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EP0548513B1 - Dispositif de commande du courant d'un fluide de travail - Google Patents

Dispositif de commande du courant d'un fluide de travail Download PDF

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Publication number
EP0548513B1
EP0548513B1 EP92118860A EP92118860A EP0548513B1 EP 0548513 B1 EP0548513 B1 EP 0548513B1 EP 92118860 A EP92118860 A EP 92118860A EP 92118860 A EP92118860 A EP 92118860A EP 0548513 B1 EP0548513 B1 EP 0548513B1
Authority
EP
European Patent Office
Prior art keywords
valve
pilot valve
control device
bore
valve member
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
EP92118860A
Other languages
German (de)
English (en)
Other versions
EP0548513A1 (fr
Inventor
Hartmut Dipl.-Ing.(Fh) Sandau
Holger Dipl.-Ing. Lueues
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
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0548513A1 publication Critical patent/EP0548513A1/fr
Application granted granted Critical
Publication of EP0548513B1 publication Critical patent/EP0548513B1/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
    • F15B13/01—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

Definitions

  • the invention relates to a control device according to the type specified in the preamble of claim 1.
  • Such a control device is already known from CH-A-543 028, in which, with the aid of a finely controllable shut-off valve, a so-called lowering valve, it is achieved that, for example, the load acting on a hydraulic working cylinder does not lead the assigned volume flow when lowering.
  • This shut-off valve has a seat valve body, which is pressed against a housing-fixed main valve seat by a relatively strong compression spring arranged in a pressure chamber.
  • the seat valve body accommodates in its interior a spherical, spring-loaded pilot valve member, which can be unlocked by an actuating device, which is designed here as a hydraulically actuated unlocking piston with an associated tappet.
  • the release piston When lowering with this check valve, the release piston rests against the poppet valve body, whereby the spherical pilot valve member is opened by the tappet and works as a simple check valve that controls a constant cross-section between the pressure chamber and the outlet.
  • the seat valve body has an axial notch on the outer circumference, which forms an adjustable throttle cross section between a pressure chamber of the working cylinder and the pressure chamber in the check valve.
  • the level of the hydraulic pressure at the unlocking piston is weighed against the force of the compression spring and the pressure in the pressure chamber and determines the stroke of the Check valve, which thus works with pure pilot control. A sequential control between the main control element and pilot control element is not possible.
  • a control device for the volume flow of a hydraulic working device in which a seat valve body cooperates with a pilot valve member arranged in it in the manner of a sequence control.
  • the pilot valve member which is actuated by a proportional magnet against the force of a spring, controls a connection from a pressure chamber on the seat valve body to the tank with its adjustable throttle point.
  • the seat valve body working as the main stage is formed here in the area of the main valve seat as a flat cone, which merges directly into a fine control cone, which can lead to discontinuities in the valve characteristic.
  • a control device is also known in which, with the aid of a finely controllable shut-off valve - a so-called lowering valve - it is achieved that, for example, the load acting on a consumer does not lead the associated pressure medium flow when lowering.
  • This check valve has a seat valve body in which a pilot valve member is guided. This pilot valve member projects into a closing bore with a control pin.
  • Such a check valve has the disadvantage that pressure medium can only drain when the control pin of the pilot valve member emerges from the drain hole.
  • the actuation path over which an actuating device must move the pilot valve member before the pressure medium can flow out is very long.
  • the control device with the characterizing features of the main claim has the advantage that the actuation paths for the check valve (lowering valve) are very short and the required actuation forces are low, so that the requirements for the use of proportional magnets as an actuating device are met.
  • the pressure medium flow can then be finely controlled. This is achieved by a sequential control of the pilot valve member and seat valve body, which is made possible by the shape of the seat valve body and the design of the pilot valve member. This ensures in particular a continuous, finely controllable outflow of the pressure medium from the pressure chamber of the working cylinder. Furthermore, by using seat valves in the closed state, extremely low leakages are achieved, so that loads are held for very long times.
  • FIG. 1 shows a hydraulic control device with a check valve in longitudinal section in FIG. 1, and a modification of the check valve in longitudinal section in FIG.
