EP3679254B1 - Soupape - Google Patents

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Publication number
EP3679254B1
EP3679254B1 EP18766189.7A EP18766189A EP3679254B1 EP 3679254 B1 EP3679254 B1 EP 3679254B1 EP 18766189 A EP18766189 A EP 18766189A EP 3679254 B1 EP3679254 B1 EP 3679254B1
Authority
EP
European Patent Office
Prior art keywords
valve
fluid
connection
control
valve housing
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.)
Active
Application number
EP18766189.7A
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German (de)
English (en)
Other versions
EP3679254A1 (fr
Inventor
Peter Bruck
Frank Schulz
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
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Publication of EP3679254A1 publication Critical patent/EP3679254A1/fr
Application granted granted Critical
Publication of EP3679254B1 publication Critical patent/EP3679254B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/021—Installations or systems with accumulators used for damping
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • F15B1/033—Installations or systems with accumulators having accumulator charging devices with electrical 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
    • 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
    • F15B13/026—Pressure compensating 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B2013/002—Modular valves, i.e. consisting of an assembly of interchangeable components
    • F15B2013/004—Cartridge 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50572—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using a pressure compensating valve for controlling the pressure difference across a flow 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
    • F15B2211/57—Control of a differential 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
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot pressure control
    • F15B2211/5753—Pilot pressure control for closing a 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/625—Accumulators
    • 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
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode

