EP4074986B1 - Soupape - Google Patents

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Publication number
EP4074986B1
EP4074986B1 EP22162366.3A EP22162366A EP4074986B1 EP 4074986 B1 EP4074986 B1 EP 4074986B1 EP 22162366 A EP22162366 A EP 22162366A EP 4074986 B1 EP4074986 B1 EP 4074986B1
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EP
European Patent Office
Prior art keywords
pressure
valve
piston
fluid
spring
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
EP22162366.3A
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German (de)
English (en)
Other versions
EP4074986A1 (fr
Inventor
Peter Bruck
Frank Niehren
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Hydac Fluidtechnik GmbH
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Hydac Fluidtechnik GmbH
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Publication of EP4074986A1 publication Critical patent/EP4074986A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • F15B13/024—Pressure relief valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • 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
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5157—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and a 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/521—Pressure control characterised by the type of actuation mechanically
    • F15B2211/522—Pressure control characterised by the type of actuation mechanically actuated by biasing means, e.g. spring-actuated
    • 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
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves

Definitions

  • the invention relates to a valve with the features in the preamble of claim 1.
  • a directional control valve is known with a pressure compensator arranged in the housing, which is connected on the inlet side to a pressure supply channel in the housing and on the outlet side to at least one connecting channel to the slide bore, and in which a useful flow limiting device is also provided with at least one throttle element engaging in the connecting channel downstream of the control orifice of the pressure compensator. Since the throttle element of the useful flow limiting device already acts upstream of the slide bore, the load pressure can be tapped at any suitable point within the housing in the known solution, with both the pressure compensator and the useful flow limiting device being accommodated in the valve housing to save space.
  • Load-sensing systems are regularly used in mobile hydraulics, which achieve a flow rate independent of the load pressure and thus a sensitive speed control of the consumer.
  • the pressure difference is kept constant across a directional valve by connecting individual pressure compensators to the individual consumer connections. which throttle the system pressure, ie the pressure of the highest load in the system, to the respective consumer pressure.
  • WO98/21485 A1 a valve arrangement for supplying at least one consumer in a manner adapted to pressure and volume flow, which can be supplied with hydraulic fluid via two working connections of a continuously adjustable directional control valve or can be connected to a tank.
  • the two working connections of the known valve arrangement are assigned a common pressure compensator, the piston of which is guided axially displaceably in an axial bore of the directional control valve slide, so that with suitable control of the directional control valve, one of the two working connections can optionally be connected to the pump connection as the pressure connection.
  • a control pressure acts on both end faces of the directional control valve slide and on the spring side of the pressure compensator piston, which corresponds, for example, to the highest system load pressure, the individual load pressure or a pressure derived from it.
  • a seat valve with a circulation valve and pressure compensator function is known, with a control piston for interrupting a connection between a fluid inlet and a fluid outlet, the fluid inlet being provided for connection to a pressure line and the fluid outlet being provided for connection to a line with a lower pressure than the pressure in the pressure line, a first pressure of the pressure line acting on a first application surface of the control piston and a second pressure in a control line acting on a second application surface of the control piston in the opposite direction to the force acting on the first application surface.
  • Hydraulic control systems of this kind with pressure and volume flow adjustment to the current requirements of one or more consumers are implemented in so-called load-sensing systems, usually using a constant pump for the pressure supply and with a pressure compensator.
  • the highest in the system The pressure that occurs in the lines to the actuators, such as hydraulic cylinders or hydraulic motors, is fed back to an input pressure compensator and compared with the system pressure that the pump is currently delivering.
  • the system pressure and volume flow are then regulated according to requirements and any volume flow that is not required with system pressure is discharged to the tank via the pressure compensator.
  • the DE 101 20 643 A1 describes a valve with a valve housing and a valve piston which is guided longitudinally therein and which, under the action of a valve spring, blocks a fluid-carrying connection between a pressure connection and a tank connection in the valve housing in its closed position and releases it in an open position and which has a Orifice which establishes a permanent fluid connection on the pressure port side with a spring chamber containing the valve spring.
