EP2584230B1 - Soupape, ensemble hydraulique avec une soupape de ce type et utilisation d'un bouton ou d'un interrupteur pour une soupape - Google Patents

Soupape, ensemble hydraulique avec une soupape de ce type et utilisation d'un bouton ou d'un interrupteur pour une soupape Download PDF

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Publication number
EP2584230B1
EP2584230B1 EP20120185588 EP12185588A EP2584230B1 EP 2584230 B1 EP2584230 B1 EP 2584230B1 EP 20120185588 EP20120185588 EP 20120185588 EP 12185588 A EP12185588 A EP 12185588A EP 2584230 B1 EP2584230 B1 EP 2584230B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
spring
sensor
slide
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.)
Not-in-force
Application number
EP20120185588
Other languages
German (de)
English (en)
Other versions
EP2584230A1 (fr
Inventor
Davide Pingani
Andrea Tamelli
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2584230A1 publication Critical patent/EP2584230A1/fr
Application granted granted Critical
Publication of EP2584230B1 publication Critical patent/EP2584230B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40523—Flow control characterised by the type of flow control means or valve with flow dividers
    • F15B2211/4053—Flow control characterised by the type of flow control means or valve with flow dividers using 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
    • F15B2211/40—Flow control
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—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
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves
    • F15B2211/5059—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves using double counterbalance 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7058—Rotary output members

Definitions

  • the invention is based on a valve which has a position detection, a hydraulic arrangement with such a valve and a use of a button or switch for a valve.
  • a valve is provided with a position detection of a valve element.
  • the valve has a valve housing in which the valve element is slidably guided.
  • a permanent magnet is arranged, which cooperates with a magnetic field sensor for detecting the position of the valve element.
  • slide valves are known from the prior art, in which a device for position detection is arranged directly on a valve slide, or cooperates with a switching magnet of the valve slide.
  • Direct mounting on a valve spool requires sensors with a very high accuracy due to the low tolerances neutral position of the valve spool.
  • the device for position detection must be calibrated consuming, which leads to high costs.
  • the invention has for its object to provide a valve and a hydraulic arrangement with such a valve, in which the position of a valve body of the valve device is simple and inexpensive detectable. This object is achieved with regard to the valve having the features of patent claim 1 and with regard to the hydraulic arrangement having the features of patent claim 10.
  • a valve in particular a slide valve or a seat valve, for example a conical, ball or seat valve seat, a valve body which is displaceable in at least two switching positions.
  • a sensor is provided which is activated in an arrangement of the valve body in one of the switching positions and deactivated in the arrangement of the valve body in the other switching position.
  • This solution has the advantage that at least two positions of the valve body can be determined with a sensor device of extremely simple construction.
  • the senor is designed as an electrical button or electrical switch.
  • Such a sensor can be used in a wide variety of valve types and, unlike the prior art, does not have to be individually calibrated for a respective valve. This leads to a low production and assembly costs and is thus extremely cost-effective.
  • a detection piston may be provided, via which the sensor can be activated by the valve body.
  • the valve body is thus not directly in operative connection with the sensor and can be configured in a conventional manner.
  • the valve is a spool valve and the valve body is a valve spool.
  • a switching position of the valve spool is then the neutral position in which the valve spool, for example, is spring-centered.
  • the valve spool is then displaced from the neutral position in the direction of the other switching positions in which the sensor is activated by the valve spool.
  • the valve spool is displaceable from a neutral position in opposite directions in a respective switching position.
  • a detection piston is provided for each sensor, which each device-wise simply coaxial with the valve spool and is movable in an end position in the direction of the valve spool.
  • a respective detection piston can then be moved out of its end position by the valve slide, whereby then the sensor associated with the respective detection piston is activated by the detection piston.
  • a spring For moving a respective detection piston into its end position, a spring can be simply used, which acts on the detection piston in the direction of its end position with a spring force.
  • valve spool is then acted upon by the spring of the respective detection piston also with the spring force, whereby it is spring-centered in its neutral position. In the neutral position, then, both detection pistons are essentially in their end positions.
  • the valve may control a first pressure medium flow path and a second independent pressure medium flow path.
  • the valve spool then has first and second control surfaces facing away from each other. When pressurizing a respective control surface of the valve spool is displaced in its switching positions. The first control surface is acted upon by the pressure in the first pressure medium flow path and the second control surface by the pressure in the second pressure medium flow path.
  • Each of the control surfaces of the valve slide can in this case limit a pressure chamber, in which then also a respective detection piston opens and can be mechanically brought into operative connection with the valve slide.
