EP3721094A1 - Dispositif de soupape - Google Patents

Dispositif de soupape

Info

Publication number
EP3721094A1
EP3721094A1 EP19705145.1A EP19705145A EP3721094A1 EP 3721094 A1 EP3721094 A1 EP 3721094A1 EP 19705145 A EP19705145 A EP 19705145A EP 3721094 A1 EP3721094 A1 EP 3721094A1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
control
port
drs
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19705145.1A
Other languages
German (de)
English (en)
Other versions
EP3721094B1 (fr
Inventor
Peter Bruck
Frank Schulz
Christian Stauch
Jan Lübbert
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hydac Fluidtechnik GmbH
Original Assignee
Hydac Fluidtechnik GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Hydac Fluidtechnik GmbH filed Critical Hydac Fluidtechnik GmbH
Publication of EP3721094A1 publication Critical patent/EP3721094A1/fr
Application granted granted Critical
Publication of EP3721094B1 publication Critical patent/EP3721094B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F15B13/0416—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
    • 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
    • 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 invention relates to a valve device with an inlet port of an inlet side for the supply of a connector at the Anschlußba ren hydraulic consumer with pressurized fluid, with a drain port of a drain side for the discharge of pressurized fluid from the connectable consumer, depending on the driving direction of this consumer to running side in the Outlet side and the drain side changed to the inlet side, with a pressure supply connection and with a return connection.
  • a hydraulic system is known with a hydraulically controllable drive part as a hydraulic consumer with two opposite drive directions, at least one drive direction to at least one pressure regulator, in particular in valve form, seen before, and a throttle between the pressure regulator and the Drive part, wherein for detecting the load state of the drive part, a sensor is provided, in the form of a pressure sensor, which is connected for each drive direction of the drive part in the associated, fluid-carrying strand between the throttle and the drive part.
  • Such hydraulic systems are increasingly demanding in terms of productivity, flexibility and energy efficiency.
  • large machines such as those used in the "mining area”, for example, multi-circuit systems are increasingly gaining acceptance, ie hydraulic structures with associated pumps for the various consumers.
  • the division of the power requirements has enormous ener- gy potential
  • Such multi-circuit systems from an economic and constructive point of view, however, difficult to use.
  • the present invention seeks to simplify such known hydraulic structures and replace them with a more efficient control or valve concept, in order to lower the respective energy intake, in order not only to save operating costs, but also to make a relieving contribution to the increasingly stricter statutory exhaust gas regulations.
  • valve device having the features of patent claim 1 in its entirety. Characterized in that according to the characterizing part of claim 1 to the respective inlet side a pressure control device and the respective outlet side a Vo lumensstromregelungs adopted acts, a kind of decentralized valve control is created with so-called. Separate control edges, the possibility of a separate control of valve elements on the Zu - and drain side of a connectable to the valve device hydraulic consumer chers, such as a hydraulic cylinder offer. In addition to an individual actuation of inlet and outlet, circuit topologies can be set, which include, for example, swim or rapid traverse positions.
  • valve device With the valve device according to the invention the requirements in the context of movement tasks for the hydraulic consumer he fills, on the one hand set a certain speed and on the other hand to ensure that the inlet side of the consumer in the case of un ter widender, so-called. Generational loads is sufficiently filled.
  • the valve device according to the invention uses a hydraulic-mecha African regulation for the variables volume flow and pressure.
  • the pressure control is then on the inlet side, which filling deficiencies in lowering movements (generatori cal load) under the assumption of sufficient supply by hy-mechanical control of a sufficiently high filling pressure avoided the be avoided.
  • the valve device according to the invention for use in a hydraulic consumer, such as a hydraulic cylinder or a movable in opposite directions hydraulic motor, at egg nem change of movement or actuation direction the addressed inlet side then to the outlet side and the outlet side to the inlet side for the respective consumer.
  • the invention Ventilvorrich device ensures that with only one device even with changing Actuate transmission directions always on the inlet side with the pressure supply the pressure control device and on the respective outlet side a Volu menstromregelungs adopted acting on the fluid flow acts.
  • valve device is able to exploit the energetic, functional and structural potentials of separate control edges in valves while at the same time controlling the ensuing complexity at the component and control levels.
  • the fiction, contemporary valve device can operate energetically low, which helps reduce Be operating costs and due to the improved control concept with the separate control edges can be within the Druckversor supply regularly provided by motorized hydraulic pumps, drive energy savings, which helps reduce exhaust emissions.
  • Ventilvor direction is provided that the pressure control device and the Volu menstromregelungs adopted each have a proportional valve together with a pressure compensator and a pressure control valve of their function forth, which are interconnected and controlled such that at a supply of Ver supply connection from the side Pressure supply connection in a flow direction, the pressure control valve works and on the side of the drain port at a predetermined Sol l pressure on the other pressure control valve, this flow direction is reversed.
  • the pressurized fluid flows over the other proportional valve and the associated pressure compensator, both of which function of their function as a flow control valve, in the direction of the return port from.