  • a pump 10 draws in pressure medium from a container 11, which is fed via a 3/2-way valve 12 and a check valve 13 to a single-acting working cylinder 14 and via a line branch 15 between working cylinder 14 and check valve 13 to a check valve 16 becomes.
  • the working cylinder 14 has a pressure chamber 17 in which a piston 18 with a piston rod 19 is guided.
  • a return line 20 leads from the shutoff valve 16 to the container 11.
  • the check valve 16 has a valve housing 21 which is penetrated in the longitudinal direction by a double-stepped bore, the bore sections of which are continuously designated 22a to 22c. This bore starts from a cylindrical recess 23, which in turn is embedded in an end face 24 of the housing 21.
  • annular grooves 25 to 28 are embedded in the central bore section 22b, the annular groove 25 being arranged in the central region of the bore section 22b.
  • the annular groove 28 is located at the transition to the bore section 22a, which is provided with an internal thread.
  • the annular groove 26 extending between the annular grooves 25 and 27 or 28 is wider and deeper and is connected via a pressure medium channel 29 penetrating the housing 21 to the line branch 15 leading to the working cylinder 14 or to the check valve 13.
  • a pressure medium channel 29 penetrating the housing 21 to the line branch 15 leading to the working cylinder 14 or to the check valve 13.
  • an annular groove 30 which is connected via a channel 31 penetrating the housing 21 to the return line 20 leading to the container 11.
  • valve housing 21 is closed on one side by a plug 33. This is inserted into the bore section 22b and, with a shoulder 34 of smaller diameter, lies against the annular shoulder 35 formed by the transition from the bore section 22b to the bore section 22c. To seal this paragraph 34 is surrounded by a sealing ring 36.
  • intermediate rings 37, 38 On the side of the plug 33 facing away from the bore section 22c there are intermediate rings 37, 38 arranged one behind the other, on which a cylindrical valve insert 39 is supported. This is fixed by a clamping screw 40 with a continuous hexagon socket 40a. This is screwed into the bore section 22a and bears against the lower end face 41 of the valve insert 39.
  • An axially extending bore 42 extends from this end face 41 in the valve insert 39 and opens into an axially aligned bore 43 of larger diameter.
  • This bore 43 starts from the end face 44 of the valve insert 39 resting on the intermediate ring 38.
  • the transition of the bores 42, 43 is designed as a main valve seat 45. In the area of this main valve seat 45, an annular groove 46 is arranged in the bore 43, from which a plurality of radially extending bores 47 extend, which penetrate the valve insert 39 and are connected to the annular groove 26 in the valve housing 21.
  • a seat valve body 51 is inserted into the valve insert 39 from the bore 43. This has a tapered section which interacts as a valve cone 52 with the main valve seat 45.
  • a cylindrical extension 53 extends from the valve cone 52 and protrudes into the annular groove 49 and merges there into an increase 54. This rise 54 widens conically to the diameter of the bore 42. The rise 54 is designed such that its largest diameter lies in the area of the bore 42 when the valve cone 52 abuts the main valve seat 45.
  • the rise 54 is followed by a short, cylindrical section 55 which, when the poppet valve body 51 is in the position described above, projects into the section of the bore 42 facing the end face 41.
  • This cylindrical section 55 merges into a tapered fine control cone 56 which projects through the bore 42 into the bore section 22a.
  • a cylindrical recess 59 is embedded in the end face 58 of the seat valve body 51 facing the intermediate rings 37, 38, from which a smaller longitudinal bore 60 extending in the same axis extends.
  • the base of the longitudinal bore 60 is conical towards the end face 63 and serves as a valve seat 61, which merges into an opposing, conical recess 62 which widens up to the opposite end face 63 of the seat valve body 51.
  • Two annular grooves 64, 65 are embedded in the longitudinal bore 60, of which the upper annular groove 64 extends in the region of the annular groove 47 of the valve insert 39.
  • the lower annular groove 65 lies at the transition the longitudinal bore 60 to the valve seat 61.
  • a further longitudinal bore 66 is arranged in the seat valve body, which extends from the end face 58 and extends eccentrically and axially parallel to the longitudinal bore 60.
  • This further longitudinal bore 66 extends into the area of the annular groove 64 and is connected to it.
  • the eccentrically arranged longitudinal bore 66 and the annular groove 47 in the valve insert 39 are connected to one another by a throttle bore 67 penetrating the seat valve body 51. Via the eccentric longitudinal bore 66 there is then a connection to a pressure chamber 68 which is formed in the bore 43 in the valve insert 39 between the plug 33 and the seat valve body 51.
  • a cylindrical pilot valve member 70 is inserted, which has a conically tapering section which interacts as a pilot valve cone 71 with the valve seat 61.