Definitions

  • the invention relates to a valve with the features in the preamble of claim 1.
  • the use of pressure compensators in hydraulically operating lifting devices is state of the art.
  • the document DE 102 02 607 C1 shows an example of the arrangement of a pressure compensator in a lifting device for lifting and lowering loads to influence the lowering behavior, the pressure compensator being arranged in a return line of a relevant lifting cylinder.
  • Another preferred application is the use in lifting devices that are equipped with a lifting mechanism damping that can be activated or deactivated.
  • a pressure compensator ensures that the accumulator pressure at an associated damping accumulator automatically follows the load pressure of the respective lifting mechanism cylinder, both when the lifting mechanism damping is activated and when the lifting mechanism is deactivated. This ensures that if the lifting mechanism damping is activated, after previously deactivated operation, no uncontrolled lifting or lowering of the lifting mechanism can take place.
  • valve with the features in the preamble of claim 1 with a valve housing which has a control connection and a fluid inlet and a fluid outlet, and with a Control piston arranged longitudinally displaceably in the valve housing, which, against the action of an energy store, in particular in the form of a compression spring, brings the control piston into at least one position forming a fluid-carrying connection between the fluid inlet and the fluid outlet by means of a control pressure prevailing at the control connection, or blocks this connection, in which Control piston a first orifice is arranged, which connects the control connection with a receiving space for the energy storage fluid-carrying, and wherein a second orifice is arranged in an intermediate part in the valve housing, by means of which the receiving space can be connected to a compensation space.
  • the invention is based on the object of providing a valve which is characterized by particularly favorable operating behavior as a pressure compensator for use in hydraulically operated lifting devices which are provided with lifting mechanism damping.
  • this object is achieved by a valve which has the features of claim 1 in its entirety.
  • an essential feature of the invention is that the valve is intended for use as a pressure compensator in hydraulically actuated lifting devices and that the compensation chamber is in fluid communication with the fluid outlet. Due to the arrangement of two diaphragms, which on the one hand lead from the control connection to the receiving space with the spring loading the control piston and, on the other hand, lead from the equalizing chamber leading the pressure of the fluid outlet to the receiving space, the valve represents a kind of piloted pressure compensator the two diaphragms with the spring arranged between them, the control pressure of the pressure compensator generated by the spring is increased.
  • the damping accumulator Since, due to the function of the pressure compensator, the pressure on the damping accumulator follows the load pressure on the lifting cylinder, the damping accumulator is automatically discharged when the lifting cylinder is lowered and is reloaded when it is lifted again.
  • the constant charging process which also takes place in the deactivated damping mode, i.e. with a functionless damping memory, requires pump power, which costs energy and which reduces the lifting speed.
  • an additional switching valve is used between the pump side and the pressure compensator, which blocks this connection in the deactivated damping mode and prevents the accumulator from charging in this mode.
  • the second diaphragm can be closed by means of a pilot control device which can be controlled by an actuating magnet. If an actuating magnet is used, the closing force of which is greater than the hydraulic force acting on the control piston, the pilot oil flow is prevented when the magnet is actuated and the control piston of the pressure compensator is therefore in the closed position, so that the pressure compensator is blocked.
  • a pilot control device which can be controlled by an actuating magnet. If an actuating magnet is used, the closing force of which is greater than the hydraulic force acting on the control piston, the pilot oil flow is prevented when the magnet is actuated and the control piston of the pressure compensator is therefore in the closed position, so that the pressure compensator is blocked.
  • the pilot control device has a pilot cone which interacts with a valve seat on the intermediate part and on which two energy stores, in particular in the form of compression springs, act in and against the effective direction of the actuating magnet.
  • the arrangement can advantageously be made in such a way that the compensation space is at least partially accommodated in the intermediate part, which establishes a fluid-conducting connection to a collecting space as a further part of the compensation space that is permanently connected to the fluid outlet via at least one fluid-conducting connection path Valve housing is in communication.
  • the actuation part of the actuation magnet is guided in a connection part of the actuation magnet provided for connecting the actuation magnet to the valve housing, which, at least partially, takes up one energy store of the pilot control device and connects to the intermediate part, the latter and the connection part being stationary on the valve housing are arranged.