  • the EN 10 2012 010 522 A1 describes a valve with the features in the preamble of claim 1 with a valve housing and a valve piston which is guided longitudinally therein and which, under the action of a valve spring, blocks a fluid-carrying connection between a pressure connection and a tank connection in the valve housing in its closed position and releases it in an open position and which has an orifice which establishes a permanent fluid connection on the side of the pressure connection with a spring chamber with the valve spring, and with a load-sensing connection in the valve housing which opens into the spring chamber, wherein a pressure reduction device is accommodated in the valve housing which, in the event of a lack of pressure at the load-sensing connection, connects the spring chamber of the valve piston to the tank connection in a fluid-carrying manner.
  • the invention is based on the object of creating a valve which provides a solution to the above-mentioned problem.
  • the pressure reduction device is accommodated in a screw-in housing that can be screwed in via a free end face of the valve housing that is opposite the other end face with the pressure connection.
  • a standard valve housing which is preferably designed as a screw-in or cartridge valve.
  • a pressure reduction device is incorporated in the valve housing, which connects the spring chamber of the valve piston with the tank connection in a fluid-carrying manner when there is no pressure at the load sensing connection, the system pressure is significantly reduced when idling; however, the required load sensing ⁇ p is automatically generated when the working hydraulics are activated.
  • the valve according to the invention is based on the basic principle of a semi-pilot-controlled pressure compensator, which has no closing element on the pilot control.
  • the valve piston which is acted upon in a spring chamber by means of a valve spring and is the main piston of the valve, compares the differential pressure between the load sensing connection and the tank connection. When idling, this difference is known to be zero and the pressure reduction device that is then used relieves the spring chamber behind the valve or main piston and the pump pressure of the pressure supply in the form of a constant pump is reduced accordingly.
  • a valve (throttle valve) is actuated, which establishes the fluid connection and thus the pressure supply between a hydraulic pump, such as a constant pump, and a hydraulic consumer, such as a hydraulic working cylinder.
  • a hydraulic pump such as a constant pump
  • a hydraulic consumer such as a hydraulic working cylinder.
  • the relief of the valve or main piston back in the area of the associated spring chamber is interrupted and the load sensing ⁇ p can rise again to the required value.
  • the pressure compensator then works again as usual with a standard pressure compensator.
  • the valve solution according to the invention is also advantageous in that it is designed to be interchangeable with a commercially available standard circulating pressure compensator used in a hydraulic supply circuit.
  • the pressure reduction device has a longitudinally movable pressure reduction piston, which with its one free end delimits a further spring chamber with a pressure piston spring and which can be controlled by the pressure in a further load-sensing connection in the valve housing, which preferably opens into a fluid chamber that is connected to the first load-sensing connection.
  • the spring-loaded pressure reduction piston is installed in the spring chamber of the valve piston in the operating sequence behind the valve spring and in idle mode, when the load-sensing pressure is zero bar, the pressure piston spring can move the pressure reduction piston into a rear travel position while simultaneously relieving the spring chamber behind the valve piston.
  • a first fluid channel is introduced into the screw-in housing, which, when released by the pressure reduction piston, creates a fluid-carrying connection between the one and the other spring chamber. It is also preferably provided that a second fluid channel is introduced into the screw-in housing, which creates a fluid-carrying connection between the other spring chamber and the tank via a connecting channel running in the valve housing in every direction of travel of the pressure reduction piston. And in a further advantageous manner, it is provided that a third fluid channel is introduced into the screw-in housing, which connects the fluid chamber to the other load sensing connection.
