44 (ganz rechts dargestellt) eine Schwimmstellung für den angeschlossenen Verbraucher 10 erlaubt, d.h. zum Ausgleich eines Pendelvolumens werden in der vierten Ventilposition 44 der Kolbenraum 14 mit dem Stangenraum 16 direkt verbunden, wobei von Seiten des zweiten Steuerventils 40 weiter Steuerfluid nachführbar ist. Ein an das erste Steuerventil 20 eingangsseitig angeschlossener Rücklaufanschluss 46 mit Verbindungsleitung 47 zum Tank T ist dabei gesperrt. Da die angesprochene Schwimmstellung respektive die Ventilposition 44 nicht zwingend notwendig ist, lässt sich die erfindungsgemäße Ventilanordnung unter Weglassen dieser Funktion auch mittels eines elektromagnetisch betätigbaren 3/4-Wege-Porportionalventils ausführen.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.

Das erste Steuerventil 20 ist, wie üblich und in dargestellter Weise im unbestromten Zustand mittels zweier, gegenüberliegender Druckfedern in seiner Neutralstellung 30 gehalten. In Wirkrichtung parallel zu der jeweiligen Druckfeder greift an dem Ventil auf gegenüberliegenden Steuerseiten ein Proportionalmagnet an, der jeweils von der zentralen Steuereinheit ECU ansteuerbar, sprich bestrombar, ist. Während die Ausgangseite des ersten Steuerventiles 20 fluidführend an die beiden Arbeitsanschlüsse A, B angeschlossen ist, ist eingangsseitig neben der Verbindungsleitung 47 zu dem ersten Steuerventil 20 führend noch eine weitere Verbindungsleitung 48 vorgesehen, die zum Ausgang des zweiten Steuerventiles 40 führt.As usual and as shown, the first control valve 20 is held in its neutral position 30 in the de-energized state by means of two opposing compression springs. In the direction of action parallel to the respective compression spring, a proportional magnet acts on the valve on opposite control sides, which can be controlled, i.e. energized, by the central control unit ECU. While 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.

Das zweite Steuerventil 40 ist wiederum aus einem elektromagnetisch betätigbaren 2/2-Wege-Proportionalventil gebildet und in seiner betätigten Stellung ist die Zulaufsteuerblende 42 aktiviert. In seiner unbetätigten, in der Fig. gezeigten Stellung wird jedoch ein möglicher Rückstrom von dem ersten 24 und dem zweiten 34 Zulauf des ersten Steuerventils 20 stammend, verhindert, und zwar über ein im zweiten Steuerventil 40 integriertes Rückschlagventil 49, das in seiner Schließstellung den dahingehenden Rücklauf vom Ausgang des zweiten Steuerventiles 40 in Richtung seines Fluideingangs verhindert. Vorzugsweise erfolgt das Sperren des dahingehenden Rücklaufmittels mittels des Rückschlagventils 49 in sitzdichter Weise. Auch wird wiederum das zweite Steuerventil 40 unbestromt über eine Druckfeder in seiner gezeigten gesperrten Position gehalten und erst bei entsprechender Bestromung, ausgelöst von der zentralen Steuereinheit ECU, wird über den der Druckfeder gegenüberliegend angeordneten Proportionalmagneten der Zulauf über die Zulaufsteuerblende 42 von der Eingangsseite des zweiten Steuerventils 40 zu seinem Ausgang hin gesteuert respektive geregelt. Anstelle der genannten Proportionalmagneten für das erste oder zweite Steuerventil 20 bzw. 40 lassen sich, insbesondere bei relativ groß dimensionierten Fluidquerschnitten, besonders bevorzugt barometrische Vorsteuerungen mit Vorsteuer-Druckreglern einsetzen.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. Instead of the aforementioned 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.