  • a pressure application surface of a respective detection piston to which a respective pressure in the respective pressure chamber in a direction of displacement of the detection piston acts away from its end position and against the spring force of the spring, is selected such that the detection piston does not counteract the spring force of the spring due to this pressure in Displaceable pressure chamber is. This avoids that the activated by the respective detection piston switch is activated by a pressure and not by the valve spool.
  • the pressure application surface of a respective detection piston may be smaller than the respective control surface of the valve spool.
  • the detection piston can be designed in two parts and have a substantially circular cylindrical pin for mechanical contacting of the valve slide and a spring plate, in particular a section with a spring plate, which can activate the sensor on the one hand and on the other with the spring force of the detection piston associated spring is acted upon , A detection piston is further preserved in its end position via its spring plate, in particular, by this rests against a seat.
  • a hydraulic arrangement has a valve according to the invention, which is arranged as a check valve in a flow path between a pressure medium source and a consumer.
  • the check valve is designed such that it is controllable only by the pressure of the pressure medium source and prevents in the closed state, a discharge of pressure medium from the consumer.
  • a flow control valve may be arranged in the pressure medium flow path between the pressure medium source and the check valve.
  • an electrical switch or an electrical switch for monitoring a neutral position and / or a switching position of a valve body of a valve can be used.
  • FIG. 1 has a hydraulic arrangement 1, a pressure medium source in the form of a hydraulic pump 2 and a driven by this consumer in the form of a hydraulic motor 4.
  • a flow control valve 6 and an inventive valve in the form of a check valve 8 is arranged in the pressure fluid flow path between the hydraulic pump 2 and the hydraulic motor 4.
  • the pump 2 delivers via a tank line 10 pressure fluid from a tank 12 into a feed line 14. This is connected to a pressure port P of the flow control valve 6.
  • This is a proportional adjustable 2/2-way valve, which in addition to the pressure port P has a working port A, to which a pressure medium line 16 is connected, which in turn is connected to a pressure port P of the check valve 8.
  • a valve spool of the flow control valve 6 is acted upon by a spring 18 in the direction of a closed position with a spring force, wherein in the closed position, a pressure medium connection between the terminals P and A is interrupted.
  • the valve spool is then movable in its switching positions against the spring force of the spring 18, in which the pressure medium connection between the pressure port P and the working port A is opened.
  • the flow control valve 6 is thus a pressure medium flow rate of the funded by the hydraulic pump 2 pressure medium adjustable.
  • a pressure relief valve 24 is arranged, which opens a connection to the tank 12 from a predetermined pressure.
  • the schematically illustrated check valve 8 has a valve body in the form of a valve spool 26 which is slidably guided in a valve bore 27 of a valve housing 28.
  • the valve spool 26 is a pressure fluid connection between the pressure port P and another working port A up and zuêtbar.
  • To the working port A connected to the hydraulic motor 4 working line 30 is connected, in which a in the flow direction to the hydraulic motor 4 opening check valve 32 is arranged.
  • the valve spool 26 is biased via a spring force of a valve spring 34 in a closed position in which the pressure medium connection between the pressure port P and the working port A is interrupted, wherein one of the valve spring 34 facing away end face 36 of the valve spool 26 at a bore bottom of the valve bore 27 is substantially present.
  • the pressure port P and the working port A open approximately radially in the valve bore 27 and are in the FIG. 1 formed approximately in a same plane approximately perpendicular to a longitudinal axis of the valve spool 26.
  • the outer side surface closes the working port A and the pressure medium connection P.
  • the end 36 is acted upon by a pressure in the valve housing 28 pressure medium from the pressure port P, wherein the valve spool 26 then at a spring force of the valve spring 34 on the over End face 36 acting control pressure moves in an opening direction against the spring force acting on it.
  • a pressure fluid connection between the pressure port P and the working port A is opened.
  • the check valve 8 can thus be acted upon only by the pressure medium upstream of the valve spool 26.
  • the valve spool 26 has a radially back-stepped valve spool portion 40 facing away from its end surface 36, which is guided through the valve housing 28 to the outside.
  • the valve spool 26 defines with its end face 36 in the valve housing 28 a cylinder space and with its valve spool portion 40 a valve spring 34 having annular space 42. With the valve spool portion 40 is arranged outside the valve housing 28 sensor 44 can be actuated. This is a conventional device constructed simple electrical button or electrical switch.
  • the neutral position or the closed position of the valve spool 26 can be determined in an extremely simple manner, in which the pressure port P is fluidly separated from the working port A.
