EP3721094B1 - Dispositif de soupape - Google Patents

Dispositif de soupape Download PDF

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Publication number
EP3721094B1
EP3721094B1 EP19705145.1A EP19705145A EP3721094B1 EP 3721094 B1 EP3721094 B1 EP 3721094B1 EP 19705145 A EP19705145 A EP 19705145A EP 3721094 B1 EP3721094 B1 EP 3721094B1
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EP
European Patent Office
Prior art keywords
pressure
valve
control
port
drs
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP19705145.1A
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German (de)
English (en)
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EP3721094A1 (fr
Inventor
Peter Bruck
Frank Schulz
Christian Stauch
Jan Lübbert
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Hydac Fluidtechnik GmbH
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Hydac Fluidtechnik GmbH
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Publication of EP3721094A1 publication Critical patent/EP3721094A1/fr
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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
    • 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
    • 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
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—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
    • F15B2211/3055—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and return line
    • 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
    • F15B2211/3057—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 two valves, one for each port of a double-acting 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
    • F15B2211/30—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
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in 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
    • F15B2211/30—Directional control
    • F15B2211/365—Directional control combined with flow control and pressure 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
    • 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
    • F15B2211/40—Flow control
    • F15B2211/465—Flow control with pressure compensation
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5151—Pressure control characterised by the connections of the pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure 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
    • F15B2211/60—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

