EP0549628B1 - Dispositif de commande pour un verin hydraulique - Google Patents

Dispositif de commande pour un verin hydraulique Download PDF

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Publication number
EP0549628B1
EP0549628B1 EP91915901A EP91915901A EP0549628B1 EP 0549628 B1 EP0549628 B1 EP 0549628B1 EP 91915901 A EP91915901 A EP 91915901A EP 91915901 A EP91915901 A EP 91915901A EP 0549628 B1 EP0549628 B1 EP 0549628B1
Authority
EP
European Patent Office
Prior art keywords
valve
bore
valve body
appliance according
pilot control
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.)
Expired - Lifetime
Application number
EP91915901A
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German (de)
English (en)
Other versions
EP0549628A1 (fr
Inventor
Hartmut Sandau
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
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Robert Bosch GmbH
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Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0549628A1 publication Critical patent/EP0549628A1/fr
Application granted granted Critical
Publication of EP0549628B1 publication Critical patent/EP0549628B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot 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
    • F15B13/01—Locking-valves or other detent i.e. load-holding devices
    • F15B13/015—Locking-valves or other detent i.e. load-holding devices using an enclosed pilot flow 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
    • 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
    • F15B13/044—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors
    • F15B13/0442—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by electrically-controlled means, e.g. solenoids, torque-motors with proportional solenoid allowing stable intermediate positions