  • this design arrangement ensures that when load sensing pressure is applied to the valve, the pressure reduction piston is moved into its position blocking the fluid-carrying connection between the spring chambers, contrary to the spring action of the pressure piston spring, which is equivalent to deactivating the pressure reduction device, with the result that the valve piston is exposed to the load sensing pressure on its side facing the spring chamber and thus controls the fluid flow from the pump pressure connection to the tank connection.
  • the load sensing ⁇ p increases again to the desired high value and the function of a standard pressure compensator is realized.
  • the respective orifice is designed as a screw-in orifice with different orifice geometries, which can be interchangeably inserted in the valve piston or in the valve housing.
  • the valve according to the invention can be adapted to a large number of fluid supply applications within the framework of a modular valve structure by adapting the orifice geometries.
  • the pressure reduction device relieves the pressure behind the first orifice in the valve piston towards the tank. This means that the pressure at the pressure connection of the valve housing is not completely relieved because the spring force of the valve spring acting on the valve piston must still be applied to the valve piston as ⁇ p. It is particularly important that the series connection of the two orifices, i.e. the first and further Orifice one behind the other, in regular LS operation both reduce the same ⁇ p, with the same size orifice one behind the other. This halves the spring force required compared to a conventional pressure compensator. The prerequisite for this is that a permanent pilot oil flow flows through the two orifices mentioned from the pressure connection of the valve to the first load sensing connection in the valve housing. By relieving the spring chamber behind the first orifice in the valve piston, it can achieve a reduction to half the usual load sensing ⁇ p value when idling.
  • the second orifice is chosen to have a slightly smaller free orifice cross-section than the first orifice in the valve piston, the figure can even be below 50% because the spring can be made even smaller.
  • valve according to the invention is connected to the output side of the pressure supply device and that the valve receives the highest pressure at the shuttle valve as load-sensing pressure.
  • the Fig.1 shows a basic representation of a hydraulic supply circuit for controlling a hydraulic consumer, here for the sake of simplicity in the form of a hydraulic differential cylinder 10 as an actuator or as a hydraulic working cylinder.
  • the said differential cylinder 10 has a piston rod unit 12 which divides the housing of the differential cylinder 10 into two fluid spaces, one in the form of a piston space 14 and one in the form of a rod space 16.
  • a pressure supply device 18 in the form of a so-called constant pump is used to supply pressure to the hydraulic working cylinder 10. Furthermore, a return line 20 is provided, via which excess fluid is discharged to a tank T, via which the pressure supply device 18 regularly removes working fluid in the form of hydraulic oil and feeds it under a predeterminable pressure into the supply circuit for supplying the differential cylinder 10.
  • a main control valve 22 is used, here for the sake of simplicity in the form of an electromagnetically actuated 4/3-way valve, which is in the Fig.1 shown in its locking neutral position. If viewed in the direction of the Fig.1 seen, the main control valve 22 moves into its right operating position, fluid of a predeterminable pressure from the pressure supply device 18 passes through the valve 22 into the piston chamber 14 and the piston rod unit 12 accordingly extends to the right. The fluid displaced from the rod chamber 16 then passes through the valve 22 into the return line 20 and thus to the storage tank T. If the valve 22 assumes its left-hand circuit diagram, fluid under pressure enters the rod chamber 16 and the piston chamber 14 is relieved via the return line 20 to the tank T. In this way, the piston rod unit 12 retracts to the left. In practice, however, proportional throttle valves with comparable valve positions are regularly used for the main control valve 22.
  • a shuttle valve 24 is connected to the inlet and outlet lines to the hydraulic working cylinder 10, which passes the highest pressure to a load-sensing line 26.
  • the fluid pressure is therefore highest on the piston side 14 and therefore at connection 3, so that the closing ball of the shuttle valve 24 is in its right closed position for the purpose of blocking the fluid supply line 1.
  • the fluid pressure relating to the piston chamber 14 is thus present via the line sections 3, 2 in the load sensing line 26.