  • a cylinder section 72 of smaller diameter adjoining the pilot valve cone projects into the bore section 22a as far as the vicinity of the recess 23 and abuts there against the tappet 73 of a proportional magnet 69.
  • This proportional magnet 69 lies against the end face 24 of the valve housing 21 and closes it.
  • the connection is sealed by a sealing ring 74 inserted into the recess 23.
  • the longitudinal bore 60 of the seat valve body 51 is closed on one side by a plug 75. This is inserted into the recess 59 and projects with a shoulder 76 of smaller diameter into the longitudinal bore 60. In an annular groove 77 arranged in the shoulder 76, a sealing ring 78 is inserted for sealing, which bears against the wall of the longitudinal bore 60.
  • the plug 75 is fixed in place with a retaining ring 80 inserted into a corresponding annular groove 79 in the recess 59. This is designed so that between the paragraph 76 and the pilot valve member 70, a pressure chamber 81 is formed in the longitudinal bore 60 when the pilot valve member 70 bears against the valve seat 61 with its pilot valve cone 71.
  • a longitudinal bore 82 is arranged in the pilot valve member 70, which extends into the cylinder section 72.
  • the longitudinal bore 82 is connected to a transverse throttle bore 83 which penetrates the cylinder section 72.
  • An annular groove 84 is formed on the outer circumference of the pilot valve member 70 and is arranged in the region of the annular groove 65 of the seat valve body 51. Fine control notches 85 with a tapering cross-section extend from this annular groove 84 and extend as far as the annular groove 64. These fine control notches 85 are designed so that they just do not reach the annular groove 64 when the pilot valve cone 71 abuts the valve seat 61.
  • An approximately cup-shaped adjusting screw 87 is inserted into the valve housing 21 by screwing it into the bore section 22a, the bottom 88 of the adjusting screw facing the clamping screw 40 without reaching it.
  • a cylindrical extension 89 extends from the bottom 88 and merges into a truncated cone 90. This protrudes into the conical recess 62 of the seat valve body 51.
  • the cylindrical extension 89 and the truncated cone 90 are penetrated in the axial direction by two merging bores 91, 92 for the passage of the cylinder section 72 of the pilot valve member 70.
  • the bore 91 of smaller diameter runs in the truncated cone 90, its diameter is larger than that of the cylinder section 72.
  • the bore 92 of larger diameter is formed in the cylindrical extension 89 and starts from the interior 93 of the adjusting screw, which is designed as a hexagon socket.
  • the truncated cone 90 is designed such that the throttle bore 83 is located within the recess 62 and outside the bore 91 of the truncated cone 90 when both the pilot valve cone 71 abuts the valve seat 61 and the valve cone 52 on the main valve seat 45.
  • a compression spring 94 is supported, which comprises the cylinder section 72 of the pilot valve member 70 and whose opposite end abuts a pressure ring 95.
  • This pressure ring 95 encompasses the cylinder section 72 in the vicinity of the end face facing the plunger 73 and is secured against being pushed off by a ball segment 96 and a locking ring 97 which is inserted into an annular groove 98 in the cylinder section 72.
  • the check valve 13 prevents a pressure medium flow from the working cylinder 14 to the 3/2-way valve 12 Ring groove 46 build-up pressure acts via the throttle bore 67 and the bore 66 also in the pressure chamber 68 and in the annular groove 64 of the seat valve body 51.
  • This annular groove is sealed against the annular groove 65 by the pilot valve member 70.
  • the annular groove 49 in the valve insert 39 is sealed against the annular groove 30 and thus the return line 20 by the cylindrical section 55 of the fine control cone 56 located in the bore 42.
  • the seat valve body 51 is therefore additionally pressed by the action of the pressure in the pressure chamber 68 against the main valve seat 45 of the valve insert 39. This contact pressure is reduced by the force due to the effect of the pressure in the ring grooves 26 and 46 on the ring surface between the outer circumference of the seat valve body 51 and the effective sealing circumference on the main valve seat 45.
  • the pressure in the return line 20 (pressure in the container 11) prevails through the connection via the channel 31 also in the annular groove 30. From there past the truncated cone 90 via the throttle bore 83 there is a connection to the longitudinal bore 82 in the pilot valve member 70 and thus to the pressure chamber 81 There is still a connection to the interior 93 of the adjusting screw 87 via the annular space between the bore 91 and the cylinder section 72.
  • the pilot valve member 70 is moved upward by the plunger 73 via the cylinder section 72.
  • the pilot valve cone 71 stands out from the valve seat 61 and the fine control notches 85 reach the area of the annular groove 64.
  • the pressure medium under pressure in the pressure chamber 68 can then get into the annular groove 65 via the bore 66, the annular groove 64 and the fine control notches 85.
  • the pressure in the pressure chamber 68 drops as a function of the opening cross section (immersion depth of the fine control notches 85 in the region of the annular groove 64).