Definitions

  • the invention is based on a control device with a proportional control valve according to the preamble of claim 1.
  • a proportional control valve according to the preamble of claim 1.
  • an electromagnetically pilot-controlled proportional control valve which has a pilot valve element actuated by a proportional magnet.
  • This pilot valve member controls the pressure in a pressure chamber arranged between the valve body of the proportional control valve and its valve housing, by the action of which the valve body is pressed against the valve seat.
  • Proportional control valves of this type have the disadvantage that the controlled or regulated pressure medium flow is subject to strong fluctuations since, in particular, the fine controllability is not sufficient for applications in which a high control quality is required. Due to the poor fine controllability of these proportional control valves, neither high control stabilities nor continuous pressure medium flows can be set.
  • the control device according to the invention with the characterizing features of claim 1 has the advantage that a short, finely controllable outflow of the pressure medium is made possible with short actuation paths for the proportional control valve and low actuation forces.
  • a stable course of the valve characteristic curve is also achieved over a large range.
  • This high control stability of the valve leads to a low-vibration mode of operation, which also reduces snarling and whistling noises.
  • the device according to the invention is particularly suitable as a so-called lowering brake valve, in which the pressure medium flowing back from the consumer (hydraulic cylinder) is throttled, so that - as mentioned at the beginning - the load does not advance or "jerky".
  • 10A denotes an approximately cup-shaped valve housing of a proportional control valve 10, which with its open end face 11 bears against a housing 12 of a proportional magnet 13.
  • Two circumferential annular grooves 15, 16 are formed in the interior of the valve housing.
  • the annular groove 15 is connected via a bore 18 and a pressure medium supplying connection 19 to a pressure medium source, and the annular groove 16 is connected via a bore 20 to a connection 21 leading to a consumer and discharging pressure medium.
  • a cylindrical bushing 23 is inserted into the valve housing 10A and fixed in the housing with a locking nut 24 with an external thread 25.
  • the valve housing has a corresponding internal thread 26 in the region of its end face 11, which starts from a cylindrical recess 27 on the end face, into which a sealing ring 28 is inserted. This seal seals the connection of the valve housing to the proportional solenoid from the outside.
  • Axially through the bushing 23 are two bores 30, 31 which merge into one another, of which the bore 31 facing the end face 11 has the smaller diameter.
  • annular groove 32 is formed in the region of the transition to the bore 31, which is connected via transverse bores 33, 34 to an annular channel 36 formed by the annular groove 15 and the bushing 23.
  • the bore 31 is penetrated by a transverse bore 37 formed in the bushing 23, which connects the bore 31 to an annular channel 38 formed by the annular groove 16 and the bushing 23.
  • a valve body 40 is guided in a tightly sliding manner in the bore 30 of the bushing 23. This interacts with a valve seat 41 formed at the transition of the bore 30 into the bore 31.
  • the valve body 40 is formed in the region of the valve seat 41 as a flat cone 42 which merges into a fine control cone 43.
  • the transition 44 from the cone to the fine control cone is not designed in the form of an edge, but as a concave curve.
  • the valve body 40 is penetrated by three merging bores 45, 46, 47 which merge into one another.
  • the bore 47 opening at the fine control cone 43 has the smallest diameter
  • the bore 45 opening at the opposite end face has the largest diameter.
  • the valve body is closed on one side by a screw 49 on the end face opposite the fine control cone.
  • the threaded part 50 of the screw projects into the bore 46, which has an internal thread over a corresponding part of its length.
  • the screw head 52 lies against the end face of the valve body in such a way that an annular channel 54 is created through the bore 45 and the screw 49.
  • an annular groove 55 is formed, into which a sealing ring 56 is inserted, which seals the annular channel 54 against the bore 46.
  • a blind bore 57 is made on the side facing away from the valve body, from the bottom of which a throttle bore 58 extends, which opens into the annular channel 54.
  • the ring channel 54 is connected via the bores 57, 58 to a pressure chamber 60 formed between the bottom of the housing 10A and the valve body 40.
  • two blind bores 61, 62 which extend from the outer circumference and are arranged in the area of the annular groove 32, run radially.
  • a throttle bore 63, 64 which both open into the bore 47, extends from the bottom thereof.
  • the bore 61 has an internal thread 65 in the region of the outer circumference of the valve body, into which a screwing throttle 66 is inserted.
  • the bore 62 is closed in the region of the outer circumference of the valve body by a plug 68.
  • the blind hole 61 is connected to the annular channel 54 via a longitudinal channel 67 and the blind hole 62 via a longitudinal channel 70.
  • the bore 47 is penetrated by a third radially extending blind bore 69, which likewise extends from the outer circumference of the valve body and is closed there by a stopper 59 (see FIG. 2).
  • a pilot valve 71 In the bore 47, a pilot valve 71 is guided in a tightly sliding manner. It projects on one side with a conically expanded valve cone 72 into the bore 46 and interacts there with a valve seat 73 formed at the transition from the bore 46 into the bore 47.