  • the sensor 44 has a rod-shaped actuator 46, which in the in FIG. 1 shown position in contact or almost in contact with an end face of the valve spool portion 40 and thus mechanically engageable with the valve spool 26.
  • the actuating element 46 is also moved via the valve spool portion 40 in this direction, whereby the sensor 44 is actuated and reports a switching signal, for example, to an electronic control unit.
  • valve spool 26 If the valve spool 26 is moved in the direction of its neutral or closed position, the actuating element 46 is likewise displaced in this direction by a sensor spring 48 of the sensor 44. Is the valve spool 26 in the in FIG. 1 shown closed position, then the actuator 46 is in a position in which the sensor 44 is turned off.
  • a leakage connection 50 is further provided, which is connected to the valve bore 27 in the region of the valve slide 26 limited annular space 42 and is connected via a tank line 52 to the tank 12.
  • the hydraulic motor 4 is also connected on the output side via a drain line 54 to the tank 12.
  • FIG. 2a shows a further hydraulic arrangement 56 with a valve 58 according to the invention.
  • the flow control valve 60 is designed as a proportionally adjustable 4/3-way valve having a pressure port P, a tank port T and two working ports A, B.
  • a first connecting line 62 is connected to a port A1 of the different FIG. 1 trained blocking valve 58 is connected and to the working port B, a second connecting line 64 is connected, which is connected to a port A2 of the check valve 58.
  • the check valve 58 has a first consumer port V1, to which a first consumer line 66 is connected, and a second consumer port V2, to which a second consumer line 68 is connected.
  • a differential cylinder 70 is provided with a one-sided piston rod 72 having a piston 74.
  • the piston 74 thus separates a cylinder chamber 76 from an annular space 78.
  • a check valve 80 or 82 opening in the direction of the pressure medium flow toward the differential cylinder 70 is arranged in a respective consumer line 66 and 68.
  • a control line 84 to the consumer line between the check valve 58 and the check valve 82.
  • a control line 86 is provided, which branches off to the consumer line 66 between the check valve 80 and the check valve 58.
  • the flow control valve 60 has a valve spool, which is displaceable from its neutral position, in which a pressure medium connection between the terminals A, B, P and T is interrupted, via actuators in the direction of first and in the direction of second switching positions, wherein the directions are opposite to each other , In the direction of the first switching positions a, the pressure medium connection between the pressure port P and the working port A and between the tank port T and the working port B is opened, while in the second switching position b a pressure medium connection between the pressure port P and the working port B and between the working port A and the tank connection T is turned on. Furthermore, the valve spool is spring-centered in its neutral position 0.
  • the check valve 58 has in contrast to the check valve 8 FIG. 1 a guided in a valve housing 88 valve spool 90, which consists of a in the FIG. 2a shown neutral position in the direction of first and second switching positions is displaceable, the directions are opposite.
  • sensors 92 and 94 are provided, which correspond to the sensor from the FIG. 1 are designed as a device extremely simple design electrical button or electrical switch.
  • the valve spool 90 is in this case slidably guided in a valve bore 92 in which four in the longitudinal direction of the valve bore 92 to each other spaced annular chambers 98, 100, 102 and 104 are formed.
  • this is in the Figure 2c shown enlarged.
  • the annular chamber 98 in Figure 2c In this case, it is connected to the connection A1, the annular chamber 100 adjacent to it to the connection V1, the next chamber 102 to the connection V2, and the outer chamber 104 to the connection A2.
  • the two middle chambers 100 and 102 are in each position of the valve spool 90 through its central radial collar 106 separated from each other.
  • the valve spool 90 has a, in the Figure 2c seen from the central radial collar 106, left radial collar 108 and a right radial collar 110.
  • the valve spool 90 is radially stepped back at its end portions 112 and 114 and each has an annular end surface 116 and 118 formed by the radial collar 108 and the end portion 112 and the radial collar 110 and the end portion 114, respectively. Furthermore, the valve slide 90 has end faces 120 and 122 respectively formed on its end section 112 and 114.
  • the valve spool 90 is actuated at a shift from his in the Figure 2c shown neutral position to the left via a coaxially to the detection piston 124 arranged thereon the sensor 92 and a shift to the right via a further detection piston 126, the sensor 94.
  • a respective detection piston 124 and 126 has a radial collar 128 and 130, each about in the central region the detection piston 124 or 126 is formed.
  • a respective piston section 132 or 134 extends from the radial collar 128 and 130 of a respective detection piston 124 or 126 to the valve spool 90.