  • the pressure in the rod chamber 16 is higher than the pressure in the piston chamber 14, with the result that the closing ball then moves in the direction of the Fig.1 seen to the left and closes off connection 3. In this way, fluid with the pressure in the rod chamber 16 then passes via line sections 1 and 2 into the load sensing line 26.
  • a pressure supply line 30 opens into the pressure connection 32 of a valve, as shown in Fig.2
  • the pressure at the pressure port 32 of the valve acts via a control line 34 on a valve piston 46 which is longitudinally movable in a valve housing 44 and which, with its opposite Control side is exposed to the counterforce from the load sensing line 26.
  • the valve piston 46 is held in its closed position by means of a valve spring 40, in which the pressure supply line 30 is blocked from a further return line 42 to the tank T.
  • the valve designed as a proportional valve as a pressure compensator comes into a regulating throttling position regarding the discharge flow from the pressure supply line 30 in the direction of tank T.
  • the valve shown is used to regulate the system pressure in a load-sensing system that is operated with a constant pump 18.
  • the valve in the form of a pressure compensator receives the maximum consumer pressure from the load-sensing system as an input variable via the load-sensing line 26.
  • the valve shown in Fig.1 The valve shown according to the state of the art accordingly has the task of increasing the pump pressure by a defined value above this value and the resulting difference is called load sensing ⁇ p.
  • This ⁇ p is required in order to achieve a uniform speed control for the differential cylinder 10 at the control edges of the directional control valve in the form of the main control valve 22 with always the same differential pressure conditions.
  • the valve after the Fig.2 has a valve housing 44 and a valve piston 46 which is guided longitudinally therein and which, under the action of the valve spring 40 in the form of a compression spring, is in its Fig.2 shown position and thereby blocks a possible fluid-carrying connection between the pressure connection 32 and a tank connection 48 in the valve housing 44.
  • the tank connection 48 can preferably consist of through holes arranged in pairs diametrically opposite to the longitudinal axis 50 in the valve housing 44, wherein according to the illustration according to the Fig.2 , only two of these opposite holes are shown.
  • the inner free end of the tank connection 48 is overrun by the outer peripheral side of the valve piston 46 and the other free end of the tank connection 48 opens into a tank-side drain chamber 52 into which the return line 42 to the storage tank T opens.
  • the Fig.2 The valve shown as a whole is designed as a so-called screw-in valve or cartridge valve and can be screwed into a valve block (not shown) or the like in a cartridge-like manner via a screw-in section 54.
  • the valve has sealing and guide rings on its outer circumference, with the discharge chamber 52, which runs radially concentrically to the longitudinal axis 50, being accommodated between two such sealing sets.
  • a diaphragm 56 is accommodated in the middle, which creates a permanent fluid connection on the side of the pressure connection 32 with a spring chamber 58 with the valve spring 40.
  • the valve spring 40 rests with its one free end in the direction of view on the Fig.2 seen, on the right side of the valve piston 46 and with its left free end on a free front side of a screw-in housing 60, which is also in the Type of a screw-in cartridge is screwed over the free front side into the valve housing 44 via a further screw-in section 62.
  • the pressure connection 32 according to the illustration after the Fig.1 also the pressure in the control line 34, which acts against the pressure in the load sensing line 26.
  • valve housing 44 is penetrated by a load sensing connection 64, which is designed as an oblique bore with one free end opening into the spring chamber 58 and with its other end into a fluid chamber 66, which is delimited by two sealing arrangements on the outer circumference of the valve housing 44 and is formed from a recess on the outer circumference of the valve housing 44.
  • the load sensing line 26 opens into this fluid chamber 66.
  • the oblique bore 64 forms, together with the valve housing 44, at the point of transition to the spring chamber 58 by reducing its free cross section, an orifice 67, which in a preferred embodiment (not shown) can also be interchangeably accommodated in the valve housing 44 in order to realize different orifice geometries.