  • the pilot spool protrudes into a hexagonal opening 74 of the locking nut 24 and interacts there with an actuating plunger 75 projecting into the opening 74 from the proportional magnet 13.
  • the pilot spool 71 penetrates the bottom of a pot-shaped spring guide element 78 which projects into the bore 31 and abuts the front side of the bush 23 with a ring-shaped edge 79.
  • the spring guide element 78 is fixed in position by the lock nut 24.
  • this has an annular groove 80, the diameter of which corresponds to that of the collar-shaped edge 79.
  • the spring guide element 78 can also be fixed in the radial direction by the edges of the opening 74; for this purpose the outer circumference of the edge 79 should then correspond to the inner circle diameter of the hexagonal opening 74.
  • One end of a compression spring 82 is supported on the inside of the spring guide element 78, the other end of which rests on a disk 83 pushed over the pilot valve 71. This disc is secured against being pushed off by a locking ring 85 which is fitted into an annular groove 84 at the end of the pilot spool.
  • the pilot spool 71 is penetrated by a transverse bore 87.
  • a longitudinal blind bore 88 which starts from the pilot valve cone 72, opens into this transverse bore.
  • Two annular grooves 90, 91 are formed on the outer circumference of the pilot valve, between which a narrow collar 92 remains. This closes the throttle bores 63, 64 when the pilot valve cone 72 bears against the valve seat 73.
  • the annular groove 90 extends from the collar 92 to the valve cone 72, which starts from the bottom of this groove.
  • two annular channels 94, 95 are formed, which in each of the blind bore 69 Working position of the spool are connected.
  • the diameter of the blind bore 69 is so large that the two ring channels are connected even when the pilot spool is lifted.
  • the proportional control valve 10 is closed when the proportional magnet 13 is not energized. Due to the action of the compression spring 82, the valve cone 72 of the pilot valve 71 is pulled to its seat 73 and thus also the valve body 40 against its seat 41. At the same time, the collar 92 closes the throttle bores 63, 64.
  • the pressure medium connection 19 is connected to the screw-in throttle 66 via the bore 18, the annular channel 36 and the bores 33, 34 and the annular groove 32. From there, pressure medium reaches the annular space 54 via the longitudinal channel 67 and from there via the throttle bore 58 and the bore 57 into the pressure space 60. At the same time, there is a connection from the annular channel 54 to the bore 62 via the longitudinal channel 70.
  • the outlet side is through the valve body on one side closed bore 31 via the bore 37, the annular channel 38 and the bore 20 with the pressure medium connection 21 in connection. Since the end face A S of the valve body acted upon by pressure medium - corresponding to the area of the bore 30 - is larger than the annular area A R - corresponding to the area difference between the bore 30 and 31, the valve body is additionally pressed against its seat 41. The leakage losses in the closed position of the check valve are very low due to the seat valves used and the long sliding guide of the pilot spool 71 in the bore 47.
  • the pilot valve 71 moves to the left through the plunger 75 of the proportional magnet 13, so that the pilot valve cone 72 lifts off its valve seat 73 and the throttle bores 63, 64 previously closed on one side by the collar 92 are opened.
  • pressure medium flows from the inlet-side connection bore 19, as previously described, to the bores 61, 62 and from there via the throttle bores 63, 64 into the ring channel 95 From there, the pressure medium passes through the opened valve seat 73 into the bore 46 which is closed on one side.
  • the bore 46 is connected to the bore 31 via the longitudinal bore 88 and the transverse bore 87 in the valve slide 71, which bore, as described above, is connected to the outlet end Pressure medium connection 21 is.
  • the pressure in the bore 61 and thus also in the pressure chamber 60 drops. If the pressure in the pressure chamber 60 falls so far that the pressure forces on the opposite valve body face ( Ring area A R ) predominate, the valve body 40 moves to the left. Pressure medium then flows out of the annular groove 32 past the opened valve seat 41 into the bore 31 and from there to the pressure medium connection 21. If the pilot valve 71 follows the plunger 75 due to the action of the spring 82 with a corresponding movement to the right, the valve body 40 also follows (Sequence control).
  • This movement of the valve body results from the changing pressure conditions on the end faces of the valve body and the mechanical guidance by the pilot spool.
  • the force to move the pilot spool is determined by the compression spring 82 and the friction in the bore 47. Since the pressure in the ring channels 94, 95 is balanced by the bore 69, no hydraulic forces act on the pilot valve. The actuating forces for the pilot spool are therefore low. If the pressure at port 19 is so low that the valve cone 40 alone cannot be moved, the pilot spool supports the movements.
  • the pilot spool 71 strikes the end face of the Valve plug 72 - after fully opening the throttle bores 63 and 64 - against the screw 52 and thus supports the movement to the left.
  • the valve body 40 is carried along by the valve cone 72 of the pilot valve.
  • FIG. 3 shows a modification of the embodiment of Figure 1, in which the valve body is made in two parts. The same parts are again provided with the same numbers.
  • This embodiment offers advantages in terms of production technology, since the cone serving as the seat cone and the fine control cone can be machined separately.
  • the valve body 40A which is tightly guided in the bush 23, is composed of an inner cylindrical valve body sleeve 100 and an outer cylindrical valve body sleeve 101.