  • the valve device according to the invention can be realized in a "dissolved construction" with individual, structurally separated valve components.
  • Ventilkompo components in particular the respective pressure control valve and the respective associated levers pressure balance, summarize their functions in a single combination valve forth.
  • the combination valve has two independently movable in a valve housing spool, in the form of a pressure control slide and in the form of a Druckwaa genschiebers that control the possible fluid-carrying connections between the pressure supply port, the return port and a Ar beitsan gleich, for the hydraulic consumer in one and the other opposite flow direction respectively forms the inlet and the drain port.
  • a decentralized valve control realize with separate STEU erkanten, which also offers structural advantages in addition to an improved control geometry, in particular as regards the reduction of the tubing and Verrohrungsaufwandes with respect to known solutions with isolated , spatially separated individual valves.
  • Ventilvorrich device is the subject of the other dependent claims.
  • the valve device according to the invention will be explained in more detail by means of embodiments according to the drawing. This show in principle and not to scale representation of the
  • Fig. 1 in the manner of a hydraulic circuit diagram, a first Ausry tion form of the valve device according to the invention in "dissolved" construction with a plurality of individual valve components;
  • FIG. 2 to 6 a second embodiment of the valve device according to the invention, with the function of the individual Ventilkom components according to FIG. 1 in a combination valve are summarized to sammengeankt.
  • the valve device shown in Fig. 1 has an inlet port ZA an inlet side for the supply of a closable at the inlet port ZA hydraulic consumer with pressurized fluid. Furthermore, a drain port AA of a drain side for the discharge of pressurized fluid from the connectable consumer is provided.
  • the Ven tilvoriques a pressure supply port P for the supply of the valve device and the hydraulic consumer with pressure fluid presettable pressure and further comprises a return port T repek tive a tank port provided for the removal of displaced fluid from the hydraulic consumer and the valve device
  • the hyd raulische consumer is GE from a hydraulic cylinder AZ forms with a piston rod unit KSE, wherein the working cylinder AZ on its piston side permanently fluid leading to the inlet port ZA in connection and the rod side with the drain port AA as shown in FIG. If the piston side of the piston rod unit KSE supplied via the inlet port ZA with pressure fluid specifiable pressure, the piston rod unit KSE, as seen in the direction of FIG.
  • both on the inlet side and on the downstream side of the valve device each have a 3/2-proportional valve PV with a pressure compensator DW available.
  • the input of the 3/2 proportional spool valve PV is connected via the pressure supply port P to a common pressure supply source such as a hydraulic pump.
  • the output of the proportional valve PV is designed in the manner of a NutzanInstitutes and designated A.
  • the proportional valve PV is, as shown, electromagnetically controllable and the valve spool is on its opposite control side with the control pressure from the user port A can be controlled.
  • the pertinent volume flow, originating from the user port A is directed to an input of the pressure compensator DW, which in the illustrated pressure compensator position leads the pressure at the user port A to the tank or return port T.
  • an adjustable pressure relief valve DBV in the usual manner against excessive operating pressure in the direction of the return port T hedged.
  • the respective pressure control valve DRV is an unspecified and shown control device that processed the pressure transducer DETA measuring pressure at the inlet connection ZA respectively at the running connection AA made clear and control signals to the pressure control valves DRV and the electromagnetically actuated proportional valves PV purpose of their Control forwards.
  • 3/2-proportional valve DRV as a directional control valve, the control edge of user port A to the right pressure compensator DW is fully open.
  • the arrangement shown acts as a current control valve.
  • the valve device shown in Fig. 1 in so-called.
  • Resolved design thus offers a hydraulic-mechanical control of the sizes of volume flow and pressure.
  • the volume flow control was placed on the discharge side of the hydraulic consumer, because such motori cal and regenerative loads can be set with the same current controller to a defi ned speed. Consequently, then so far as the pressure control on the inlet side, whereby Be Shellungsde ficits are avoided in lowering movements (regenerative load) assuming a sufficient supply by hydraulic-mechanical adjustment of a sufficiently high filling pressure.
  • the valve shown in Fig. 2 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 slide DRS and DWS control the fluid-carrying connections between the pressure supply port P, the working port A and the return flow port T, which forms the tank port.
  • pilot control chamber X in which a control pressure px, which comes from the pressure supply port P, pending, said control pressure px proportional to the force of the energized actuating magnet or proportional solenoid acts from left to right on the pressure control slide DRS.
  • a pilot channel 5 is provided which has a diaphragm 3 or an unspecified Darge notified flow control valve as a pressure divider of the pilot control. in this respect is the pilot pressure px to a reporting area 1, which, as seen in the direction of FIG. 2, the left end face of the pressure control slide DRS forms and in the illustrated in Fig.
  • FIG. 2 displacement position of the pressure control slide DRS is the pilot chamber X, otherwise of the Valve housing is limited, essentially reduced to zero, except for a designated notch for the hydraulic end position of Druckregelschie bers DRS in his in Fig. 3a, 3b tion right end or stop posi.
  • a compensation chamber E can be seen, which according to the representation according to FIG. 2 has likewise moved substantially to the volume zero.