  • control piston is designed as a hollow piston, at least in the area of the control connection and at least in the area in which, at least partially, the energy store is accommodated, with one orifice, designed as a screw-in piece, being inserted into the control piston, the two cavities of which permanently connected to each other in a fluid-carrying manner.
  • the orifice is designed as a screw-in piece, identical control pistons can be fitted with different orifices for the desired function adjustment.
  • the control piston can advantageously be provided with a stop part on the side of the intermediate part, which is in one and in the other Stop position can be brought into contact with the valve housing or with the intermediate part.
  • the arrangement can be made such that the control connection is introduced into the valve housing in the axial direction and the fluid inlet and the fluid outlet reach through the valve housing in the radial direction, the hollow piston on the outer circumference with the valve housing Limited annular space, which in the other stop position of the control piston completely passes over the fluid outlet.
  • the invention also relates to a device for damping the lifting mechanism, the device having the features of claim 10.
  • a hydraulically actuated lifting cylinder is denoted by 2, by means of whose working piston 4 a load 6 can be raised and lowered.
  • To control the lifting cylinder 2 its working spaces 8 and 10, which are separate from the working piston 4, are connected to a 4/3-way slide valve 12 which can be controlled by a relevant operator and which has a pressure supply connection P and a tank connection T leading to the tank side.
  • the lifting device is provided with a lifting mechanism damper 14, which is connected to the piston-side working space 8 via a connection point 16 and to the rod-side working space 10 of the lifting cylinder 2 via a connection point 18.
  • the lifting mechanism damping 14 has a hydropneumatic damping accumulator 20, the oil side 22 of which is connected at a connection point 24 to an accumulator line 26.
  • two electrically actuated switching valves 28 and 30 are provided, which can be switched against a mechanical restoring force into an open position to activate the lifting mechanism damping 14.
  • the switching valve 28 connects the piston-side working chamber 8 of the lifting cylinder 2 via the connection point 16 with the storage line 26.
  • the other switching valve 30 connects the rod-side working chamber 10 of the lifting cylinder 2 with a return line 32 leading to the tank side T in the open position Fig.
  • the switching valves 28 and 30 are in a switching position in the absence of electrical actuation in which the switching valve 28 with a check valve 34 blocks the fluid flow from the working chamber 8 to the storage line 26, but the fluid flow in allows reverse direction.
  • switching valve 30 blocks the fluid flow from the rod-side working chamber 10 of the lifting cylinder 2 to the return line 32 with a check valve 36, but enables the fluid flow in the opposite direction.
  • a pressure compensator 38 is inserted between the storage line 26 and the pressure supply connection P, the control connection 40 of which is connected via a control line 42 to the connection point 16, which is connected to the piston-side working chamber 8 of the lifting cylinder 2.
  • the load pressure of the working chamber 8 of the lifting cylinder 2 is therefore applied to the control connection 40 via the control line 42. Since the pressure compensator 38 is connected with its input 44 via a charging line 48 to the pressure supply connection P and with its output 46 to the accumulator line 26, the accumulator pressure of the damping accumulator 20 follows the load pressure of the working chamber 8 of the lifting cylinder 2.
  • the piston-side working chamber 8 of the lifting cylinder 2 is connected to the tank side T via the 4/3-way valve 12 during lowering operations.
  • the switching position shown of the switching valve 28 is therefore discharged via its check valve 34 during each lowering operation of the damping accumulator 20. Since the pressure of the damping accumulator 20 follows the load pressure in the working chamber 8 of the pressure cylinder 2 due to the function of the pressure compensator 38, the damping accumulator 20 is charged again via the charging line 48 with each new lifting process.
  • a switching valve 50 is inserted in the prior art in the charging line 48 between pressure compensator 38 and pressure supply connection P, which a charging current when lifting mechanism damping 14 is deactivated towards the Damping memory 20 prevents and only releases the charging line 48 when the lifting mechanism damping 14 is activated.
  • the charging line 48 is protected against a return flow in the direction of the pressure supply connection P by a check valve 52.
  • the diaphragm or throttle shown in the control line 42 and the diaphragm or throttle in the charging line 48 (each without a reference number) are used for improved control and coordination of the hydraulic circuit (likewise Fig. 3 ).
  • the Fig. 2 shows in a separate representation the design of the pressure compensator 38 according to a first embodiment of the invention.
  • the so-called cartridge design valve has a valve housing 54 with an open end 56 and an end which is closed in a pressure-tight manner by a screwed-in end piece 58.
  • the valve housing 54 can be installed in a valve block, not shown, in the manner customary for cartridge cartridges.