Des Weiteren weist die Ventilanordnung ein drittes Steuerventil 50 auf, in Form einer Druckwaage ausgebildet, die in eine Verbindung zwischen einer Druckversorgung P und dem zweiten Steuerventil 40 geschaltet ist. Das dritte Steuerventil 50 ist als 2/2-Wege-Druckwaage ausgestaltet und in seiner gezeigten Neutralstellung wird mit seiner Zulaufsteuerblende 52 der Zulauf zwischen einer Druckversorgung P und dem zweiten Steuerventil 40 gesteuert. In der anderen Stellung dieser Druckwaage 50 ist der dahingehende Zulauf gesperrt.Furthermore, the 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.

Auf seiner der Zulaufsteuerblende 52 zugewandten Steuerseite greift ein Loadsensing-Druck LS an, der der Verbindungsleitung 48 zwischen dem ersten 20 und dem zweiten 40 Steuerventil entnommen ist. Auf seiner der Sperrstellung zugewandten Steuerseite liegt ein Steuerdruck an, der einer Verbindungsleitung 54 zwischen dem zweiten 40 und dem dritten Steuerventil 50 entnommen ist. Mithin ist der Ausgang des dritten Steuerventiles 50 über die Leitung 54 auf die Eingangsseite des zweiten Steuerventils 40 permanent fluidführend angeschlossen. Auf der Seite, wo der Loadsensing-Druck LS an der Steuerseite des dritten Ventiles 50 angreift, wird der dahingehende Angriff von einer Druckfeder am dritten Steuerventil 50 mit unterstützt. Der von der Verbindungsleitung 48 stammende Loadsensing-Druck LS kann über einen Anknüpfungspunkt 56 an weitere Ventilsektionen (nicht dargestellt) im Bedarfsfall weitergeleitet werden. Ferner steht der Loadsensing-Druck LS an einer Schnittstelle 58 der Ventileinheit 60, bestehend aus erstem, zweiten und drittem Steuerventil 20, 40 und 50 zur Verfügung. Mit einem dahingehenden Loadsensing-Druck LS lässt sich beispielsweise eine der Druckversorgung P dienende Schwenkwinkelpumpe 62 ansteuern, die jedoch im vorliegenden gezeigten Fall von der zentralen Steuereinheit ECU ausschließlich elektrisch angesteuert wird.On its control side facing the inlet control orifice 52, a load sensing pressure LS acts, which is taken from the connecting line 48 between the first 20 and the second 40 control valve. On its control side facing the blocking position, 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. On the side where 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. Furthermore, 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. With such 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.

Die gezeigte Steuer- oder Rechnereinheit ECU kann, wie mit Pfeilen dargestellt, eingangsseitig Bedienbefehle entgegennehmen und ausgangsseitig noch weitere, nicht näher dargestellte Ventilsektionen mit ansteuern.The 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.

Mit der erfindungsgemäßen Ventilanordnung ist eine Auflösung von Steuerkanten über ein erstes Steuerventil 20 und ein zweites Steuerventil 40 realisiert, wobei das erste Steuerventil 20 die jeweiligen Rücklaufsteuerblenden 26 und 36 für die Ansteuerung des Rücklaufes aus dem Verbraucher 10 aufweist und das zweite Steuerventil 40 weist die Zulaufsteuerblende 42 für die Ansteuerung des Zulaufs zum ersten Steuerventil 20 und mithin zum Verbraucher 10 auf. Ein drittes Steuerventil 50 innerhalb der Ventileinheit 60, die insoweit als Ganzes tauschbar und auch als Nachrüstsatz zur Verfügung steht, ist in der Art einer Druckwaage ausgebildet und erlaubt insgesamt eine Zulaufvolumenstromregelung für den Verbraucher 10.With the valve arrangement according to the invention, 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.

Claims (7)