  • a pressure reduction device 68 is provided as a whole in the valve housing 44 and thus also as an integral component of the screw-in housing 60, which connects the spring chamber 58 to the tank connection 48 or to the tank-side drain chamber 52 in a fluid-conducting manner in the event of a lack of control pressure at the load sensing connection 26.
  • the pressure reduction device 68 in the screw-in housing 60 has a first fluid channel 70, which with its first section 72 opens with one free end into the spring chamber 58 and with its other free end into a transverse bore 74 in the screw-in housing 60 as the second section of the fluid channel 70.
  • the transverse bore 74 opens with its one free end into a further spring chamber 76, through which a pressure piston spring 78 passes.
  • This pressure piston spring 78 is supported with its one free end in extension of the valve spring 40 and in coaxial arrangement to the longitudinal axis 50 on an inner end wall of the screw-in housing 60 and with its other free end on a pressure reduction piston 80 which, as a component of the pressure reduction device 68, is guided in a hollow cylindrical recess in the screw-in housing 60 and sealed on the outer circumference.
  • the pressure reduction piston 80 is shown in its rear travel position, in which it rests with a pin-like stop part 82 on an end wall of the recess within the screw-in housing 60.
  • the other free end of the transverse bore 74 opens into a circumferential annular gap 84, which is formed on the inner circumference by an outer wall of the screw-in housing 60 and is delimited on the outer circumference by an inner wall of the valve housing 44.
  • a second fluid channel 86 is introduced into the screw-in housing 60, which opens with one free end into the second spring chamber 76 and with its other free end into an obliquely running connecting channel 88, which in this respect establishes the connection between the second spring chamber 76 and the tank-side discharge chamber 52, into which the tank connection 48 in the valve housing 44 also opens.
  • the first spring chamber 58 is connected to the tank side T in a fluid-conducting manner via the longitudinal bore 72 and the transverse bore 74 as parts of the first fluid channel 70 and via the second spring chamber 76, the second fluid channel 86 and the obliquely running connecting channel 88.
  • the receiving chamber is provided in the form of the annular gap 84.
  • the pressure reduction piston 80 with its stop part 82 delimits a further fluid chamber 90, into which a third fluid channel 92 in the screw-in housing 60 opens, which passes the pressure from the first fluid chamber 66 and thus from the load-sensing line 26 to the further second fluid chamber 90 on the back of the pressure reduction piston 80 via a further inclined bore 94 as the further load-sensing connection.
  • the fluid pressure in the load-sensing line 26 serves both the connection 64 and the connection 90 via the common fluid chamber 66, which is recessed along the outer circumference of the valve housing 44 and into which the load-sensing line 26 opens with its one free end.
  • the pressure reduction piston 80 has, on its side opposite the stop part 82, a further stop part 96 which, in a fully compressed position of the pressure piston spring 78, may strike the front, inner end wall of the screw-in housing 60, which in this respect also delimits the second spring chamber 76.
  • the pressure-reducing piston 80 is moved to its position in the pressure port 32 by means of the constant pump 18 under a predeterminable pump pressure under the spring action of the pressure piston spring 78.
  • Fig.2 shown rear position and thereby releases the fluid-carrying connection between the two spring chambers 58, 76 via the channels already mentioned.
  • a load-sensing pressure is created and this is initially relieved via the connection 64 and the fluid guide 70, 72, 74, 76, 86, 88, 52 to the tank T.
  • the pressure is then discharged via the fluid chamber 66 into the further
  • the load sensing pressure introduced into the additional fluid chamber 90 through the load sensing connection in the form of the inclined bore 94 then leads, when the additional spring chamber 76 is kept pressureless, to the pressure reduction piston 80 being moved from its position in the Fig.2 shown stop position to the right and in doing so passes over the transverse bore 74 with its outer circumference and in this respect prevents the pressure reduction described above via the load sensing connection 64 to the tank T.