  • a guide cylinder 60 extends in the valve housing 54 to a spring receiving space 62 with an enlarged inner diameter of which the bores 64 closest to the open end 56 connect the fluid inlet 44 ( Fig. 1 ) and the other bores 66 the fluid outlet 46 ( Fig. 1 ) form.
  • the open housing end 56 forms the control connection 40 of the valve.
  • a control piston 68 is guided in a longitudinally displaceable manner, which is designed as a hollow piston and is loaded at its inner end by a compression spring 70 provided as an energy store.
  • the end of the compression spring 70 facing away from the control piston 68 is supported on an intermediate part 72, which on the one hand rests on a step 74 of the valve housing 54 and on the other hand rests on the end piece 58 in Is set in the axial direction and seals the spring receiving space 62 by means of a sealing device 76.
  • the in Fig. 2 As shown in the depressurized state, the control piston 68 is moved by the compression spring 70 into an end position in which the control piston 68 rests with an end stop part 78 on a housing step located at the end of the spring receiving space 62. In the other end position displaced against the force of the compression spring 70, the control piston 68 rests with the stop part 78 on the intermediate part 72.
  • the control piston 68 has an outer annular space 80 into which the fluid inlet 44 formed by the bores 64 opens and whose axially inner end forms a control edge 82.
  • the in Fig. 2 In the illustrated end position of the control piston 68, the depressurized state shown is the control edge 82 in front of the bores 66, so that the fluid outlet 46 is closed.
  • control edge 82 In the control position of the control piston 68 shifted against the force of the compression spring 70, the control edge 82 exposes the connection to the annular space 80, with the control edge 82 completely traversing the bores 66 of the fluid outlet 46 when the control piston 68 is in the right end position.
  • the control piston 68 designed as a hollow piston has, in the area adjoining the spring receiving space 62, an area tapered in internal diameter with an internal thread 84 into which a screw-in piece 86 is screwed, in which a first orifice 88 is located, which has the control input 40 the spring receiving space 62 connects.
  • a second panel 90 is formed which connects the spring receiving space 62 with a compensation space 92 located in the intermediate part 72, which in turn is connected via radial bores 94 with a collecting space 96, which is as Annular space between the outer circumference of the intermediate part 72 and the inside of the valve housing 54 is located.
  • the collecting space 96 is above inclined connecting sections 98 in the valve housing 54
  • Fluid ducts in the valve block, not shown, are connected to the fluid outlet 46 formed by the bores 66, so that the pressure of the damping accumulator 20 is effective on the second diaphragm 90 via the connecting paths 98, the collecting chamber 96 and the compensation chamber 92.
  • the combination of the two orifices 88 and 90 with the compression spring 70 in between forms a type of pilot control for the pressure compensator, the pilot oil flow flowing through the second orifice 90 increasing the control pressure generated by the compression spring 70.
  • the Fig. 3 shows how the Fig. 1 , the circuit of a hydraulically actuated lifting device, wherein the lifting mechanism damper 14 works with a pressure compensator according to a second embodiment of the valve according to the invention, which is shown in Fig. 4 is shown separately in longitudinal section.
  • the valve housing 54 of the second exemplary embodiment corresponds in construction to the first exemplary embodiment, as are the internal components, such as control piston 54 with first aperture 88, compression spring 70, intermediate part 72 as the closure of spring receiving space 62 and second aperture 90.
  • the compensation space 92 formed in the intermediate part 72 is not closed by a closed end piece 58, but is replaced by a connection part 102 screwed into the valve housing 54 for an actuating magnet 104.
  • the connection part 102 rests on the intermediate part 72 for its axial fixing.
  • the actuation magnet 104 has an axially displaceable actuation part 106 which, when the magnet 104 is energized, in Fig. 4 moves to the left.
  • the actuating part 106 which is guided displaceably in the connection part 102, extends into a chamber 108 formed in the connection part 102, which forms a continuation of the adjoining compensation space 92 in the intermediate part 72.
  • the actuating part 106 is used to control a pilot cone 110, for which a valve seat 112 is formed on the intermediate part 72. This is located on the intermediate part 72 in front of the access to the second panel 90, so that it can be closed by the pilot cone 110.
  • a third compression spring 120 is inserted between the pressure plate 118 and the intermediate part 72, the spring force of which is less than that of the other pressure spring 116 resting on the pressure plate 118.
  • the second diaphragm 90 can be closed by means of the pilot cone 110 when the magnet 104 is actuated, or can be released by means of the restoring force of the third compression spring 120 when the electromagnet 104 is not actuated.
  • the pilot oil flow is prevented, so that the control piston 68 closes the connection between the fluid inlet 44 and the fluid outlet 46.
  • the valve assumes not only the function of the pressure compensator 38 when the lifting mechanism damping 14 is activated, but also the function of the switching valve 50, which blocks the charging line 48, when the lifting mechanism damping 14 is deactivated Fig. 1 and replaces this.