Definitions

  • the pressure sensor records the current load situation on the drive part, that the pressure controller connects the secondary side of the system to a tank cap or return connection in its basic position, and that when the pressure controller is activated, the secondary pressure is based on the pressure of the proportional pilot control minus the am Valve piston of the pressure regulator is regulated attacking spring force, a control and regulation concept is realized in an advantageous manner, based on a basic system for hydraulically controllable drive parts or consumers, such as hydraulic working cylinders or hydraulic drive motors, a pressure, path, speed and position measurement for the movable components of the respective selected drive part can be achieved.
  • Such hydraulic systems are subject to increasing demands in terms of productivity, flexibility and energy efficiency.
  • multi-circuit systems are becoming increasingly popular, i.e. hydraulic structures with assigned pumps for the various consumers.
  • the distribution of the performance requirements involves an enormous, energetic Potential.
  • cost and space-sensitive applications however, such multi-circuit systems are difficult to use from an economic and constructive point of view.
  • the invention is based on the object of simplifying such known hydraulic structures and replacing them with a more efficient control or valve concept in order to reduce the respective energy consumption in order not only to save operating costs, but also to make a contribution to the to create increasingly strict legal exhaust gas regulations.
  • valve device with the features of patent claim 1 in its entirety. Due to the fact that, according to the characterizing part of patent claim 1, the pressure control device and the volume flow control device each have a proportional valve and a pressure control valve in addition to a pressure compensator in terms of their function, which are interconnected and controlled in such a way that when the inflow connection is supplied from the pressure supply connection in one direction of flow one pressure control valve works as a pressure regulator and on the side of the outflow connection, when a predefinable setpoint pressure is exceeded at the other pressure control valve, the flow direction reverses and the pressure fluid flows via the other proportional valve and the associated pressure compensator, both of which work as flow control valves, in the direction of the return connection away.
  • valve device can be implemented in a “separate design” with individual valve components that are structurally separate from one another.
  • a kind of decentralized valve control is created with so-called separate control edges, which offer the possibility of separate activation of valve elements on the inflow and outflow side of a hydraulic consumer, such as a hydraulic working cylinder, that can be connected to the valve device.
  • circuit topologies can be implemented that include, for example, floating or rapid traverse positions.
  • valve device With the valve device according to the invention, the requirements within the scope of movement tasks for the hydraulic consumer are met, on the one hand setting a specific speed and on the other hand being able to ensure that the inlet side of the consumer is sufficiently filled in the case of supporting, so-called generator loads.
  • the valve device uses a hydraulic-mechanical regulation for the volume flow and pressure variables.
  • volumetric flow control On the outlet side of the consumer, because motor and generator loads can be set to a defined speed with the same current controller. Accordingly, the pressure control is then on the inflow side, which means that filling deficits during lowering movements (generative load) are avoided assuming an adequate supply through hydraulic-mechanical adjustment of a sufficiently high filling pressure.
  • valve device according to the invention is used with a hydraulic consumer, such as a hydraulic working cylinder or a hydraulic motor that can be moved in opposite directions, when the direction of movement or actuation changes, the inlet side in question then becomes the outlet side and the outlet side becomes the inlet side for the respective consumer.
  • the valve device according to the invention ensures that with only one device, even with changing directions of actuation, the pressure control device always acts on the inflow side with the pressure supply and on the respective outflow side a volume flow control device acts to control the fluid flow.
  • the valve device according to the invention is able to use the energetic, functional and structural potential of separate control edges in valves and at the same time to master the resulting complexity at the component and control level.
  • the valve device according to the invention can be operated in an energetically favorable manner, which helps to reduce operating costs, and due to the improved control concept with the separate control edges, drive energy can be saved within the framework of the pressure supply, regularly provided by motor-driven hydraulic pumps, which helps to reduce exhaust gas values.
  • valve components in particular the respective pressure control valve and the respective associated pressure compensator, in terms of their functions in a single combination valve.
  • the combination valve has two control slides that can be moved independently in a valve housing, in the form of a pressure control slide and in the form of a pressure balance slide, which control the possible fluid-carrying connections between the pressure supply connection, the return flow connection and a working connection, which is used for the hydraulic Consumers in the one and the other opposite direction of flow respectively forms the inlet and outlet connection.