  • a respective end face of the piston section 132 or 134 facing the valve spool 90 has a substantially dome-shaped configuration and rests in the neutral position of the valve spool 90 its respective end face 120 and 122 from.
  • the piston portions 132 and 134 thereby collar into the annular chamber 98 and 104, respectively.
  • another piston portion 136 and 138 extending from a respective radial collar 128 and 130, away from the valve spool 90.
  • a valve spring 144 and 146 is arranged, which surrounds the respective piston portion 136 and 138, respectively supported on the valve housing 88 and the respective radial collar 128 and 130 acted upon by a spring force in the direction of the valve spool 90.
  • the valve spool 90 is then spring-centered via the valve spring 144 or 146 in its neutral position.
  • the spring chambers 140 and 142 are each connected to the tank 12 via a leakage channel 150 or 152.
  • valve spool 90 shifts into its switching positions in which a pressure medium connection between the ports A1 and V1 and between the ports V2 and A2 is opened. Downstream of the connection V1 of the check valve 58 then the check valves 80 and 82 are opened, in which case the cylinder chamber 76 with the hydraulic pump 2 and the annular space 78 with the tank 12 are in fluid communication.
  • the detection piston 126 is also moved by the end face 122 of the valve spool 90 abuts the end face of the piston portion 134.
  • the displacement of the detection piston 126 also takes place counter to the spring force of the valve spring 146 in the direction of the actuating element 46. Since this rests against an end face of the piston portion 138, it is moved in the direction of the sensor 94, whereby it is actuated.
  • the other sensor 92 remains unconfirmed because the detection piston 124 remains in its end position by the valve spring 144 assigned to it, in which the radial collar 128 abuts an annular surface of the valve housing 58 substantially abuts. Since only the sensor 94 is actuated, it can be concluded that the valve spool 90 is displaced in its direction from its neutral position.
  • valve spool 90 When the valve spool 90 reaches its neutral position, the actuating element 46 of the sensor 94 is likewise returned to its initial position by the sensor spring 48, in which the sensor 94 is unactuated. Since the sensor 92 is also unconfirmed in the neutral position of the valve spool 90, it can thus be concluded in a simple manner that the valve spool 90 is also in its neutral position.
  • the annular chamber 104 Upon a displacement of the valve spool of the flow control valve 60 in the switching positions b, the annular chamber 104 is connected to the hydraulic pump 2 and the annular chamber 98 to the tank 12.
  • the valve spool 90 is shifted at appropriate pressure ratios in its switching positions in the figures to the left, which in turn the sensor 92 is actuated via the detection piston 132.
  • the sensor 94 remains unconfirmed.
  • the port A2 is connected to the port V1 and the port A1 to the port V1. If the pressure in the annular chamber 104 decreases after the valve spool of the flow control valve 60 has been shifted to its neutral position 0, the valve spool 90 is spring-centered again into its neutral position, and the sensor 92 is again inactive.
  • a diameter of the valve spool 90 facing piston portions 132 and 134 of the detection piston 124 and 126 is selected such that a pressure force acting on it due to a pressure in the annular chamber 98 and 104 is smaller than the spring force of the valve spring 144 or 146, so that the detection piston 124 or 126 is displaceable only by the valve spool 90.
  • the sensors 92 and 94 advantageously have a comparatively low precision, whereby simple switches are sufficient as a device for position detection, resulting in a very cost-effective valve with position monitoring.
  • FIG. 2b is a flow control valve 154 as a variant of the flow control valve 60 FIG. 2a shown.
  • This has, in contrast to the flow control valve 60, a neutral position 0, in which the working ports A and B are each throttled connected to the tank port T.
  • pressure medium in particular from the annular chambers 98 and 104 of the check valve 58, can flow to the tank 12.
  • the hydraulic assembly 156 is separate from the FIG. 2b differing flow control valve 158.
  • the connections between the pressure port P and the working port A or B are in each case throttled.
  • branches off from the feed line 14, a channel with a pressure relief valve 160, the spring force of the valve spring 162 is adjustable in contrast to the previous embodiments.
  • a hydraulic pump 2 driving motor 164 is shown in the FIG. 3 in addition, a hydraulic pump 2 driving motor 164 is shown.