  • the outside diameter of the valve body sleeve 101 corresponds to the diameter of the bore 30 in the bushing 23.
  • This valve body sleeve 101 is penetrated axially by two bores 102, 103 which merge into one another in the same axis, of which the bore 103 opening in the region of the valve seat 41 has the smaller diameter.
  • the diameter of this bore 103 is smaller than the diameter of the bore 31 in the bushing 23.
  • the end face of the valve body sleeve 101 facing the valve seat 41 is designed as a flat cone 105. This runs in the region of the diameter of the bore 31, ie in the region of the valve seat 41, into a concavely rounded transition 107 such that an annular shoulder 108 remains on the end face of the valve body sleeve, the outer diameter of which is slightly smaller than the diameter of the bore 31.
  • In the valve body sleeve 101 there is a radially extending blind bore 109 extending from the outer circumference, from the bottom of which a throttle bore 110 extends, which opens into the bore 102.
  • the bore 102 and the annular groove 32 are connected to one another via the bores 109, 110.
  • the inner valve body sleeve 100 consists of a fine control cone 111 which projects into the bore 31 and a cylindrical section 112 which projects through the bore 103 into the bore 102.
  • the outer circumference of the section 112 corresponds to the diameter of the bore 103
  • the outer diameter of the fine control cone 111 corresponds to the outer diameter of the ring shoulder 108.
  • the fine control cone lies flush against the ring shoulder, so that there is a smooth transition from the cone 105 via the concave transition 107 to the fine control cone 111 trains.
  • Two inner bores 114, 115 run axially through the inner valve body sleeve 100, of which the bore 115 opening at the fine control cone 111 has the smaller diameter.
  • two radial, opposite blind bores 116, 117 run, from the bottom of which a throttle bore 118, 119 extends, both of which open into bore 115.
  • the bore 115 is penetrated again by a blind bore 120, which likewise starts from the outer circumference of the section 112 and is closed there by a plug, not shown.
  • the valve body 40A is closed on one side on the side opposite the fine control cone by a screw 49A.
  • the threaded part 50A of the screw projects into the bore 114 of the inner valve body sleeve, which has an internal thread 122 over a corresponding part of its length.
  • the screw head 52A lies against the end face of the outer valve body sleeve 101 in such a way that the inner valve body sleeve is braced against the outer one.
  • An annular space 123 delimited by the screw is formed between the two valve body sleeves in the area of the bore 102 and the section 112.
  • an annular groove 55A is formed, into which a sealing ring 56A is inserted, which seals the bore 114 on one side.
  • In the screw head 52A is on the fine control cone facing away from a blind bore 57A, from the bottom of which a throttle bore 58A emerges, which opens into the annular space 123.
  • a pilot valve 71A corresponding to the exemplary embodiment described above is guided in the bore 115 in a tightly sliding manner. It extends with its valve cone 72A into the bore 114 and interacts there with a valve seat 125 formed at the transition of the bores 114, 115.
  • the collar 92A on the outer circumference of the pilot valve closes the throttle bores 118, 119 when the valve cone 72A is in contact with the seat 125.
  • the annular grooves 90A, 91A together with the wall of the bore 115 form two annular channels 126, 127, which pass through the blind bore 120 in each working position of the spool are connected to each other.
  • FIG. 4 shows a further exemplary embodiment, which differs from the ones described above in that the valve body and pilot spool are designed differently.
  • the same parts are provided with the same numbers here.
  • the valve cone 40B differs from the valve cones 40, 40A in that it has a displaced valve seat 73B for the pilot valve 71B.
  • the bore 46B is a longitudinal bore consisting of three bore sections 130, 131, 132 which merge into one another with the same axis.
  • the bore section 130 starting from the bore 46B corresponds to the bore 47.
  • the bore section 131 is formed, which has a larger diameter and merges into the bore section 132, which opens at the fine control cone .
  • the diameter of the bore section 132 is smaller than that of the bore section 130.
  • the transition between the bore sections 131, 132 is designed as a valve seat 73B.
  • the pilot spool 71B essentially consists of two cylindrical spool sections 134, 135, of which the section 135 projects through the fine control cone to the plunger 75 and interacts with it and the spring guiding device in a prescribed manner.
  • the slide section 135 has a diameter which is smaller than that of the bore section 132, so that an annular space 138 remains between the slide section and the bore section.
  • the slide section 135 In the area of the bore section 131, the slide section 135 has a narrow collar 137 which interacts with the valve seat 73B. The diameter of this collar is as large as that of the bore section 130.
  • the slide section 135 merges in the region of the throttle bore 63B, 64B into the slide section 134, which is guided in the bore section 130 in a tightly sliding manner and projects into the bore 46B.
  • a further annular space 139 remains between the slide section 135 and the bore section 130.
  • the slide section 134 is designed such that the throttle bores 63B, 64B are closed by it when the collar 137 abuts the valve seat 73B.
  • pilot valve 71B there is also a longitudinal bore 88B which extends from the bore 46B and opens into the transverse bore 87B.
  • the valve seat 41 is opened and closed analogously to the exemplary embodiments according to FIG. 1.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Magnetically Actuated Valves (AREA)
  • Safety Valves (AREA)
  • Actuator (AREA)