  • a decentralized valve control with separate control edges can be implemented with just one combination valve with two control slides that can be moved independently in the valve housing, which, in addition to improved control geometry, also offers structural advantages, in particular with regard to the reduction in the amount of tubing and piping compared to known solutions with isolated, spatially separated valves separate individual valves.
  • the valve device shown has an inlet connection ZA on an inlet side for supplying a hydraulic consumer that can be connected to the inlet connection ZA with pressurized fluid. Furthermore, an outlet connection AA is provided on an outlet side for the discharge of pressurized fluid from the consumer that can be connected. Furthermore, the valve device has a pressure supply connection P for supplying the valve device and the hydraulic consumer with pressure fluid at a predefinable pressure, and a return connection T or a tank connection is also provided for discharging displaced fluid from the hydraulic consumer and the valve device.
  • the hydraulic consumer is formed from a hydraulic working cylinder AZ with a piston rod unit KSE, the working cylinder AZ on its piston side is permanently in fluid communication with the inlet port ZA and the rod side is connected to the outlet port AA as shown in FIG 1 . If the piston side of the piston rod unit KSE is supplied with pressure fluid at a predefinable pressure via the inlet connection ZA, the piston rod unit KSE moves in the direction of the 1 viewed to the right and the fluid in the rod space is discharged from the working cylinder AZ via the outlet connection AA.
  • the outflow connection AA then becomes the inflow connection ZA and the fluid displaced on the piston side during the retracting movement of the piston rod unit KSE leaves the working cylinder AZ via an outflow connection AA, which originally formed the inflow connection ZA during the extending movement.
  • the piston rod unit KSE of the working cylinder AZ therefore performs a reciprocating movement and, to this extent, a movement in opposite axial directions.
  • a hydraulic motor unit (not shown) could also act as a hydraulic consumer, which could also rotate in opposite directions, depending on how full its chambers are.
  • a 3/2 proportional slide valve DRV with a pressure compensator DW is present both on the inflow side and on the outflow side of the valve device.
  • the input of the 3/2 proportional spool valve DRV is connected to a standard pressure supply source, such as a hydraulic pump, via the pressure supply port P.
  • the output of the proportional valve DRV is in the form of a useful connection and is denoted by A.
  • the proportional valve DRV can be actuated electromagnetically and the valve spool can be actuated on its opposite control side with the control pressure from the useful port A.
  • the volume flow in question, coming from the useful connection A, is reduced to one input of the pressure compensator DW, which, in the pressure compensator position shown, supplies the pressure at the service port A to the tank or return port T. In another control position of the respective pressure compensator DW, it assumes a position blocking the pertinent fluid path.
  • one control side of the respective pressure compensator DW is acted upon by an energy accumulator, in particular in the form of a compression spring, and the return pressure, originating from the useful port A, is also available as control pressure, provided that the respective proportional valve DRV has its further, in the 1 occupies the slide position shown, in which the fluid-carrying connection from the pressure supply port P to the user port A is prevented and otherwise there is a fluid connection returning from the user port A in the direction of one control side of the pressure compensator DW.
  • the pressure PM is present at a measuring connection M, which is tapped at the inlet connection ZA or at the outlet connection AA of the working cylinder AZ.
  • the right 3/2 proportional spool valve DRV acts as a directional control valve, with the control edge from useful port A to the right-hand pressure compensator DW being fully open.
  • the arrangement shown then acts as a flow control valve.
  • a possible structure of a so-called 2 A possible structure of a so-called 2 .
  • the essential components of the combination valve are only shown in principle and in a simplified manner, and the combination valve is also only shown with its upper half above its actuating axis, with the rotationally symmetrical overall valve housing of the combination valve not being shown for the sake of simplicity, but of course the includes valve mimics explained in more detail below and leaves passages correspondingly free to form the individual connections P, A, T, M.
  • the valve shown has two slides in the form of a pressure control slide DRS shown on the left and a pressure compensator slide DWS shown on the right.
  • the pertinent two slides DRS and DWS control the fluid-carrying connections between the pressure supply port P, the working port A and the return port T, which in this respect forms the tank port.
  • the return port T shown on the left or tank port of a pilot stage, formed from a pilot cone 18, which can be controlled by an actuating magnet of conventional design for the combination valve shown, is combined with the main tank port (return port T) shown on the right, but this is not absolutely necessary.
  • pilot control space X in which a control pressure px, which originates from the pressure supply port P, is present, with said control pressure px being proportional to the force of the energized actuating magnet or proportional magnet acts from left to right on the pressure control slide DRS.
  • a pilot channel 5 is provided, which has an orifice 3 or a flow control valve (not shown) as a pressure divider of the pilot.
  • the pilot pressure is px on a reporting surface 1, which, in the direction of the 2 seen, forms the left end face of the pressure control slide DRS and in the in 2
  • the pilot chamber X which is otherwise delimited by the valve housing, is essentially reduced to zero, except for a notch marked 2 for the hydraulic end position of the pressure control slide DRS in its in Figures 3a, 3b shown right end or stop position.