  • the pressure reduction piston 80 moves, as explained, against the spring action of the pressure piston spring 78 into its position blocking the fluid-carrying connection between the spring chambers 58 and 76 and the proportional control of the fluid flow from the pump pressure connection 32 to the tank connection T takes place, supported by the respective control pressure in the control line 34.
  • the pressure reduction device 68 is deactivated as a whole and the Fig.2
  • the valve shown operates like a standard pressure compensator in a supply circuit, for example according to the embodiment according to Fig.1 .
  • orifice 56 with its free opening cross-section is selected to be slightly larger than the free orifice cross-section of the orifice 67, asymmetrical differential pressure values can also be achieved if required within the scope of the pressure reduction by means of the relevant device 68.
  • the Fig.2 The valve shown in the form of a cartridge solution allows the system pressure in hydraulic supply circuits, as exemplified in the Fig.1 shown, are significantly reduced when idling and when the working hydraulics in the form of the differential cylinder 10 are activated, the required load sensing ⁇ p is again automatically generated, as described.

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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)
  • Safety Valves (AREA)

Claims (9)

  1. Soupape comprenant un corps (44) de soupape et un piston (46) de soupape, qui y est guidé avec possibilité de se déplacer longitudinalement, un raccord (32) de pression et un raccord (48) de réservoir, dans laquelle le piston (46) de la soupape, sous l'action d'un ressort (40) de soupape, obture, dans sa position fermée, une communication fluidique entre le raccord (32) de pression et le raccord (48) de réservoir dans le corps (44) de la soupape et la dégage dans une position d'ouverture et a un diaphragme (56), qui donne une communication fluidique permanente du côté du raccord (32) de pression avec un espace (58) de ressort ayant le ressort (40) de la soupape, et comprenant un raccord (64) load-sensing dans le corps (44) de la soupape, qui débouche dans l'espace (58) de ressort, dans laquelle, dans le corps (44) de la soupape, est logé un dispositif (68) d'abaissement de la pression, qui, lorsque la pression manque au raccord (64) load-sensing, met l'espace (58) de ressort du piston (46) de la soupape en communication fluidique avec le raccord (48) de réservoir, caractérisée en ce que le dispositif (68) d'abaissement de la pression est logé dans un boîtier (60) vissé, qui peut être vissé par un côté frontal libre du corps (44) de la soupape, qui fait face à l'autre côté frontal ayant le raccord (32) de pression.
  2. Soupape suivant la revendication 1, caractérisée en ce que le dispositif (68) d'abaissement de la pression a un piston (80) d'abaissement de la pression, qui peut se déplacer longitudinalement, qui délimite, par l'un de ses côtés frontaux libres, un autre espace (76) de ressort ayant un ressort (78) de piston de pression et qui peut être commandé par la pression dans un autre raccord (94) load-sensing dans le corps (44) de la soupape, qui débouche, de préférence dans un espace (66) pour du fluide, qui communique avec le raccord (64) load-sensing.
  3. Soupape suivant la revendication 2, caractérisée en ce que, dans le boîtier (60) de vissage, est ménagé un premier conduit (70) pour du fluide, qui, laissé libre par le piston (80) d'abaissement de la pression, donne une communication fluidique entre l'un (58) et l'autre espaces (76) de ressort.
  4. Soupape suivant la revendication 3, caractérisée en ce que, dans le boîtier (60) de vissage, est ménagé un deuxième conduit (86) pour du fluide, qui, dans chaque sens de déplacement du piston (80) d'abaissement de la pression, donne une communication fluidique entre l'autre espace (76) de ressort par un conduit (88) de liaison s'étendant dans le corps (44) de la soupape et allant au réservoir (T).
  5. Soupape suivant la revendication 4, caractérisée en ce que, dans le boîtier (60) de vissage, est ménagé un troisième conduit (92) pour du fluide, qui met en communication, avec l'autre raccord (94) load-sensing, l'autre espace (90) pour du fluide, qui est délimité par le piston (80) d'abaissement de la pression.