Abstract

Le dispositif de commande pour un vérin hydraulique présente une soupape d'arrêt (10) dans laquelle un corps de soupape (40; 40A; 40B) coopère avec un siège de soupape (41) solidaire du corps. Dans le corps de soupape est placé un élément de soupape pilote (72; 72A; 72B), lequel coopère avec un siège de soupape (73; 73A; 73B) également disposé dans le corps de soupape, ainsi qu'avec des orifices d'étranglement (63, 64; 118, 119; 63B, 64B). Les efforts de pression exercés sur l'élément de soupape pilote sont compensés, de sorte que ce dernier puisse être actionné par un aimant proportionnel (13).

Claims (10)

  1. Dispositif de commande pour un vérin hydraulique avec une soupape de commande proportionnelle (10) ayant une alimentation (19) et une évacuation (21), qui comporte un corps de soupape (40 ; 40A ; 40B), agissant avec un siège de soupape (41) solidaire de la cage et dans lequel est disposé un élément de soupape pilote (71, 72 ; 71A, 72A ; 71B, 137) pouvant être actionné par un aimant proportionnel (13) monté sur la soupape pilote proportionnelle, élément qui s'appuie sous la force d'un ressort contre un siège de soupape (73 ; 73A ; 73B) placé dans le corps de soupape, et commande la pression dans un espace de pression (60) formé entre le corps de soupape et la cage de soupape (10A), le corps de soupape étant pressé contre le siège de soupape (41) sous l'effet de cette pression, caractérisé en ce que l'élément de soupape pilote comporte un corps de soupape à siège (72 ; 72A ; 137) et un tronçon de tiroir pilote (90, 91, 92, 90A, 91A, 92A, 134) placé en série, en ce que l'espace de pression (60) est en communication avec l'alimentation (19) par deux endroits d'étranglement (66 ; 58 ; 110, 58A) montés en série, et en ce que cet espace de pression (60) peut être relié à l'évacuation (21) par l'élément de soupape pilote placé entre les endroits d'étranglement (66 ; 58 ; 110, 58A) branchés en série et un canal (88, 87 ; 88B, 87B ;138) à ouvrir par cet élément.
  2. Dispositif selon la revendication 1, caractérisé en ce que les deux endroits d'étranglement (66 ; 58 ; 110, 58A) sont réalisés dans le corps de soupape (40 ; 40A ; 40B).
  3. Dispositif selon les revendications 1 et/ou 2, caractérisé en ce que les deux endroits d'étranglement (66 ; 58, 110 ; 58A) sont en communication entre eux par des canaux de l'agent de pression (61, 67, 54, 70, 62 ; 123) placés dans le corps de soupape (40 ; 40A ; 40B).
  4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce que dans le corps de soupape (40, 40A ; 40B) sont réalisés des endroits d'étranglement (63, 64 ; 118, 119 ; 63B, 64B) pouvant être modifiés par le tronçon de tiroir pilote (90, 91,92 ; 90A, 91A, 92A ; 134) et par l'intermédiaire desquels la pression se trouve commandée dans l'espace de pression (60).
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que le ressort (82) agit en exerçant une traction sur l'élément de soupape pilote (71, 72 ; 71A, 72A ; 71B, 137).
  6. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que le corps de soupape (40 ; 40A ; 40B) comporte un cône (42 ; 105 ; 42B) à angle obtus qui se transforme en un cône de guidage précis (43 ; 111 ; 43B) et en ce que le passage du premier cône au cône à guidage précis est arrondi.
  7. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce que des rainures annulaires (90, 91 ; 90A, 91A) sont réalisées sur le tronçon du tiroir pilote, et en ce que les forces s'exerçant sur l'élément de soupape pilote sont équilibrées.
  8. Dispositif selon la revendication 7, caractérisé en ce que les canaux annulaires (94, 95 ; 126, 127) formés par les rainures annulaires (90, 91 ; 90A, 91A) et le corps de soupape (40 ; 40A) sont reliés ensemble dans l'élément de soupape par un alésage borgne (69 ; 120) fermé.
  9. Dispositif selon l'une des revendications 1 à 8, caractérisé en ce que l'élément de soupape (40A) se compose d'au moins un manchon de corps de soupape (100) interne et d'un manchon de corps de soupape (101) externe.
  10. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce que sur l'élément de soupape pilote (71B) est réalisé un collet (137) circulaire coopérant avec le siège de soupape (73B).
EP91915901A 1990-10-10 1991-09-21 Dispositif de commande pour un verin hydraulique Expired - Lifetime EP0549628B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4032078A DE4032078C2 (de) 1990-10-10 1990-10-10 Steuervorrichtung für einen hydraulischen Arbeitszylinder
DE4032078 1990-10-10
PCT/DE1991/000748 WO1992007194A2 (fr) 1990-10-10 1991-09-21 Dispositif de commande pour un verin hydraulique