  • a compensating space E can be seen, according to the representation after the 2 is also essentially collapsed to the volume of zero.
  • the compensating chamber E is delimited by the valve housing and by a compensating surface 4 as part of an annular collar, which is radially widened compared to the other diameter of the pressure control slide DRS.
  • the annular surface 4 ′ of the annular collar opposite the compensation surface 4 in the present case provided with the same diameter as the compensation surface 4 , is directly exposed to the supply pressure px at the pressure supply connection P .
  • the compensating chamber E is permanently fluid-carrying connected to the useful port A via the compensating channel 6 shown in dashed lines in the pressure control slide DRS.
  • the compensating channel 6 opens out at a further or right annular surface 9 of the pressure control slide DRS, with the annular surface 9 having the same diameter as the annular surface 4, which in this respect serves as a compensating surface for the surface 9, which is of particular importance for the function.
  • the right annular surface 9 is also part of an annular collar with a further stop surface 9' with the same Diameter that also delimits the pressure supply port P in the position shown.
  • the diameters of the surfaces 4' and 9' can differ from one another, only the diameters of the surfaces 4 and 9 must be the same.
  • an actual pressure reporting space Y is available, which, in the direction of the 2 seen, is limited on the left side by a reporting surface 11 for the actual pressure p A in pressure control mode and otherwise by a cylindrical recess in the pressure balance slide DWS, which overlaps or encompasses a right free end area of the cylindrical pressure control slide DRS with its left annular surface 12. While the reporting area 11 forms the right free front end of the pressure control slide DRS, opposite there is a circular area 16 with the same diameter on the inside of the pressure balance slide DWS. A possible control pressure p A , which originates from the useful port A, is thus pressure-effective on the reporting surface 11 as well as on the circular surface 16 of the pressure compensator slide DWS.
  • the reporting or control pressure P A is reported to the surfaces 11 and 16 in the pressure compensator mode. Due to the possible movement of the two slides DRS and DWS, the free volume of the actual pressure signaling chamber Y changes.
  • a signaling channel 7, shown in dashed lines is used, which is connected to an im Diameter compared to the annular surfaces 9, 9 'reduced central collar or annular collar opens out, which is insofar permanently fluid-carrying with the user port A in connection.
  • the pertinent reporting channel 7 for the actual or control pressure p A at the useful port A opens into the actual pressure reporting space Y.
  • a damping diaphragm 8 can be connected to the reporting channel 7 in an optional manner, ie if required.
  • the pressure compensator slide DWS is supported via a widened end flange surface on an energy storage device in the form of a compression spring 14 for the pressure compensator, with the pertinent compression spring 14 being made relatively hard. Furthermore, there is a stop 15 for the free movement of the pressure compensator slide DWS to the left in the valve housing, which is not specified in more detail.
  • the spring 14 is also supported with its end opposite the flange surface of the pressure compensator slide DWS on wall parts of a pertinent valve housing.
  • another energy store is guided in the form of a compression spring 10, which co-determines the response behavior of the pressure controller in a relatively soft manner.
  • the pertinent compression spring 10 is supported with its one free end on the circular surface 16 of the pressure compensator slide DWS and with its other free end on the face of a bore in the pressure control slide DRS.
  • a reporting space M is present in the valve housing, which, in the direction of the 2 seen, is limited on the left side by a reporting surface 17, which forms the right free front end of the pressure compensator slide DWS in the area of its flange widening.
  • the core idea of this valve concept according to the invention lies in the separation of the tasks of pressure control and pressure compensator function, which are distributed between the two slides DRS and DWS, which are provided with independent energy storage devices in the form of compression springs 10 and 14, with compression spring 10 not only acting on the pressure compensator slide DWS acts on its circular surface 16, but also via a contact possibility in the area of the further annular surface 9' on the pressure control slide DRS.
  • the left slide or pressure control slide DRS implements the pressure control function, starting from the pressure supply port P to the pressure port A.
  • the soft spring 10 keeps it in the rest position at the left stop.
  • the pressure control slide DRS has three channels, with the pilot channel 5 supplying the pilot stage with fluid (oil) from the pressure supply port P.
  • the pilot channel 5 supplying the pilot stage with fluid (oil) from the pressure supply port P.
  • an orifice plate 3 is used in channel 5 or a miniature flow control valve (not shown) integrated in the pressure control slide valve DRS.
  • the advantage of the latter solution is the lower and constant pilot current. This means that the control pressure in the pilot chamber X is independent of the supply pressure at port P. However, this is offset by higher production costs.
  • the reporting channel 7, reports the actual pressure p A at the working port A in the inner space Y between the two slides DRS and DWS.
  • a damping screen 8 can be used here.
  • Notch 2 is used to create a hydraulic end position for the pressure control slide DRS.