  1. Valve arrangement for supplying pressure medium to a hydraulic consumer, which valve arrangement has two work ports (A, B) for fluid connection to the consumer, with a first control valve,
    - which has a first supply (24), via which a first supply flow from the first work port (A) to the consumer (10) can be controlled, and with a first return control orifice (26), via which a first return flow (28) from the consumer (10) can be controlled via the second work port (B), simultaneously with the first supply (24); and
    - which has a second supply (34), via which a second supply flow from the second work port (B) to the consumer (10) can be controlled, and with a second return control orifice (36), via which a second return flow (38) from the consumer (10) can be controlled via the first work port (A), simultaneously with the second supply (34); and
    with a second control valve (40) having a supply control orifice (42) with which the respective supply (24, 34) of the first control valve (20) can be controlled,
    wherein a third control valve (50) in the form of a pressure compensator is connected in a connection between a pressure supply (P) and the second control valve (40), wherein the third control valve (50), as a 2/2-way pressure compensator, in one of its positions controls a supply between the pressure supply (P) and the second control valve (40) with its supply control orifice (52) and blocks this supply in another position, and
    wherein a control pressure, which is taken from a connecting line (54) between the second (40) and the third (50) control valve, is applied towards its blocking position,
    characterised in that
    at least one load-sensing (LS) pressure, which is taken from a connecting line (48) between the first (20) and the second (40) control valve, acts on its opposing control sides directed towards its supply control orifice (52); and
    in that the second control valve (40) in its unactuated position prevents a possible return flow, originating from the first (24) and the second (34) supply of the first control valve (20), through a check valve (49) integrated in the second control valve (40), which check valve in its closed position prevents the return flow from the outlet of the second control valve (40) towards its fluid inlet.
  2. Valve arrangement according to claim 1, characterised in that the first (24) and/or the second (34) supply of the first control valve are each configured free of means for narrowing the flow cross-section, in particular free of orifices or throttles.
  3. Valve arrangement according to claim 1 or 2, characterised in that the first control valve (20) is a 3/4-way proportional valve, preferably a 4/4-way proportional valve, which can be actuated with pilot pressure regulators and which in one valve position (44) permits a floating position for the connected consumer (10).
  4. Valve arrangement according to one of the preceding claims, characterised in that the second control valve (40) is a 2/2-way proportional valve which can be actuated with a pilot pressure regulator and in that the supply control orifice (42) is activated in an actuated position and a return flow, originating from the first (24) and the second (34) supply of the first control valve (20), is prevented in an unactuated position.
  5. Valve arrangement according to one of the preceding claims, characterised in that the current fluid pressure for both consumer ports (A, B) is picked up by means of a measured value device (18) and forwarded to a central control or computer unit (ECU) which initiates the actuation for the first (20) and the second (40) control valve and which controls the pressure supply (P) that is provided with a swivel angle pump (62).
  6. Valve arrangement according to one of the preceding claims, characterised in that the first control valve (20) is connected on the inlet side to the second (40) control valve and has a return port (46) on the inlet side, preferably leading to the tank (T).
  7. Valve arrangement according to one of the preceding claims, characterised in that the connectable hydraulic consumer (10) is a working cylinder with different rod and piston surfaces or a hydraulic motor.
EP19718099.5A 2018-05-07 2019-04-09 Valve arrangement for supplying a hydraulic consumer with pressure medium Active EP3759357B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018003728.3A DE102018003728A1 (en) 2018-05-07 2018-05-07 Valve arrangement for supplying pressure medium to a hydraulic consumer
PCT/EP2019/058885 WO2019214887A1 (en) 2018-05-07 2019-04-09 Valve arrangement for supplying a hydraulic consumer with pressure medium

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EP3759357A1 EP3759357A1 (en) 2021-01-06
EP3759357C0 EP3759357C0 (en) 2024-06-05
EP3759357B1 true EP3759357B1 (en) 2024-06-05

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US (1) US11168713B2 (en)
EP (1) EP3759357B1 (en)
DE (1) DE102018003728A1 (en)
WO (1) WO2019214887A1 (en)

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US11231053B2 (en) * 2018-06-13 2022-01-25 Parker Hannifin Emea S.À.R.L. Hydraulic valve arrangement
DE102021108081B4 (en) 2021-03-30 2023-02-02 Andreas Lupold Hydrotechnik Gmbh Device for controlling a hydraulic pump or a hydraulic motor
DE102022111288A1 (en) 2022-05-06 2023-11-09 Jungheinrich Aktiengesellschaft Hydraulic system for an industrial truck and industrial truck
EP4393867A1 (en) * 2022-12-23 2024-07-03 CNH Industrial Italia S.p.A. Telescopic handler

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

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