Publications (2)

Publication Number Publication Date
EP0549628A1 EP0549628A1 (fr) 1993-07-07
EP0549628B1 true EP0549628B1 (fr) 1994-07-27

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP91915901A Expired - Lifetime EP0549628B1 (fr) 1990-10-10 1991-09-21 Dispositif de commande pour un verin hydraulique

Country Status (5)

Country Link
US (1) US5328148A (fr)
EP (1) EP0549628B1 (fr)
DE (2) DE4032078C2 (fr)
RU (1) RU2082024C1 (fr)
WO (1) WO1992007194A2 (fr)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140604A1 (de) * 1991-12-10 1993-06-17 Bosch Gmbh Robert Steuervorrichtung fuer den volumenstrom eines hydraulischen arbeitsmittels
WO1996012111A1 (fr) * 1994-10-15 1996-04-25 Mannesmann Rexroth Gmbh Procede permettant d'actionner un distributeur a siege 2/2 pilote et distributeur a siege 2/2 pilote permettant de mettre ledit procede en ×uvre
DE4446860A1 (de) * 1994-12-27 1996-07-04 Herion Werke Kg Regelventil
US5538026A (en) * 1995-03-29 1996-07-23 Parker-Hannifin Corporation Pilot-operated proportional control valve
DE19634319A1 (de) * 1996-08-24 1998-02-26 Bosch Gmbh Robert Elektrohydraulische Steuervorrichtung
US5878647A (en) * 1997-08-11 1999-03-09 Husco International Inc. Pilot solenoid control valve and hydraulic control system using same
DE19955521A1 (de) * 1999-11-18 2001-05-23 Bosch Gmbh Robert Vorrichtung zur Steuerung eines hydraulischen Volumenstroms zumindest eines belasteten Arbeitsmittels
JP2014502711A (ja) * 2010-12-28 2014-02-03 ボルボ コンストラクション イクイップメント アーベー 建設機械用の保持弁
RU2576828C1 (ru) * 2014-12-26 2016-03-10 Открытое акционерное общество "Омское машиностроительное конструкторское бюро" Клапан высокого давления
RU2686744C1 (ru) * 2018-08-13 2019-04-30 Сергей Анатольевич Паросоченко Дросселирующее устройство

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2694544A (en) * 1950-07-19 1954-11-16 Atkomatic Valve Company Inc Pressure actuated valve
GB875402A (en) * 1958-01-17 1961-08-16 Franco Belge De Material De Ch Improvements in and relating to a fluid control valve
US3033228A (en) * 1959-03-23 1962-05-08 Lewis K Rimer Low-force valve control
US3667722A (en) * 1970-10-22 1972-06-06 Ite Imperial Corp Proportional valve
DE3042277A1 (de) * 1980-11-08 1982-06-03 Robert Bosch Gmbh, 7000 Stuttgart Steuervorrichtung fuer einen hydraulischen arbeitszylinder
DE3125143A1 (de) * 1981-06-26 1983-01-13 Mannesmann Rexroth GmbH, 8770 Lohr "druckminderventil"
DE3429218A1 (de) * 1984-08-08 1986-02-20 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Elektromagnetisches hydroventil
CH671080A5 (fr) * 1986-10-01 1989-07-31 Sulzer Ag
US4741364A (en) * 1987-06-12 1988-05-03 Deere & Company Pilot-operated valve with load pressure feedback

Also Published As

Publication number Publication date
RU2082024C1 (ru) 1997-06-20
WO1992007194A3 (fr) 1992-05-29
US5328148A (en) 1994-07-12
DE59102380D1 (de) 1994-09-01
DE4032078A1 (de) 1992-04-16
WO1992007194A2 (fr) 1992-04-30
EP0549628A1 (fr) 1993-07-07
DE4032078C2 (de) 1997-08-07

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