  • the right slide or pressure compensator slide DWS works in this respect as a pressure compensator, which compares the pressure at the useful port A with the pressure at the measuring port 20 or with the pressure in the signaling chamber M. The resulting control pressure difference is defined by the design of the hard spring 14 as the additional energy store.
  • the Figures 3a, 3b and 3c represent different rest states of the combination valve, the no-load rest state as shown in FIG Figure 3a shows the same valve state as shown in FIG 2 is reproduced, and the Figure 3b represents a loaded rest condition for the valve, whereas the 3c shows the valve in the loaded state of rest and pre-energized.
  • the stressed resting state as shown after Figure 3b is characterized by a load pressure at the measuring connection 20 or in the reporting space, which acts on the reporting surface 17 on the right-hand side of the printing carriage slide DWS.
  • the pressure present at the reporting area 17 moves the pressure compensator slide DWS as shown in FIG Figure 3b into the left end position, which is defined, for example, with the aid of the annular stop 15.
  • the seat-tight holding of the load requires a seat-tight construction of a sealing point between the signaling space M to the return port T (not shown).
  • the fluid-carrying connection between the useful port A and the return port T is closed except for the relief notch 13, which is geometrically small.
  • the pressure control slide DRS displaces fluid or oil volume from the actual pressure signaling chamber Y with its end face 11, whereby this fluid volume can flow out via the signaling channel 7 into the working connection A, but from there it cannot flow out of the system due to the closed connection valve PV can escape.
  • the fluid (oil) is therefore forced to flow into the intermediate space Z and via the relief notch 13 of the pressure compensator in the form of the pressure compensator slide DWS into the tank or return connection T, until the pressure control slide DRS closes the fluid-carrying connection between the useful port A and the intermediate space Z.
  • Fluid flows from the pressure supply port P to the working port A.
  • the pressure at the working port A corresponds to the target pressure set in the pilot control chamber X with the help of the pilot control stage minus the pressure difference, which corresponds to the spring force that the preloaded pressure control spring 10 exerts on the pressure control piston or pressure control slide DRS exercises
  • the pilot stage mentioned is realized by components that are given the reference symbols 3, 5, 18 and 19.
  • the actual pressure p A at the useful port A is reported via the pertinent signaling channel 7 in the pressure control slide DRS on its right-hand face 11 in the inner space in the form of the actual-pressure signaling space Y and with the help of the face 1 of the same size on the left-hand side of the pressure control slide DRS with the pilot pressure px in the pre-control room X.
  • the geometry of the pressure control slide DRS is designed in such a way that the space Y and thus the surface 11 is always connected to the useful port A via the signaling channel 7 .
  • the pressure compensator is in one of its two end positions or possibly in between.
  • the triangular notch 2 opens a connection from the pilot control chamber X into the relief chamber E and from there via the equalization channel 6 and the intermediate space Z into the return port T. It must be ensured in the design that the connection from the relief or equalization chamber E to the return port T remains intact is retained when the pressure compensator is at the left stop, which is shown in the Figure 5b is shown. In this case, the relief notch 13 remains as a residual opening from the intermediate space Z to the tank or return port T.
  • the fluid (oil) flowing out via the notch 2 lowers the pilot control pressure px to such an extent that an equilibrium, determined by the useful port pressure p A , is reached between the useful port pressure p A and the pilot pressure p x adjusts.
  • the pressure control slide DRS then remains in the effective range of notch 2. The stability of this state depends to a large extent on the selected notch geometry. In addition, it must be ensured that the flow resistance through the compensating channel 6 and the relief notch 13 is significantly lower than the resistance over the notch 2. Its resistance must not exceed that of the fully open pilot valve cone seat 19.
  • the pressure compensator operation is shown. If the pilot pressure px in the pilot chamber X is less than the working pressure am Useful connection A or in space Y, the resulting force acting on surfaces 1 and 11 of pressure control slide DRS moves pressure control slide DRS to the left end position as shown in the illustration 6 .
  • the cross-section from useful connection A to intermediate space Z thus opens up completely.
  • the working pressure p A then acts directly on the left annular surface 12 and indirectly via the signaling channel 7 on the left circular surface 16 of the pressure compensator slide DWS as a signaling pressure.
  • the pressure compensator slide DWS compares the working pressure p A with the measurement pressure p M , which acts on the right-hand circular area 17 of the pressure compensator.
  • the area 17 corresponds to the sum of the areas 12 and 16.
  • the pressure compensator slide DWS assumes a position in which the volume flow from the useful port A to the tank or return port T at the throttle point between the intermediate space Z and the return port T is throttled in such a way that the measured pressure p M minus the control pressure difference ⁇ p M defined by the spring 14 sets in at the useful port A.
  • an electro-hydraulic control for hydraulic drives is created overall, which can work in two directions both in motor and in generator mode.
  • a pilot operated proportional spool valve is used, which combines the function of a pressure reducer for the inlet pressure control and a pressure compensator for the outlet flow control in one combination valve.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)