  • This pressure is established in accordance with the ratio of the throttle cross section at the throttle 67 and the opening cross section of the fine control notches 85. Falls accordingly far pushed up pilot valve member 70, the pressure in the pressure chamber 68 so far that the compressive forces in the annular groove 46 predominate on the annular surface between the outer circumference of the seat valve body 51 and the sealing circumference on the main valve seat 45, the seat valve body 51 is lifted from the main valve seat 45. Pressure medium from the annular groove 46 then flows past the opened main valve seat 45 into the annular groove 49. From there, there is a connection past the fine control cone 56, which is immersed in the annular groove 49, to the hexagon socket 40a. Pressure medium passes from there to the annular groove 30 and thus via the return line 20 to the container 11.
  • the opening movement of the seat valve body 51 reduces the relative displacement between the latter and the pilot valve member 70, so that the opening cross section at the fine control notches 85 becomes smaller. This allows a higher pressure to build up in the pressure chamber 68 via the throttle 67. Thus, the opening movement of the seat valve body 51 is braked until an equilibrium is reached. Pressure medium from the annular groove 46 or the line branch 15 can now flow out evenly, so that the load to be lowered on the working cylinder 14 does not lead ahead, and buzzing noises and jerking of the working cylinder are prevented.
  • the pilot valve member 70 follows this movement due to the action of the compression spring 94.
  • the opening cross section of the fine control notches 85 thus becomes even smaller or zero, so that the pressure in the pressure chamber 68 increases. Due to this increasing pressure in the pressure chamber 68 and the mechanical guidance of the pilot valve member 70 via the pilot valve cone 71 on the valve seat 61, the seat valve body 51 is also moved downward (sequential control).
  • the force to move the pilot valve member 70 is primarily dependent on the biasing force of the compression spring 94. This biasing force can be varied by a corresponding screwing depth of the adjusting screw 88.
  • the pilot valve member 70 is pressed via the tappet 73 of the proportional magnet 69 up to the shoulder 76 of the plug 75, so that the seat valve body 51 is thus moved.
  • the 3/2-way valve 12 is brought into the switching position II, so that pressure medium flows through the pump 10 via the check valve 13 in the through position to the working cylinder 14.
  • the check valve 16 is characterized - as already described - by the low required actuation forces and by short actuation paths.
  • the hydraulic forces on the pilot valve member 70 are almost equalized and dynamic pressures on the pilot valve member 70 in the region of the valve seat 71 or the adjusting screw 87 are avoided by the respective conical design of the poppet valve body and the adjusting screw 87 in the region of the truncated cone 90.
  • both the pilot control volume flow past the valve seat 71 and the main volume flow past the opened fine control cone 56 are diverted to the annular groove 30 without significant backpressures occurring in the area of the cylinder section 72 in the interior 93 of the adjusting screw 87.
  • valve cone 52 and fine control cone 56 Due to the spatial separation of valve cone 52 and fine control cone 56, these can be manufactured without great manufacturing outlay. If the seat valve body 51 is moved upward, the valve cone 52 lifts off the main valve seat 45. However, pressure medium cannot yet flow out of the annular groove 49, since the short cylindrical section 55 on the fine control cone 56 is still arranged within the bore 42 (gap seal). Only when this short cylindrical section 55 emerges from the bore 42 can the pressure medium flow increase as a function of the depth of immersion of the fine control cone 56. Discontinuities in the volume flow curve when the seat valve body is opened are thus avoided since the sealing point of the valve cone 52 on the main valve seat 45 is followed by the gap seal on the fine control cone 55, 56.
  • FIG. 2 shows a modified embodiment of the check valve, in which the design of the pilot valve member 70a and that of the seat valve body 51a are changed.
  • the pilot valve member 70a differs from that previously described by an elongated longitudinal bore 82a. This also penetrates the cylinder section 72a almost completely, ie it extends to the vicinity of its free end face.
  • a transverse throttle bore 100 opens into the longitudinal bore, which connects it to the interior 93 of the adjusting screw 87.
  • the throttle bore 83a is formed in the latter, which also opens into the longitudinal bore 82a.
  • the cylindrical section 55 on the seat valve body 51a merges into a cylindrical fine control section 56a of the same diameter.
  • triangular fine control notches 101 are arranged, which point towards the cylindrical section 55 and taper towards it.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Driven Valves (AREA)
  • Magnetically Actuated Valves (AREA)
  • Lift Valve (AREA)