  • the check valve 193 is according to another embodiment as a block diagram in the FIG. 3 shown. Downstream of the check valve 58 are in the FIG. 3 two different variations for connection of the differential cylinder 70 is provided. The right variation, unlike the embodiment in the FIG. 2a Check valves 166 and 168, the valve body are each acted upon by a spring 170 and 172 with a spring force in the direction of its closing direction. In the second variant, left in the FIG. 3 is provided in parallel to a respective check valve 166 and 168, a valve 174 and 176, respectively. These are each a proportional 2/2-way valve. A valve spool of the respective valve 174 and 176 is acted upon via a spring force of a spring in the closing direction.
  • valve spool of the valve 174 or 176 additionally acts in the closing direction, the pressure of its associated consumer line 66 or 68 between the check valve 193 and the respective valve 174 and 176, respectively, for each of which a branch of the consumer line 66 and 68 control line 178 and 180 is provided.
  • a respective valve slide of the valve 174 or 176 is acted upon by a pressure between a respective valve 174 or 176 and the differential cylinder 70 via a control line 182 or 184.
  • valve spool of the right valve 176 in its opening direction via a control line 186 from the pressure of the consumer line 66 between check valve 193 and the left valve 174 and the valve spool of the left valve 174 in its opening direction via the control line 188 from the pressure of the consumer line 68 between check valve 193 and the right valve 176 acted upon.
  • the block diagram of the check valve 193 schematically shows the sensors 92 and 94 which are actuated by the valve spool of the check valve 193. Furthermore, the leakage channels 150, 152 opening in the tank 12 are shown. A pressurization of the valve spool of the check valve 193 takes place through the control lines 190 and 192, which branch off respectively from the connecting line 62 and 64 respectively.
  • FIG. 4 has the check valve 193 off FIG. 3 formed in the valve housing 88 working ports V1 and V2.
  • the sensors 92 and 94 are laterally screwed into the valve housing 88 and each have two electrical contacts 194 and 196 for electrical contacting.
  • FIG. 5 shows in a longitudinal sectional view along a sectional plane AA FIG. 4 the check valve 193.
  • the working ports V1 and V2 are here introduced as blind holes in the valve housing 88. At the bottom of the hole of a respective port V1 and V2 leads a slant channel 198 or 200 to the annular chamber 100 and 102.
  • the ports A1 and A2 are introduced as slanted channels 202 and 204 in the valve housing 88 and open respectively in the annular channel 98 and 104.
  • a respective detection piston 206 or 208 designed in two parts.
  • each of the radial collar 128 or 130 leading to the valve spool 90 piston portion 210 and 212 is configured in one piece and rod-shaped.
  • the respective piston section 210 and 212 can then be supported on the piston section 136 or 138 with its end face facing away from the valve slide 90. Each with its facing the valve spool 90 face the piston portion 210 and 212 may be supported on the valve spool 90.
  • a respective blind bore 214 or 216 extends approximately to the radial collar 108 or 110 of the valve slide 90 and has a larger diameter than that of its respective end face 120 and 122 ago introduced, approximately coaxially to the longitudinal axis of the valve spool 90 extending blind holes respective rod-shaped piston portion 210 and 212, respectively.
  • FIG. 6 shows the check valve 193 in a longitudinal sectional view, wherein the sectional plane approximately perpendicular to the sectional plane AA FIG. 4 runs.
  • leakage channels 150 and 152 can be seen, the spring chambers 140 and 142 with the tank 12 from FIG. 3 connect fluidly.
  • the spring chambers 140 and 142 are each accommodated in a housing cartridge 218 or 220 screwed into the valve housing 88. These are the same design, so for the sake of simplicity only in the FIG. 6 left housing cartridge 218 is described below.
  • the housing cartridge 218 has an inner portion 222 immersed in the valve housing 88 and a larger diameter outer portion 224.
  • the outer portion 224 has, see FIG.
  • the valve housing 88 has a continuous valve bore 226 with two different diameters. In its middle region, in which the valve slide 90 in the valve bore 226 is slidably guided, the diameter is smaller than in their end regions 228 and 230, respectively, in which the housing cartridge 218 or 220 is immersed. In a respective end region 228 and 230 of the valve bore 226th an internal thread 232 is introduced into which the respective housing cartridge 218 or 220 is screwed with an external thread 234. A screw-in depth of the housing cartridge 218 is limited by an annular end face 238 formed between the inner and outer sections 222, 224, which essentially abuts the valve housing 88 in the screwed-in state.
  • the spring chamber 140 is introduced as a blind hole in the housing cartridge 218, in which case the radial collar 128 of the detection piston 206 from FIG. 5 as spring plate is slidably guided in the spring chamber 140.
  • An end position of the spring plate 128 is formed by the bore bottom of the blind hole of the spring chamber 140, wherein the bottom of the bore points away from the valve slide 90.
