EP3679254A1 - Soupape - Google Patents
SoupapeInfo
- Publication number
- EP3679254A1 EP3679254A1 EP18766189.7A EP18766189A EP3679254A1 EP 3679254 A1 EP3679254 A1 EP 3679254A1 EP 18766189 A EP18766189 A EP 18766189A EP 3679254 A1 EP3679254 A1 EP 3679254A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- valve
- fluid
- control
- connection
- 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.)
- Granted
Links
- 239000012530 fluid Substances 0.000 claims abstract description 42
- 230000006835 compression Effects 0.000 claims abstract description 18
- 238000007906 compression Methods 0.000 claims abstract description 18
- 238000004146 energy storage Methods 0.000 claims description 9
- 238000013016 damping Methods 0.000 description 19
- 230000006870 function Effects 0.000 description 6
- 238000000034 method Methods 0.000 description 4
- 230000003213 activating effect Effects 0.000 description 2
- 230000000903 blocking effect Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 241000935974 Paralichthys dentatus Species 0.000 description 1
- 238000009825 accumulation Methods 0.000 description 1
- 230000006399 behavior Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000007639 printing Methods 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
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, in particular for use as a pressure compensator in hydraulically actuated lifting devices, with a valve housing having a control port and a fluid inlet and a fluid outlet, and with a longitudinally movable in the valve housing control piston, against the action of an energy storage device, in particular Form of a compression spring, by means of a prevailing at the control terminal control pressure brings the control piston in at least one fluid-conducting connection between the fluid inlet and the fluid outlet forming position or blocks this connection.
- an energy storage device in particular Form of a compression spring
- pressure compensators in hydraulically operated lifting devices is state of the art.
- the document DE 10202607 C1 shows by way of example the arrangement of a pressure compensator in a lifting device for raising and lowering loads for influencing the lowering behavior, wherein the pressure compensator is arranged in a return line of a respective lifting cylinder.
- Another preferred application is the use in lifting devices that are equipped with an activatable or deactivatable Hubtechniksdämpfung.
- the invention has the task of providing a valve that is characterized by a particularly favorable performance as a pressure compensator for use in hydraulically operated lifting devices, which are provided with Hubwerksdämpfung. According to the invention this object is achieved by a valve having the features of claim 1 in its entirety.
- a wesentl Ie special feature of the invention is that in the control piston, a first diaphragm is arranged, which connects the control port with a receiving space for the energy storage fluid, and that a second diaphragm is arranged in an intermediate part in the valve housing , by means of which the receiving space can be connected to a compensation chamber, which is in fluid-conducting connection with the fluid outlet.
- the valve is a kind of pilot-operated pressure compensator by the combination of both diaphragms with the spring arranged therebetween is the control pressure generated by the spring
- the second diaphragm can be closed by means of a pilot control device, which can be actuated by an actuating magnet.
- a pilot control device which can be actuated by an actuating magnet.
- the pilot control device on a pilot cone which cooperates with a valve seat on the intermediate part and on the in and against the effective direction of the actuating magnet two energy storage, in particular in the form of compression springs, attack.
- the arrangement can be made in such a way that the compensation chamber is at least partially accommodated in the intermediate part which produces a fluid-conducting connection to a collecting chamber as a further part of the compensation chamber, which permanently carries fluid via at least one fluid-carrying connection path to the fluid outlet in the valve housing communicates.
- the actuating part of the actuating magnet is guided in a provided for the connection of the actuating magnet with the valve housing connecting part of the actuating magnet, which receives, at least partially, an energy storage of the pilot control device and then to the intermediate part, the latter and the connecting part stationary on Valve housing are arranged.
- the control piston at least in the region of the control connection and at least in the region in which, at least partially, an energy storage is included, designed as a hollow piston, wherein the one orifice, designed as Einschraub congress used in the control piston, the two cavities permanently fluid-conducting connects to each other.
- the aperture as Einschraub Federation identical control piston for the desired function adjustment can be equipped with ample defencel cal aperture.
- control piston may be provided on the side of the intermediate part with a stop member, the ment in one and in the other stop Stel in contact with the valve housing or with the intermediate part can be brought.
- the arrangement can be made such that the control connection is introduced in the axial direction into the valve housing and the fluid inlet and the fluid outlet in radial direction to pass through the valve housing, wherein the hollow piston outside circumference with the valve housing defines an annular space which completely overflows the fluid outlet in the other stop position of the control piston.
- the invention also relates to a device for Hubwerksdämpfung for at least one hydraulic consumer, in particular in the form of a hydraulic working cylinder, wherein the device has the features of claim 10.