  • the compensation space E is bounded by the valve housing and by a compensation surface 4 as part of a collar, which is widened radially relative to the other diameter of the pressure regulating slide DRS.
  • the compensation surface 4 against the opposite annular surface 4 'of the annular collar, provided in the present case the same diameter as the compensation surface 4, is directly the supply pressure px exposed at the pressure supply port P. Furthermore, the compensation chamber E is permanently connected in a fluid-conducting manner to the utility connection A via the compensation channel 6 shown in dashed lines in the pressure control slide DRS. Accordingly, the compensation channel 6 opens at a further or right annular surface 9 of the pressure control slide DRS, wherein the annular surface 9 has the same diameter as the annular surface 4, which serves as a compensation surface for the surface 9, which is for the function tion of particular importance.
  • the right annular surface 9 is part of an annular collar with a further stop surface 9 'with the same diameter, which limits the pressure supply port P in the position shown.
  • the diameters of the surfaces 4 'and 9 may be different voneinan, only the diameters of the surfaces 4 and 9 must be the same.
  • a gap Z in the connection between Nutzan circuit A and return port T is present in which there is a resulting from this connection control pressure pz. In the extent parallel to the pressure control slide DRS extending gap Z open the user port A and the main return port T radially.
  • an actual pressure reporting room Y is present, which, as seen in the direction of FIG. 2, is limited on the left side of a reporting area 1 1 for the actual pressure pA in pressure control mode and otherwise by a zy-cylindrical recess in the pressure compensator slide DWS with its left annular surface 12 engages over a right free end portion of the cylindrical pressure control slide DRS respectively comprises. While the Mel defiguration 1 1 forms the right free end face of the pressure control slide DRS, opposite a circular surface 1 6 with the same diam water on the inside of the pressure compensator slide DWS available. An et waiger control pressure pA, which comes from the user port A, is thus effective pressure on the reporting area 1 1 as well as on the circular surface 16 of the pressure compensator slide DWS.
  • the reporting or control pressure PA in pressure compensator operation to the areas 1 1 and 1 6 is further reported.
  • the free volume of the actual pressure reporting room Y changes.
  • the control pressure pA on the part of NutzanInstitutes in the Ist Kunststoff-reporting room Y wei ter meetings can serve a dashed reproduced reporting channel 7, the a center collar or annular collar reduced in diameter relative to the annular surfaces 9, 9 ', which in this respect is permanently in fluid communication with the service port A in connection.
  • At its other end of the pertinent message channel 7 opens for the actual or control pressure PA at the user port A in the actual pressure message room Y from.
  • a Dämp be fung aperture 8 connected.
  • the pressure compensator slide DWS is supported by a widened end-side flange surface on an energy store in the form of a pressure spring 14 for the pressure compensator, wherein the pertinent compression spring 14 is made relatively hard.
  • the spring 14 is supported with its the flange of the pressure compensator slide DWS stronglylie ing end of wall parts of a pertinent valve housing from. Fer ner is according to the illustration of FIG.
  • the pertinent compression spring 10 is supported with its one free end on the circular surface 1 6 of the pressure compensator slide DWS and with its other free end on the end face of a bore in the pressure control slide DRS.
  • a message room M in the valve housing is present, which, as seen in the direction of Fig. 2, on the left side of a reporting area 1 7 is limited, which forms the right free end face of Druckwaa genschiebers DWS in the region of its Flanschverbreiterung.
  • a measuring port 20 which leads in pressure compensator operation, the measuring pressure pM.
  • a relief notch 1 3 is introduced in the region of the main return port T on the left free end En de of the pressure compensator DWS, otherwise the thus free frontal End of the annular surface 12 is limited, which forwards the pressure pA on the user port A to the pressure balance slide DWS in pressure compensator operation.
  • a conical seat 1 9 for the pertinent pilot cone in unspecified Valve housing available.
  • the core idea of this valve concept according to the invention lies in the separation of the tasks pressure control and pressure compensator function, which are distributed to the two slides DRS and DWS, which are provided with independent energy storage in the form of the compression springs 10 and 14, wherein the compression spring 10 not only on the pressure compensator slide DWS on the circular area 1 6 acts, but also on a investment opportunity in the area of the other ring surface 9 'on the pressure control slide DRS.
  • the left slide or pressure control slide DRS realized the pressure control function, starting from the pressure supply port P to Druckan circuit A.
  • the soft spring 10 holds him in the rest position on the left to beat.
  • the pressure control slide DRS has three channels, wherein the pilot control channel 5 supplies the pilot stage with fluid (oil) from the pressure supply connection P.
  • the pilot control channel 5 supplies the pilot stage with fluid (oil) from the pressure supply connection P.
  • the pressure divider function of the pilot stage comes in the channel 5 either a diaphragm 3 used or integrated into the pressure control slide DRS miniature flow control valve (not shown).
  • An advantage of the latter solution is the lower and constant pilot current.
  • the control pressure in the control room before tax X from the supply pressure at port P is independent. However, this is offset by higher production costs.
  • a damping diaphragm 8 can be used here.
  • the further existing channel 6 as a compensation channel causes a pressure equalization between the gap Z, which is disposed between the terminals A and T, and the compensation chamber E.