  • an annular closing element 240 is provided, by the inner circumferential surface of which the valve spool 90 facing away piston portion 136 is sealingly and slidably received and abuts with its outer lateral surface on an inner circumferential surface of a bore in the housing cartridge 218, which has a slightly larger diameter as the spring chamber 140 has.
  • the housing cartridge 218 Seen in the longitudinal direction after the closing element 240, the housing cartridge 218 has an internal thread 242 into which a sensor housing 244 of the sensor 92 is then screwed.
  • the closing element 240 is then supported on an end face of the sensor housing 244 and the valve spring 144 in turn is supported on an annular end face of the closing element 240 and acts on the radial collar 128 of the detection piston 206, see FIG. 5 with the spring force in the direction of the valve spool 90.
  • the closing element 240 has an inner and outer sealing ring, wherein the outer sealing ring on the housing cartridge 218 and the inner sealing ring on the piston portion 136 abuts and the spring chamber 140 seals substantially to the outside.
  • the spring chamber 140 is connected via a radial channel 246 introduced in the housing cartridge 218 with an annular space 248, which surrounds the housing cartridge 218 and is inserted into the valve housing 88, which in turn is connected to the leakage channel 150.
  • the radial channel 246 is spaced from the bore base of the spring chamber 140 so that in the illustrated arrangement of the radial collar 128 in its voltage applied to the bottom of the hole end position of the radial channel 246 is not covered by this.
  • the formed as a cylindrical pin piston portion 210 is slidably guided in a pin bore 250 of the housing cartridge 218, wherein the housing cartridge 218 has in the region of the piston portion 210 at its outer periphery and in the region of the pin bore sealant to seal the annular space 98 to the outside.
  • the construction of the sensors 92 and 94 is based on the in the FIG. 6 right sensor 94 explained in more detail.
  • the sensor 94 has an actuating ball 252, which is mounted on the end side in a sensor housing 254.
  • the actuating ball 252 bears against a conical seat 256 of the closing element 240 and the piston section 138 is somewhat spaced with its end face from the actuating ball 252.
  • the sensor housing 254 is stepped and has a threaded portion 256 with an external thread, which is screwed into the internal thread 242 of the housing cartridge 220.
  • FIG. 7 shows a hydraulic arrangement 258 in a further embodiment, in contrast to the embodiment of FIG. 3 a differently designed check valve 260 has.
  • the working ports V1 and V2 in the neutral position of the valve spool of the check valve 260 via a leakage channel 262 and a tank line 264, to which the leakage channels 150 and 152 are connected, connected to the tank 12.
  • an unintentional displacement of the valve spool of the check valve 260 from its neutral position due to a high consumer-side pressure is additionally avoided.
  • valve spool 266 additionally has two valve spool channels 268 and 270, in the neutral position of the valve spool 260, the annular spaces 100, 102 to the tank 12 from FIG. 7 to connect via the introduced in the valve housing 88 tank channel 262.
  • the valve spool channels 268 and 270 are each introduced obliquely and parallel to each other in the valve spool 90 in the region of the radial collar 106 as a blind hole from a formed by the radial collar 106 of the valve spool 90 end face 272 and 274 ago.
  • valve slide channels 268 and 270 then each end approximately in the center of the valve slide 90 seen in the longitudinal direction and are each connected to a centrally introduced into the radial collar 106 radial bore 276 and 278.
  • the radial bores are fluidly connected to a valve housing 88 between the annular chambers 100 and 102 introduced further annular chamber 280, in turn, the leakage channel 262 opens.
  • the radial bores 276 and 278 are displaced away from the annular chamber 280, whereby the fluidic connection between the annular chamber 280 and the radial bores 276 and 278 and thus to the annular chambers 100 and 102 is interrupted via the oblique valve slide channels 268 and 270, respectively.
  • FIG. 9 shows a hydraulic arrangement 282 according to another embodiment, in which the check valve 283 substantially in accordance with the hydraulic arrangement of FIG. 3 is educated and unlike FIG. 3 the flow control valve 284 has another configuration. This is designed as 7/3-way valve.
  • the flow control valve 284 has two output ports Y1 and Y2 and an input port X, which are each connected to a further proportionally adjustable 3/3-way valve 286. With these, a pressure medium volume flow to the pressure port P of the flow control valve 284 is additionally controlled.
  • the port X of the flow control valve 284 is connected to the feed line 14, and the output ports Y1 and Y2 are connected to a common supply line 288 which is connected to an input port X of the directional control valve 286.