- 1 is a symbol view of the circuit of a hydraulically actuated, provided with a Hubtechniksdämpfung lifting device.
- Fig. 2 shows a comparison with a practical embodiment, for example
- FIG. 3 is a symbol view of the circuit of a hydraulically operated ble, provided with a Hubtechniksdämpfung lifting device which has a valve according to a second embodiment of the invention as a pressure compensator;
- Fig. 4 is a longitudinal section of the second embodiment of the valve according to the invention.
- a hydraulically actuated lifting cylinder is denoted by 2, by means of which working piston 4, a load 6 can be raised and lowered.
- 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 respective 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 Hubtechniksdämpfung 14, which is connected via a connection point 1 6 with the piston-side working space 8 and a connection point 18 with the rod-side working space 10 of the lifting cylinder 2.
- the hoist damping 14 has, according to the prior art, a hydro-pneumatic damping memory 20, whose oil side 22 is connected at a connection point 24 with a storage line 26.
- a hydro-pneumatic damping memory 20 whose oil side 22 is connected at a connection point 24 with a storage line 26.
- two electrically actuated switching valves 28 and 30 are provided, the force against a mechanical reset in a passage position for activating the Hubtechniksdämpfung 14 are switchable.
- 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 in the passage position the rod-side working space 10 of the lifting cylinder 2 with a leading to the tank side T return line 32.
- the switching valves 28 and 30 are in the absence of electrical operation in a switching position in which the switching valve 28 with a check valve 34 blocks the fluid flow from the working space 8 to the storage line 26, the Fluke idstrom but in the reverse direction allows.
- the other Druckven- til 30 locks in this switching position with a check valve 36, the fluid flow from the rod-side working space 10 of the lifting cylinder 2 to Return line 32, however, allows the fluid flow in the reverse direction.
- a pressure compensator 38 is inserted between the storage line 26 and the pressure supply port P, the control port 40 via a control line 42 to the connection point 1 6 in conjunction, which is connected to the piston-side working chamber 8 of the lifting cylinder 2. Therefore, the load pressure of the working space 8 of the lifting cylinder 2 is 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 port P and with its output 46 to the storage 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 of the switching valve 28 shown in Fig. 1 therefore takes place via the check valve 34, a discharge of the damping memory 20 at each lowering operation. Since the pressure of the damping accumulator 20 by the function of the pressure compensator 20 follows the load pressure in the working chamber 8 of the printing cylinder 2, a new charging process of the damping accumulator 20 takes place with each new lifting operation via the charging line 48.
- a switching valve 50 is inserted, which is deactivated when Hubwerkdsämpfung 14 prevents a charging current in the direction of the damping memory 20 and only when activated Hubtechniksdämpfung 14 the Charging line 48 releases.
- the charge line 48 is protected by a check valve 52 against a return current in the direction of the pressure supply port P.
- the aperture or throttle shown in FIG. 1 in the control line 42 as well as the aperture or throttle in the loading line 48 are used for improved control and coordination of the hydraulic circuit (also FIG. 3).
- Fig. 2 shows in a separate presen- tation the formation 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 a pressure-tight end closed by a screwed end 58 on. With its in Fig. 2 l inks departmenten housing section, the valve housing 54 in cartridge cartridges usual manner in a valve block, not shown, can be installed. From the open end 56 forth in the valve housing 54 extends a mecanicszyl indians 60 to an enlarged inside diameter spring receiving space 62.
- the valve housing 54 In the area of enterprisesszyl inder 60, the valve housing 54 axially staggered holes 64 and 66, the access to the investigatingszyl inder 60 and of which the boreholes 64 closest to the open end 56 form the fluid inlet 44 (FIG. 1) and the other bores 66 form the fluid outlet 46 (FIG. 1).
- the open housing end 56 forms the control port 40 of the valve.
- a control piston 68 is guided longitudinally movable, which is designed as a hollow piston and is loaded at its innenl end near end by an energy accumulator provided as a compression spring 70.
- the rule of the piston 68 facing away from the end of the compression spring 70 is supported on an intermediate part 72, which is fixed on the one hand by contact with a step 74 of the valve housing 54 and on the other hand by abutment on the end piece 58 in the axial direction and the spring receiving space 62 by means of a sealing device 76 seals.
- the control piston 68 is moved by the compression spring 70 in an end position in which the control piston 68 rests with an end-side stop member 78 at a located at the end of the spring receiving space 62 housing stage. In the shifted against the force of the compression spring 70 other end position of the control piston 68 abuts with the stop member 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. In the pressure-free state shown in FIG. 2, in the illustrated end position of the control piston 68, the control edge 82 is located in front of the bores 66, so that the fluid outlet 46 is closed.