Claims (11)

  1. Soupape comprenant un corps (54) de soupape, qui a un raccord (40) de commande ainsi qu'une entrée (64) de fluide et une sortie (66) de fluide, et comprenant un piston (68) de réglage, qui est monté déplaçable longitudinalement dans le corps (54) de la soupape et qui, à l'encontre de l'effet d'un accumulateur (70) d'énergie, notamment sous la forme d'un ressort de compression, met, au moyen d'une pression de commande régnant au raccord (40) de commande, le piston (68) de réglage dans au moins une position formant une communication fluidique entre l'entrée (40) de fluide et la sortie (66) de fluide ou obture cette communication, dans laquelle dans le piston (68) de réglage est disposé un premier obturateur (88), qui met le raccord (40) de commande en communication fluidique avec un espace (62) de réception de l'accumulateur (70) d'énergie, et dans laquelle un deuxième obturateur (90) est disposé dans une partie (72) intermédiaire du côté (54) de la soupape, obturateur (90) au moyen duquel l'espace (62) de réception peut être mis en communication avec un espace (92) de compensation, caractérisée en ce que la soupape est prévue pour être utilisée comme balance (38) manométrique dans des dispositifs (2) de levage à actionnement hydraulique et en ce que l'espace (92) de compensation est en communication (98) fluidique avec la sortie (66) de fluide.
  2. Soupape suivant la revendication 1, caractérisée en ce que le deuxième obturateur (90) peut être fermé au moyen d'un dispositif (110) pilote, qui peut être commandé par un aimant (104) d'actionnement.
  3. Soupape suivant la revendication 2, caractérisée en ce que le dispositif pilote a un cône (110) pilote, qui coopère avec un siège (112) de soupape de la partie (72) intermédiaire et qu'attaque, dans le sens contraire au sens d'actionnement de l'aimant (104) d'actionnement, deux accumulateurs (116, 120) d'énergie, notamment sous la forme de ressort de compression.
  4. Soupape suivant la revendication 1 ou 2, caractérisée en ce que l'espace (92) de compensation est reçu au moins en partie dans la partie (72) intermédiaire, qui ménage une communication (94) fluidique avec un espace (96) collecteur sous la forme d'une autre partie de l'espace (92) de compensation qui, par au moins une section (98) de communication fluidique, est en communication fluidique permanente avec la sortie (66) de fluide du corps (54) de la soupape.
  5. Soupape suivant la revendication 3, caractérisée en ce que la partie (106) d'actionnement de l'aimant (104) d'actionnement est guidée dans une partie (102) de raccord de l'aimant (104) d'actionnement, qui est prévue pour la liaison de l'aimant (104) d'actionnement au corps (54) de la soupape, qui, au moins en partie, reçoit le un accumulateur (116) d'énergie du dispositif (110) pilote et se raccorde à la partie (72) intermédiaire.
  6. Soupape suivant la revendication 5, caractérisée en ce que la partie (72) intermédiaire et la partie (102) de raccordement sont montées fixes sur le corps (54) de la soupape.
  7. Soupape suivant l'une des revendications précédentes, caractérisée en ce que le piston (68) de réglage est, au moins dans la partie du raccord (40) de commande et au moins dans la partie dans laquelle, au moins en partie, le un accumulateur (70) d'énergie est reçu, réalisé sous la forme d'un piston creux et en ce que le un obturateur (88), réalisé sous la forme d'une pièce (86) de vissage, est inséré dans le piston (68) de réglage, dont les deux espaces creux communiquent fluidiquement entre eux en permanence.
  8. Soupape suivant l'une des revendications précédentes, caractérisée en ce que le piston (68) de réglage est pourvu du côté de la partie (72) intermédiaire d'une partie (78) de butée, qui, dans la une et dans l'autre opposition de butée, peut être mise en contact avec le corps (54) de la soupape et respectivement avec la partie (72) intermédiaire.
  9. Soupape suivant la revendication 7 et la revendication 8, caractérisée en ce que le raccord (40) de commande est inséré dans le corps (54) de la soupape dans la direction axiale et l'entrée (64) de fluide et la sortie (66) de fluide traversent le corps (54) de la soupape dans la direction radiale et en ce que le piston creux délimite du côté du pourtour extérieur avec le corps (54) de la soupape un espace (80) annulaire, qui, dans l'autre position de butée du piston (68) de réglage, passe complètement sur la sortie (66) de fluide.
  10. Dispositif d'amortissement d'un dispositif d'amortissement (23) et de levage, comprenant une source (P) d'alimentation en pression, un dispositif (20) d'accumulation de pression, au moins un consommateur (2) hydraulique, notamment sous la forme d'un vérin de travail hydraulique, et une soupape suivant l'une des revendications précédentes, qui est raccordée, par un espace (8) de travail du consommateur (2) hydraulique, au raccord (40) de commande de la soupape, dont l'entrée (64) de fluide est raccordée à la source (P) d'alimentation en pression et dont la sortie (66) de fluide est raccordée au dispositif (20) d'accumulation de pression.
  11. Dispositif suivant la revendication 12, caractérisé en ce que le un espace (8) de travail, qui est raccordé au raccord (40) de commande de la soupape, est monté en même temps par un robinet (28) d'arrêt dans la communication (26) fluidique entre la soupape et le dispositif (20) d'accumulation de pression et en ce qu'un autre espace (10) de travail du consommateur (2) hydraulique est raccordé par un autre robinet (30) d'arrêt à un conduit (32) de retour menant au côté (T) réservoir.
EP18766189.7A 2017-09-06 2018-09-05 Soupape Active EP3679254B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017008359.2A DE102017008359A1 (de) 2017-09-06 2017-09-06 Ventil
PCT/EP2018/073823 WO2019048455A1 (fr) 2017-09-06 2018-09-05 Soupape