  • the directional control valve 286 Via a first output connection Y1, the directional control valve 286 is connected to a pressure line 290, which is connected to the pressure connection P of the flow control valve 284 via a check valve 292 which opens toward the flow control valve 284.
  • the directional control valve 286 is connected to a control line 294 via which a valve spool of the directional control valve 286 can be acted upon with pressure medium in the direction of a closed position.
  • the input terminal X and the output terminals Y1 and Y2 are separated from each other.
  • a first switching position of the valve spool of the directional control valve 286 via a control line 296 with pressure medium of the supply line 288 between the flow control valve 284 and the directional control valve 286 can be acted upon, wherein in the first switching positions a, the input terminal X is connected in a throttled manner to the output terminal Y1.
  • a further displacement of the valve spool of the directional control valve 286 after the first switching positions to second switching positions b in addition a connection between the input terminal X and the output terminal Y2 is opened.
  • FIG. 10 the check valve 283 is off FIG. 9 shown in a longitudinal sectional view. This corresponds essentially to the check valve 193 from the FIG. 6 ,
  • the left sensor 92 is shown in the FIG. 10 .
  • the valve spool 90 is in the FIG. 10 shown in a switching position, in which on the one hand, the annular chamber 98 is connected to the annular chamber 100 and the annular chamber 104 with the annular chamber 102.
  • the displacement of the valve spool 90 is limited by the fact that its end face 120 rests against an end face of the housing cartridge 218.
  • the pin-shaped piston portion 210 of the detection piston 206 is immersed in the switching position in the spring chamber 140, whereby this displaces the piston portion 136 against the spring force in the direction of the sensor 92, which in turn the actuating ball 252 in a in the FIG. 10 not shown actuating position is shifted, in which the sensor 92 is actuated or turned on. exceeds the spring force of the valve spring 144 acting on the valve spool 90 compressive forces, the valve spool 90 is moved by the spring force of the valve spring 144 in its neutral position.
  • a valve in particular a slide valve or a seat valve, which has a valve body. This is movable at least in two switching positions. In order to detect the position of the valve body in one of the switching positions, a sensor is provided which is activated in a switching position and deactivated in the other switching position.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
  • Check Valves (AREA)

Claims (12)

  1. Soupape à tiroir comprenant un tiroir de soupape (26 ; 90), qui peut être déplacé dans au moins deux positions de commutation, un capteur (44 ; 92, 94) étant prévu, lequel est activé dans l'une des positions de commutation du tiroir de soupape (26 ; 90) et est désactivé dans l'autre position de commutation, une position de commutation du tiroir de soupape (90) étant une position neutre, depuis laquelle le tiroir de soupape (90) peut être déplacé dans la direction de l'autre position de commutation, dans laquelle le capteur (92, 94) est activé par le tiroir de soupape (90), caractérisée en ce que le tiroir de soupape (90) peut être déplacé de la position neutre dans des directions opposées à chaque fois dans une position de commutation, deux capteurs (92, 94) étant prévus, l'un des capteurs (92) pouvant être activé dans la première position de commutation du tiroir de soupape (90) et l'autre capteur (94) pouvant être activé dans la deuxième position de commutation du tiroir de soupape (90).
  2. Soupape selon la revendication 1, dans laquelle le capteur (44 ; 92, 94) est réalisé sous forme de touche ou de commutateur.
  3. Soupape selon la revendication 1 ou 2, dans laquelle un piston de détection (124, 126) est prévu, par le biais duquel le capteur (92, 94) peut être activé par le tiroir de soupape (90).
  4. Soupape selon l'une quelconque des revendications précédentes, dans laquelle, pour un capteur respectif (92, 94), est à chaque fois prévu un piston de détection (124, 126), lesquels pistons de détection s'étendant essentiellement coaxialement au tiroir de soupape (90) et présentant à chaque fois dans une direction de déplacement vers le tiroir de soupape (90) une position de fin de course, un piston de détection respectif (124, 126) pouvant être déplacé depuis le tiroir de soupape (90) hors de sa position de fin de course pour activer le capteur respectif (92, 94).
  5. Soupape selon la revendication 4, dans laquelle un piston de détection respectif (124, 126) peut être tendu dans sa position de fin de course par le biais d'une force de ressort d'un ressort (144, 146).
  6. Soupape selon la revendication 5, dans laquelle le tiroir de soupape (90) est centré par ressort dans sa position neutre par le biais de la force de ressort des ressorts (144, 146) des pistons de détection (124, 126).