- control edge 82 When the control piston 68 is displaced against the force of the compression spring 70, the control edge releases the connection to the annular space 80, wherein the control edge 82 completely overflows the bores 66 of the fluid outlet 46 when the control piston 68 is in the right end position.
- the designed as a hollow piston control piston 68 has in the adjoining the spring receiving space 62 area an inner diameter tapered portion with an internal thread 84 into which a Einschraub Scientific 86 is screwed, in which there is a first aperture 88, which the control input 40 with the spring-receiving space 62 connects.
- a second aperture 90 is formed, which connects the spring receiving space 62 with a located in the intermediate part 72 compensation chamber 92, which in turn via radial bores 94 with a collecting space 96 in connection, which is known as Annular space between the outer periphery of the intermediate part 72 and the inside of the valve housing 54 is located.
- the Venti lgetude 54 of the second embodiment corresponds in construction to the first embodiment, as well as the inner components, such as control piston 54 with first aperture 88, compression spring 70, intermediate portion 72 as a conclusion of the spring-receiving space 62 and second aperture 90.
- the compensation chamber 92 formed in the intermediate part 72 is not closed off by a closed end piece 58, but is replaced by a connecting part 1 02 screwed into the valve housing 54 for an actuating magnet 10 04.
- the connecting part 1 02 abuts the intermediate part 72 for its axial fixing.
- the actuation magnet 104 has an axially movable actuation part 106 which, when the magnet 104 in FIG. 4 is energized, moves to the left.
- the displaceably guided in the connector part 1 02 operating part 106 extends into a formed in the connection part 1 02 chamber 108, which forms a continuation of the subsequent expansion space 92 in the intermediate part 72.
- the actuating member 1 06 is used to control a pilot cone 1 1 0, for the intermediate part 72, a valve seat 1 1 2 is formed. This is located on the intermediate part 72 before access to the second aperture 90, so that it can be closed by the pilot cone 1 10.
- the actuating member 106 is located with its free end to a located in the chamber 108 pressure piece 1 14 at which a second compression spring 1 1 6 is supported with its one end, with its other end to a
- Pressure plate 1 18 rests, which forms an enlarged diameter, rear part of the valve plug 1 10.
- a third compression spring 120 is inserted between the pressure plate 1 18 and the intermediate part 72, the spring force is lower than that of the other, on the pressure plate 1 18 applied compression spring 1 1 6.
- the second aperture 90 is closed with actuated magnet 104 by means of the pilot cone 1 10 or releasable with non-actuated solenoid 104 by means of the restoring force of the third compression spring 120.
- the pilot oil flow is suppressed, so that the control piston 68 closes the connection between the fluid inlet 44 and fluid outlet 46.
- the valve assumes not only when activated Hubwerksdämpfung 14, the function of the pressure compensator 38, but with deactivated Hubtechniksdämpfung 14 additionally the function of the charging line 48 blocking switching valve 50 of FIG. 1 and replace this.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- General Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Transportation (AREA)
- Combustion & Propulsion (AREA)
- Civil Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Geology (AREA)
- Fluid-Pressure Circuits (AREA)
- Safety Valves (AREA)
Abstract
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 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3679254A1 true EP3679254A1 (fr) | 2020-07-15 |
EP3679254B1 EP3679254B1 (fr) | 2021-11-10 |
Family
ID=63528748
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP18766189.7A Active EP3679254B1 (fr) | 2017-09-06 | 2018-09-05 | Soupape |
Country Status (4)
Country | Link |
---|---|
US (1) | US11268544B2 (fr) |
EP (1) | EP3679254B1 (fr) |
DE (1) | DE102017008359A1 (fr) |
WO (1) | WO2019048455A1 (fr) |
Families Citing this family (1)
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)
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 |
WO2012093703A1 (fr) * | 2011-01-06 | 2012-07-12 | 日立建機株式会社 | Transmission hydraulique d'engin de travaux équipé d'un dispositif d'avance de type chenilles |
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 |
-
2017
- 2017-09-06 DE DE102017008359.2A patent/DE102017008359A1/de not_active Withdrawn
-
2018
- 2018-09-05 WO PCT/EP2018/073823 patent/WO2019048455A1/fr unknown
- 2018-09-05 EP EP18766189.7A patent/EP3679254B1/fr active Active
- 2018-09-05 US US16/643,892 patent/US11268544B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
WO2019048455A1 (fr) | 2019-03-14 |
EP3679254B1 (fr) | 2021-11-10 |
US20200347855A1 (en) | 2020-11-05 |
DE102017008359A1 (de) | 2019-03-07 |
US11268544B2 (en) | 2022-03-08 |
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