Claims (11)

  1. Dispositif de commande du débit d'un dispositif actif hydraulique de préférence un vérin, comprenant une vanne d'arrêt (16) ayant un organe formant siège de vanne (51, 51a) coopérant avec un siège de vanne principal (45) solidaire du boîtier et recevant un organe de vanne de commande préalable (70, 70a) coopérant avec un dispositif de manoeuvre (69, 73), cet organe coopérant avec un siège de vanne (61) prévu dans l'organe formant siège de vanne, sous l'effet de la force d'un ressort (94) et commandant la pression dans une chambre de pression (68) formée entre l'organe formant siège de vanne et le boîtier de vanne (21, 33), l'organe formant siège de vanne étant poussé par l'action de cette pression contre le siège de vanne principal (45), caractérisé en ce que la chambre de pression (68) est reliée par un point d'étranglement (67) de section constante, en permanence avec la chambre de pression (17) du dispositif moteur (14), et par un point d'étranglement variable (64, 85) avec un réservoir (11) dont la section est variable par l'organe de vanne de commande préalable (70, 70a) et le dispositif de manoeuvre coopérant avec l'organe de vanne de commande préalable (70, 70a) est un aimant proportionnel (69) monté sur la vanne d'arrêt, l'organe formant siège de vanne (51, 51a) comportant un tiroir de commande fine (55, 56, 56a) prévu séparé géométriquement du siège de vanne principal (45) et le ressort (94) agissant sur l'organe de vanne de commande préalable (70, 70a) s'appuyant sur le boîtier et sur l'organe de vanne de commande préalable (70, 70a) et chargeant l'organe formant siège de vanne (51, 51a) en direction de ces sièges de vanne (61, 45).
  2. Dispositif de commande selon la revendication 1, caractérisé en ce que le point d'étranglement (67) a une section constante dans l'organe formant siège de vanne (51, 51a).
  3. Dispositif de commande selon la revendication 1 ou 2, caractérisé en ce que la section des points d'étranglement variables (64, 85) est modifiée par un décalage relatif de l'organe de vanne de commande préalable (70, 70a) par rapport à l'organe formant siège de vanne (51, 51a).
  4. Dispositif de commande selon l'une des revendications 1 à 3, caractérisé en ce que l'organe de vanne de commande préalable (70, 70a) peut être coulissé par l'aimant proportionnel (69) contre l'action d'un ressort de compression (94).
  5. Dispositif de commande selon l'une des revendications 1 à 4, caractérisé en ce que le siège de vanne principal (45) coopérant avec l'organe de siège de vanne (51, 51a) est prévu dans un insert de vanne (39) solidaire du boîtier.
  6. Dispositif de commande selon la revendication 5, caractérisé en ce que le tiroir de commande fine (55, 56, 56a) de l'organe formant siège de vanne (51, 51a) coopère avec un perçage (42) dans l'insert de vanne (39) solidaire du boîtier.
  7. Dispositif de commande selon l'une des revendications 1 à 6, caractérisé en ce que la vanne d'arrêt (16) comporte des moyens (90) pour diriger le flux, ces moyens évitant dans une très large mesure les pressions dynamiques lorsque la vanne d'arrêt (13) est ouverte.
  8. Dispositif de commande selon l'une des revendications 1 à 7, caractérisé en ce que le ressort (94) agissant sur l'organe de vanne de commande préalable (70, 70a) est prévu à l'extérieur de l'organe formant siège de vanne (51) et agit sur l'organe de vanne de commande préalable (70, 70a) en le tirant.
  9. Dispositif de commande selon l'une des revendications 1 à 8, caractérisé en ce que le diamètre actif du siège de vanne principal (45) et du tiroir de commande fine (55), sont de même dimension.
  10. Dispositif de commande selon la revendication 9, caractérisé en ce que les diamètres actifs du siège de vanne (71) et des encoches de commande fine (85) de l'organe de vanne de commande préalable (70, 70a) sont de mêmes dimensions.
  11. Dispositif de commande selon l'une des revendications 1 à 10, caractérisé en ce que l'organe de vanne de commande préalable (70, 70a) en aval du cône de vanne de commande préalable (71a) rejoint par un épaulement annulaire un segment cylindrique (72a) de plus petit diamètre qui traverse un perçage (91) pour arriver dans le volume intérieur (93) d'une vis de réglage (87), cette dernière logeant le corps de vanne de commande préalable (71a), et l'organe de vanne de commande préalable (70a) comporte un perçage longitudinal (82a) qui débouche dans une chambre de pression (81) appliquée contre la face frontale de l'organe de vanne de commande préalable (70a) et communique par un premier perçage d'étranglement (83a) avec le canal d'écoulement au niveau de l'épaulement annulaire et par un second perçage d'étranglement (100) avec le volume intérieur (93) de la vis de réglage (87).
EP92118860A 1991-12-10 1992-11-04 Dispositif de commande du courant d'un fluide de travail Expired - Lifetime EP0548513B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4140604 1991-12-10
DE4140604A DE4140604A1 (de) 1991-12-10 1991-12-10 Steuervorrichtung fuer den volumenstrom eines hydraulischen arbeitsmittels