  6. Soupape suivant l'une des revendications 2 à 5 précédentes, caractérisée en ce que, si la pression est nulle au raccord (64) load-sensing et à l'autre raccord (94) load-sensing et, pour une pression de pompage pouvant être donnée à l'avance au raccord (32) de pression, le piston (80) d'abaissement dégage, sous l'action du ressort (78) du piston de pression, la communication fluidique entre les deux espaces (58, 76) de ressort, de manière à ce que la pression de diaphragme, se créant derrière le diaphragme (56) au moyen de la pression de pompage dans l'espace (58) de ressort du piston (46) de la soupape, décroisse vers le raccord (48) de réservoir et de manière à ce que la pression de pompage au raccord (32) de pression soit abaissée.
  7. Soupape suivant la revendication 5, caractérisée en ce que, pour une pression load-sensing apparaissant dans l'autre espace (90) pour du fluide, le piston (80) d'abaissement de la pression est, à l'encontre de l'action du ressort (78) de piston de pression, déplacé dans sa position obturant la communication fluidique entre les espaces (58, 76) de ressort, de sorte que le piston (46) de la soupape effectue, à l'encontre de la pression load-sensing dans l'espace (58) de ressort sur son côté, tourné vers l'espace (58) de ressort, la commande du courant de fluide du raccord (32) de pression de pompage au raccord (48) de réservoir.
  8. Soupape suivant l'une des revendications précédentes, caractérisée en ce que le diaphragme (56) et/ou un autre diaphragme (67) au raccord (64) load-sensing est conformé respectivement sous la forme d'un diaphragme de vissage ayant des géométries de diaphragme différentes, qui peut être inséré en plongeant dans le piston (46) de la soupape ou dans le corps (44) de la soupape et/ou en ce que les deux diaphragmes (56, 67) sont montés l'un derrière l'autre en série.
  9. Circuit hydraulique d'alimentation comprenant
    - un consommateur (10) hydraulique, comme un vérin différentiel ;
    - un dispositif (18) d'alimentation en pression, comme une pompe constante ;
    - un réservoir (T) ou un retour (42) ;
    - une soupape (22) de commande principale, montée entre le dispositif (18) d'alimentation en pression et le consommateur (10) hydraulique ; et
    - une soupape (24) à deux voies entre le consommateur (10) hydraulique et la soupape (22) de commande principale,
    caractérisé en ce qu'une soupape suivant l'une des revendications précédentes est raccordée au côté de sortie du dispositif (18) d'alimentation en pression, qui reçoit la pression la plus haute à la soupape (24) à deux voies comme pression load-sensing.
EP22162366.3A 2021-04-14 2022-03-16 Soupape Active EP4074986B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102021001960.1A DE102021001960A1 (de) 2021-04-14 2021-04-14 Ventil

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EP4074986A1 EP4074986A1 (fr) 2022-10-19
EP4074986B1 true EP4074986B1 (fr) 2024-05-15

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Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3909291C2 (de) 1989-03-21 1998-10-29 Heilmeier & Weinlein Wegesteuerventil mit Druckwaage
DE19646445A1 (de) 1996-11-11 1998-05-14 Rexroth Mannesmann Gmbh Ventilanordnung
DE10120643B4 (de) 2000-11-10 2012-05-24 Bosch Rexroth Aktiengesellschaft Vorgesteuertes Druckventil
EP2241764B1 (fr) 2009-04-17 2011-08-31 HAWE Hydraulik SE Soupape à siège dotée d'une fonction de soupape de dérivation et de compensateur de pression
DE102009049548A1 (de) * 2009-10-16 2011-04-21 Hydac Fluidtechnik Gmbh Ventilanordnung
DE102012010522A1 (de) * 2012-05-25 2013-11-28 Hydac Fluidtechnik Gmbh Ventil für Ventilanordnung

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DE102021001960A1 (de) 2022-10-20

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