  7. Soupape selon les revendications 4 à 6, dans laquelle la soupape à tiroir (58) commande un premier et un deuxième chemin d'écoulement de fluide sous pression (A1, V1 ; A2, V2), le tiroir de soupape (90) présentant deux première et deuxième surfaces de commande (116, 120 ; 118, 122) s'écartant l'une de l'autre pour la sollicitation par pression du tiroir de soupape (90) dans la direction de ses positions de commutation, la première surface de commande (116, 120) pouvant être sollicitée avec du fluide sous pression du premier chemin d'écoulement de fluide sous pression (A1, V1) et l'autre deuxième surface de commande (118, 122) pouvant être sollicitée avec du fluide sous pression du deuxième chemin d'écoulement de fluide sous pression (A2, V2).
  8. Soupape selon la revendication 7, dans laquelle les surfaces de commande (116, 120 ; 118, 122) du tiroir de soupape (90) délimitent à chaque fois un espace de pression (98, 104) dans lequel débouche à chaque fois un piston de détection (124, 126) et dans lequel le tiroir de soupape (90) vient en contact mécanique avec le piston de détection respectif (124, 126) pour le déplacement, une surface d'engagement de pression d'un piston de détection respectif (124, 126), au niveau de laquelle une pression dans l'espace de pression respectif agit dans une direction de déplacement du piston de détection (124, 126) en l'éloignant de sa position de fin de course, et la force de ressort des ressorts (144, 146) associés au piston de détection respectif (124, 126) étant choisies de telle sorte que les pistons de détection (124, 126) ne puissent pas être déplacés à l'encontre de la force de ressort par le biais de la pression dans l'espace de pression respectif (98, 104).
  9. Soupape selon les revendications 5 à 8, dans laquelle le piston de détection (124, 126) est réalisé en deux parties avec une première partie de piston réalisée sous forme de goupille (210, 212) pour le contact mécanique du tiroir de soupape (90) et avec une partie de piston réalisée pour activer le capteur (92, 94) en tant que coupelle de ressort (128, 130), sur laquelle partie de piston s'engage le ressort respectif (144, 146), et la coupelle de ressort (128, 130) pouvant être tendue par la force de ressort du ressort (144, 146) dans la position de fin de course du piston de détection (124, 126), la goupille (210, 212) pouvant s'appuyer contre une surface de support de la coupelle de ressort (128, 130) opposée au ressort.
  10. Agencement hydraulique comprenant une soupape selon l'une quelconque des revendications précédentes, qui est disposée en tant que soupape d'arrêt (8, 58) dans un chemin d'écoulement de fluide sous pression entre une source de fluide sous pression (2) et un consommateur (4, 78).
  11. Agencement hydraulique selon la revendication 10, dans lequel la soupape d'arrêt (8, 58) peut être sollicitée avec une pression dans la direction de ses positions de commutation dans le chemin d'écoulement de fluide sous pression connecté à la source de fluide sous pression (2) en amont de son corps de soupape (26, 90).
  12. Agencement hydraulique selon la revendication 10 ou 11, dans lequel, dans le chemin d'écoulement de fluide sous pression entre la soupape d'arrêt (8, 58) et la source de fluide sous pression (2), est disposée une soupape de régulation de l'écoulement (6, 60).
EP20120185588 2011-10-20 2012-09-24 Soupape, ensemble hydraulique avec une soupape de ce type et utilisation d'un bouton ou d'un interrupteur pour une soupape Not-in-force EP2584230B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201110116632 DE102011116632A1 (de) 2011-10-20 2011-10-20 Ventil, hydraulische Anordnung mit einem derartigen Ventil und Verwendung eines Tasters oder Schalters für ein Ventil

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EP2584230A1 EP2584230A1 (fr) 2013-04-24
EP2584230B1 true EP2584230B1 (fr) 2014-06-04

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CN111348229A (zh) * 2018-12-23 2020-06-30 邯郸市复兴区宏昌科技有限公司 一种能消除水锤效应的液体分装装置
CN114321439B (zh) * 2021-12-29 2023-10-03 湖北三江航天红峰控制有限公司 一种自动换向阀

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US3921665A (en) * 1974-12-17 1975-11-25 Us Army Limit valve with overtravel detector
US6792902B2 (en) * 2002-04-22 2004-09-21 Borgwarner Inc. Externally mounted DPCS (differential pressure control system) with position sensor control to reduce frictional and magnetic hysteresis
DE102006049724A1 (de) 2006-10-21 2008-04-24 Robert Bosch Gmbh Ventilanordnung mit Positionssensor

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