  • the right slide or pressure compensator DWS works so far as a pressure compensator, which compares the pressure at the user port A with the pressure at the measuring port 20 and with the pressure in the reporting room M.
  • the resulting rule pressure difference is defined by the design of the hard spring 14 as the wide ren energy storage.
  • FIG. 3a, 3b and 3c represent different resting states of the combinati onsventils, wherein the unloaded resting state as shown in FIG. 3a shows the same valve state, as it is given in Fig. 2 again, and Fig. 3b gives a loaded rest state for the Ven valve again, whereas Fig. 3c shows the valve in the loaded state of rest and mecanicstromt.
  • Figs. 3a, 3b and 3c concern the possible rest conditions of the combination valve according to the invention, i. the conditions in which no fluid (oil) flows over the flow paths P-A or A-T.
  • unloaded th idle state Fig. 2 and 3a
  • the two slides DRS and DWS are located in the end positions defined by the springs 10 and 14 and the housing stops. In this case, the fluid-conducting connection between the pressure supply connection P and the utility port A is closed, the connection from the utility port A to the return port T fully open.
  • the loaded resting state according to the illustration of Fig. 3b is characterized by a load pressure at the measuring port 20 respectively in the notification room marked acts on the reporting area 1 7 on the right side of the carriage slide DWS on this.
  • the pending on the reporting area 1 7 pressure moves the pressure compensator slide DWS as shown according to the Fig. 3b in the left end position, which is defined for example by means of the annular stop 15.
  • the seat-tight holding of the load requires a seat-tight construction of a sealing point between the Mel deraum M to the return port T (not shown).
  • the fluid leading de connection between the user port A to the return port T is closed except for the geometrically small failing relief notch 1 3.
  • a Vorbestromung the actuating magnet which controls the pilot cone 18, makes sense.
  • a pilot pressure px adjusts, which acts on the reporting area 1 and shifts the pressure control slide DRS to the right until it closes the fluid-carrying connection from the utility A to the space Z.
  • PV proportional or check valve
  • FIGS. 4a and 4b now show the actual pressure control operation.
  • fluid flows from the pressure supply port P to Nutzan circuit A.
  • the pressure at the user port A corresponds to the pre-control room X using the pilot stage set target pressure minus the pressure difference corresponding to the spring force, the biased pressure control spring 10 to the pressure control piston or Pressure control slide DRS exerts.
  • the aforementioned pilot control stage is realized by components that are represented by the reference numerals 3, 5, 18 and 1 9.
  • the actual pressure pA at the user port A is reported via the reporting message channel 7 in the pressure control slide DRS on the right end face 1 1 in the inner space in the form of Ist Kunststoff-reporting room Y and with the help of the same large face 1 on the left side of Druckre gelschiebers DRS with the pilot pressure px in Vorêtraum X compare.
  • the geometry of the pressure control slide DRS is designed so that the space Y and thus the surface 1 1 is always connected via the message channel 7 with the user port A.
  • the pressure Weigh ge in one of its two end positions or possibly in between This only affects the spring force acting on the pressure control slide DRS and changes the control pressure at the utility connection A only minimally.
  • FIGS. 5a, 5b show the pressure control operation at saturation. If the setpoint pressure which is predetermined by the supply of the pilot solenoid at the pilot control valve 18 can not be achieved because a very large volume flow flows out of the utility connection A, no counterbalance action, even with full opening of the flow path from the pressure supply connection P to the utility connection A, is established. between the end faces 1 and 1 1 on the pressure control slide DRS. As a result, this moves so far to the right that he closes the angepro term fluid-carrying path P to A again, so that the payload connection pA continues to fall and the slider leaves the control range ver. This is prevented by means of the triangular notch 2 on the pressure control slide DRS.
  • the triangular notch 2 opens a connection from the pilot chamber X in the relief space E and from there via the equalization channel 6 and the gap Z in the return port T. It is to ensure constructively that the connection of relief or compensation chamber E to the return port T is also maintained when the pressure compensator is located on the left stop, which is shown in Fig. 5b. In this case, the relief notch 1 3 remains as Restöff voltage from the gap Z to the tank or return port T. The effluent via the notch 2 fluid (oil) lowers the pilot pressure px so far that a determined by the Nutzan gleichdruck pA equilibrium between the Nutzan gleichdruck pA and the pilot pressure p x . The pressure control slide DRS then remains in the effective range of the notch 2.
  • the stability of this state depends essentially on the selected Ker gegege. It is additionally to ensure that the Strömungswi resistances on the equalization channel 6 and the relief notch 1 3 are significantly smaller than the resistance over the notch 2. Their resistance must not exceed that of the fully open pilot cam seat 19.
  • the pressure balance slide DWS compares the working pressure pA with the measuring pressure pM, wel cher acts on the right circular surface 1 7 of the pressure compensator.
  • the surface 1 7 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 user port A to the tank or return port T at the throttle point between the gap Z and the return port T ge is throttled that adjusts the user port A, the measuring pressure pM minus the defined by the spring 14 control pressure difference DrM.
  • an electrohydraulic control system for hydraulic drives is created as a whole, which can operate in both directions in both motor and regenerative operation. Since a pilot operated Proportionalschieberventil is used, the function of a pressure reducer for the supply pressure control and a