Publications (2)

Publication Number Publication Date
EP0548513A1 EP0548513A1 (fr) 1993-06-30
EP0548513B1 true EP0548513B1 (fr) 1996-04-10

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP92118860A Expired - Lifetime EP0548513B1 (fr) 1991-12-10 1992-11-04 Dispositif de commande du courant d'un fluide de travail

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Country Link
US (1) US5290007A (fr)
EP (1) EP0548513B1 (fr)
DE (2) DE4140604A1 (fr)
RU (1) RU2102635C1 (fr)

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DE19955521A1 (de) 1999-11-18 2001-05-23 Bosch Gmbh Robert Vorrichtung zur Steuerung eines hydraulischen Volumenstroms zumindest eines belasteten Arbeitsmittels
DE19955524B4 (de) * 1999-11-18 2008-04-17 Robert Bosch Gmbh Vorrichtung zur Steuerung eines hydraulischen Volumenstroms eines belasteten Arbeitsmittels
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DE4032078C2 (de) * 1990-10-10 1997-08-07 Bosch Gmbh Robert Steuervorrichtung für einen hydraulischen Arbeitszylinder

Also Published As

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US5290007A (en) 1994-03-01
DE59205959D1 (de) 1996-05-15
EP0548513A1 (fr) 1993-06-30
RU2102635C1 (ru) 1998-01-20
DE4140604A1 (de) 1993-06-17

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