Claims (9)

  1. Dispositif de soupape comprenant
    - un raccord (ZA) d'entrée d'un côté d'entrée pour l'alimentation en fluide sous pression d'un consommateur hydraulique pouvant être raccordé au raccord (ZA) d'entrée,
    - un raccord (AA) de sortie d'un côté de sortie pour l'évacuation de fluide sous pression du consommateur pouvant être raccordé, dans lequel, suivant le sens de commande de ce consommateur, le côté d'entrée devient le côté de sortie et le côté de sortie devient le côté d'entrée,
    - un raccord (P) d'alimentation en pression, et
    - un raccord (T) de reflux,
    dans lequel du respectif
    - côté d'entrée agît un dispositif de régulation de la pression, et
    - côté de sortie agît un dispositif de régulation du courant en volume,
    caractérisé en ce que le dispositif de régulation de la pression et le dispositif de régulation du courant en volume ont, par leur fonction, respectivement une soupape (PV) proportionnelle et une soupape (DRV) de réglage de la pression outre une balance (DW) manométrique, qui sont montées entre elles et commandées, de manière à ce que, lors d'une alimentation du raccord (ZA) d'entrée de la part du raccord (P) d'alimentation en pression dans un sens de passage, la une soupape (DRV) de réglage de la pression travaille en régleur de pression, et de la part du raccord (AA) de sortie, lorsqu'une pression de consigne pouvant être donnée à l'avance est dépassée à l'autre soupape (DRV) de réglage de la pression, le sens de passage s'inverse, et le fluide sous pression s'évacue en direction du raccord (T) de reflux, en passant par l'autre soupape (PV) proportionnelle et par la balance (DW) manométrique associée, qui travaillent toutes deux par leur fonction en soupape de réglage du courant.
  2. Dispositif de soupape suivant la revendication 1, caractérisé en ce que la soupape (DRV) respective de réglage de la pression est une vanne proportionnelle à passage direct, de préférence une vanne proportionnelle à passage direct à 3/2 voies, qui, pouvant être commandée au moyen d'au moins un aimant (18) proportionnelle, rend possible le réglage d'une prescription de pression de consigne à la soupape (DRV) de réglage de pression.
  3. Dispositif de soupape suivant la revendication 1 ou 2, caractérisé en ce que la soupape (DRV) respective de réglage de pression et la balance (DW) manométrique lui appartenant respectivement sont rassemblées en une soupape de combinaison par leurs fonctions.
  4. Dispositif de soupape suivant la revendication 3, caractérisé en ce que la soupape de combinaison dispose de deux tiroirs de commande pouvant se déplacer indépendamment dans un corps de soupape, sous la forme d'un tiroir (DRS) de réglage de pression et sous la forme d'un tiroir (DWS) de balance manométrique, qui commandent les liaisons fluidiques possibles entre le raccord (P) d'alimentation en pression, le raccord (T) de reflux et un raccord (A) de travail, qui forme en liaison avec une soupape (PV) proportionnelle dans un sens d'écoulement et dans l'autre sens opposé, le raccord (ZA) d'entrée ou le raccord (AA) de sortie.
  5. Dispositif de soupape suivant la revendication 4, caractérisé en ce que la soupape de combinaison a, à l'intérieur du corps de la soupape, les espaces suivants :
    - un espace (X) pilote, dans lequel une pression (px) de commande, qui provient du raccord (P) d'alimentation en pression, agît, conformément à l'effet de l'aimant proportionnel alimenté en courant, sur le tiroir (DRS) de réglage de pression,
    - un espace (E) de compensation,
    - un espace (Z) intermédiaire dans la liaison fluidique possible entre le raccord (A) utile et le raccord (T) de reflux, dans lequel une pression (pz) de commande provenant de cette liaison agît,
    - un espace (Y) de signalisation de la pression réelle, dans lequel agît une pression (pA) de commande, qui provient de la pression respective au raccord (A) utile, et
    - un espace (M) de signalisation, dans lequel une pression (pM) de commande s'applique, à l'encontre de l'effet d'un accumulateur (14) d'énergie, au tiroir (DWS) de la balance manométrique.
  6. Dispositif de soupape suivant la revendication 5, caractérisé en ce que, dans le tiroir (DRS) de réglage de la pression est introduit un conduit (5) pilote pour un diaphragme (3) ou une soupape de réglage de la pression pour un pilotage, qui relie fluidiquement le raccord (P) d'alimentation en pression à une surface (1) de signalisation, qui limite au moins en partie l'espace (X) pilote.
  7. Dispositif de soupape suivant la revendication 5 ou 6, caractérisé en ce que, dans le tiroir (DRS) de réglage de la pression est introduit un conduit (6) de compensation, qui relie fluidiquement le raccord (A) utile à l'espace (E) de compensation.
  8. Dispositif de soupape suivant l'une des revendications 5 à 7, caractérisé en ce que, dans le tiroir (DRS) de réglage de la pression est introduit un conduit (7) de signalisation, comprenant un diaphragme (8) d'amortissement pouvant éventuellement y être monté, qui achemine la pression (pA) réelle au raccord (A) utile dans l'espace (Y) de signalisation de la pression réelle, qui est délimité par le tiroir (DWS) de la balance manométrique, ainsi que d'un côté (11) de commande du tiroir (DRS) de réglage de la pression, qui est guidé dans l'espace (Y) de signalisation de la pression réelle.
  9. Dispositif de soupape suivant l'une des revendications 5 à 8, caractérisé en ce que le tiroir (DWS) de la balance manométrique s'appuie sur un autre accumulateur (10) d'énergie, qui attaque l'espace (Y) de signalisation de la pression réelle, en traversant le tiroir (DRS) de réglage de la pression.
EP19705145.1A 2018-02-20 2019-02-07 Dispositif de soupape Active EP3721094B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018001303.1A DE102018001303A1 (de) 2018-02-20 2018-02-20 Ventilvorrichtung
PCT/EP2019/052965 WO2019162097A1 (fr) 2018-02-20 2019-02-07 Dispositif de soupape