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EP3679254A1 EP3679254A1 (fr) 2020-07-15
EP3679254B1 true EP3679254B1 (fr) 2021-11-10

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EP18766189.7A Active EP3679254B1 (fr) 2017-09-06 2018-09-05 Soupape

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DE (1) DE102017008359A1 (fr)
WO (1) WO2019048455A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11781573B2 (en) 2020-07-23 2023-10-10 Parker-Hannifin Corporation System, valve assembly, and methods for oscillation control of a hydraulic machine

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3605980A1 (de) 1985-03-05 1986-10-16 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Proportionalventil mit druckdifferenzwaage
DE4140409A1 (de) * 1991-12-07 1993-06-09 Robert Bosch Gmbh, 7000 Stuttgart, De Elektrohydraulische steuereinrichtung
DE10202607C1 (de) 2002-01-24 2003-07-31 Hydac Fluidtechnik Gmbh Steuervorrichtung, insbesondere für den Einsatz bei hydraulisch arbeitenden Hubeinrichtungen
DE102005006321A1 (de) 2005-02-11 2006-08-17 Hydac Fluidtechnik Gmbh Ventil, insbesondere Proportinal-Druckbegrenzungsventil
DE102009049548A1 (de) * 2009-10-16 2011-04-21 Hydac Fluidtechnik Gmbh Ventilanordnung
CN103299087B (zh) * 2011-01-06 2016-07-06 日立建机株式会社 具有履带式行驶装置的作业机的液压驱动装置
DE102012010522A1 (de) * 2012-05-25 2013-11-28 Hydac Fluidtechnik Gmbh Ventil für Ventilanordnung
DE102012016457A1 (de) 2012-08-17 2014-02-20 Hydac System Gmbh Einrichtung zum Steuern des Ladezustandes mindestens eines Druckspeichers
DE102016012335A1 (de) 2016-10-14 2018-04-19 Hydac Fluidtechnik Gmbh Ventilvorrichtung sowie Druckregelsystem mit einer solchen Ventilvorrichtung

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DE102017008359A1 (de) 2019-03-07
WO2019048455A1 (fr) 2019-03-14
US20200347855A1 (en) 2020-11-05
EP3679254A1 (fr) 2020-07-15
US11268544B2 (en) 2022-03-08

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