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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)
  • Servomotors (AREA)

Abstract

L'invention concerne un dispositif de soupape comprenant : un raccord d'arrivée (ZA) d'un côté d'arrivée pour l'alimentation en fluide sous pression d'un consommateur hydraulique pouvant être raccordé au raccord d'arrivée (ZA) ; un raccord d'évacuation (AA) d'un côté d'évacuation pour l'évacuation du fluide sous pression hors du consommateur pouvant être raccordé, le côté d'arrivée pouvant être modifié en le côté d'évacuation et le côté d'évacuation en le côté d'arrivée selon le sens de pilotage dudit consommateur ; un raccord d'alimentation en pression (P) ; et un raccord de retour (T). Le dispositif est caractérisé en ce qu'un système de régulation de pression agit sur le côté d'arrivée respectif et un système de régulation de débit volumique agit sur le côté d'évacuation.
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 true EP3721094A1 (fr) 2020-10-14
EP3721094B1 EP3721094B1 (fr) 2022-06-01

Family

ID=65411864

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19705145.1A Active EP3721094B1 (fr) 2018-02-20 2019-02-07 Dispositif de soupape

Country Status (4)

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

Families Citing this family (3)

* Cited by examiner, † Cited by third party
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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
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

Also Published As

Publication number Publication date
DE102018001303A1 (de) 2019-08-22
EP3721094B1 (fr) 2022-06-01
WO2019162097A1 (fr) 2019-08-29
US20200378409A1 (en) 2020-12-03

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