Publications (2)

Publication Number Publication Date
EP3721094A1 EP3721094A1 (fr) 2020-10-14
EP3721094B1 true EP3721094B1 (fr) 2022-06-01

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EP19705145.1A Active EP3721094B1 (fr) 2018-02-20 2019-02-07 Dispositif de soupape

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US (1) US20200378409A1 (fr)
EP (1) EP3721094B1 (fr)
DE (1) DE102018001303A1 (fr)
WO (1) WO2019162097A1 (fr)

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Publication number Priority date Publication date Assignee Title
CN112648244B (zh) * 2021-02-19 2022-06-14 太原理工大学 泵阀协同多执行器电液系统及其控制方法
IT202100019439A1 (it) * 2021-07-22 2023-01-22 Roberto Tomassini Attuatore idraulico controllato per l'impiego su veicoli, rimorchi, semi-rimorchi, carichi sospesi e macchinari industriali.
DE102022002037A1 (de) * 2022-06-09 2023-12-14 Hydac Mobilhydraulik Gmbh Hydraulisches System

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Publication number Priority date Publication date Assignee Title
DE19646445A1 (de) * 1996-11-11 1998-05-14 Rexroth Mannesmann Gmbh Ventilanordnung
US6860291B2 (en) * 2001-04-17 2005-03-01 Bucher Hydraulics Gmbh Directional control valve comprising an internal pressure regulator
DE20208577U1 (de) * 2002-06-03 2003-12-11 Hawe Hydraulik Gmbh & Co. Kg Elektrohydraulische Hubsteuervorrichtung für Flurförerfahrzeuge
DE10330869A1 (de) 2003-07-09 2005-02-17 Hydac System Gmbh Hydraulisches System
DE102004048642A1 (de) * 2004-10-04 2006-04-06 Bosch Rexroth Aktiengesellschaft Hydraulische Steueranordnung
DE102005021887A1 (de) * 2005-05-04 2006-11-16 Kässbohrer Geländefahrzeug AG Verfahren sowie Vorrichtung zur Fahrstabilitätserhöhung von Kraftfahrzeugen
US7302797B2 (en) * 2005-05-31 2007-12-04 Caterpillar Inc. Hydraulic system having a post-pressure compensator
DE102008064138A1 (de) * 2008-12-19 2010-07-01 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102009033645A1 (de) * 2009-07-17 2011-01-20 Robert Bosch Gmbh Hydraulische Steueranordnung

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DE102018001303A1 (de) 2019-08-22
EP3721094A1 (fr) 2020-10-14
US20200378409A1 (en) 2020-12-03
WO2019162097A1 (fr) 2019-08-29

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