EP0717817A1 - Bloc a soupapes hydrauliques de commande - Google Patents

Bloc a soupapes hydrauliques de commande

Info

Publication number
EP0717817A1
EP0717817A1 EP94926905A EP94926905A EP0717817A1 EP 0717817 A1 EP0717817 A1 EP 0717817A1 EP 94926905 A EP94926905 A EP 94926905A EP 94926905 A EP94926905 A EP 94926905A EP 0717817 A1 EP0717817 A1 EP 0717817A1
Authority
EP
European Patent Office
Prior art keywords
valve
control
pressure
control valve
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP94926905A
Other languages
German (de)
English (en)
Other versions
EP0717817B1 (fr
Inventor
Helmut Stangl
Gerhard Beutler
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0717817A1 publication Critical patent/EP0717817A1/fr
Application granted granted Critical
Publication of EP0717817B1 publication Critical patent/EP0717817B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1204—Position of a rotating inclined plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/08—Pressure difference over a throttle
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/5109—Convertible
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/86582—Pilot-actuated
    • Y10T137/86614—Electric

Definitions

  • the invention relates to a hydraulic control valve block according to the preamble of claim 1.
  • the known control valve block is converted to the control valve block according to the invention by replacing the spring pressure part of its second control valve with the seat valve and decommissioning the valve piston of the second control valve.
  • one of the two hydraulic connections of the seat valve preferably its outlet, is connected to an existing hydraulic connection, preferably the tank connection of the control valve block, and the other hydraulic connection of the seat valve, preferably its inlet, is connected to the pressure medium channel additionally formed in the control valve block, which preferably opens into the control pressure channel of the first control valve with the lower control pressure.
  • the first control valve When the seat valve is completely closed, the first control valve maintains its function, ie it works, for example, as a differential pressure valve, the activation of which with the differential pressure can be changed in a targeted manner by opening the seat valve in accordance with the relief of the lower of the two control pressures resulting from the differential pressure. As soon as the lower control pressure is reduced to zero, the first control valve works as a pressure valve; it can therefore be used with the help of the seat valve for both flow rate and pressure control.
  • the control of the seat valve can be arbitrary or depending on the field of application of the control valve block depending on various parameters, such as the speed of a drive motor for the pump, the working pressure of the same using a corresponding pressure / current converter or the temperature of the coolant when used in a hydraulic fan drive for the cooling system of an internal combustion engine.
  • the control valve block converted and designed in this way has the same function as the combination of this external seat valve and the control valve block before the conversion, namely that of the flow rate, with considerably less construction and assembly effort due to the elimination of the external, electrically controlled seat valve by accommodating the same instead of the second control valve and pressure control with remote-controlled change in the characteristic curve of the former control and automatic hydraulic switchover from one to the other control.
  • the seat valve can be controlled in the direction of the open position in addition to the electrical control with the hydraulic input pressure prevailing at its valve input.
  • the control part can be of a switching or proportional design and act against a spring acting on the poppet valve in the direction of the closed position, which advantageously has such a characteristic that when its response pressure is reached, the pressure increase between the beginning and end of opening (at full flow) is as small as possible.
  • control part with two proportional nal act opposite directions of action, one of which acts upon the valve body of the seat valve in the direction of the closed position and thus, possibly with a relatively weak spring also acting in the closed position, determines the pressure value at which the hydraulic inlet pressure pushes the seat valve from the closing position the openness switches; the other proportional solenoid acts on the valve body of the poppet valve in the direction of open opening.
  • valve piston can be shut down either by means of fixation by the poppet valve or by a piston which is replaced by it and which
  • This piston is preferably shut down by a spring
  • the spring expediently acts on the valve body of the seat valve in the direction of the closed position.
  • FIG. 1A is a longitudinal section of a control valve block with a piston and a seat valve according to the first embodiment of the invention
  • FIG. 1B is a circuit diagram of the control valve block of FIG. 1A
  • FIG. 2A shows a longitudinal section of a control valve block with a piston valve and a seat valve according to the second exemplary embodiment of the invention.
  • Fig. 2B is a circuit diagram of the control valve block according to Fig. 2A.
  • FIG. 3A and 3B will be described first, since it represents the basic construction from which the control valve blocks according to FIGS. 1A, 1B, 2A and 2B result from simple retrofitting and retrofitting with the additional pressure medium channel .
  • 3A is a longitudinal section of the known control valve block and
  • FIG. 3B is a circuit diagram of the control valve block according to FIG. 3A.
  • 3A comprises a housing 1, a first control valve 2 and a second control valve 3, both of which are designed as throttling 3/2-way valves and each have a valve bore passing through the housing 1, and a valve piston 4 slidably guided in the valve bore 4 or 5 and each include a spring pressure part 6 or 7.
  • Each spring pressure part 6, 7 is screwed into a bore extension of the valve bore opening at the right end of the housing 1 in the drawing and comprises a spring housing 8 or 9, one between two spring plates 10, 11 or 12, 13 in the spring housing 8 or 9 clamped helical compression spring assembly 14 or 15 and an adjusting member 16 or 17 consisting of a tensioning piston 18 or 19 with external thread, which engages in the drawing on the right outer housing plate 11 or 13, and one on the tensioning piston 18 or 19 screwed screw arrangement 20 or 21 for changing the pretension of the helical compression spring arrangement 14 or 16.
  • Both spring pressure parts 6, 7 thus act on the valve pistons 4 or 5 in the direction of the opening closed by a closure part 22 or 23 the respective valve bore on the left side of the housing 1 in the figure, with between each closure part 22 and 23 and the front side of the arranged valve piston 4 or 5, a hydraulic pressure chamber 24 or 25 is formed.
  • the housing 1 has five hydraulic connections: a first hydraulic connection P, a second hydraulic connection A, a third, to the tank leading tank connection T and a fourth hydraulic connection D (only shown in FIG. 3A) with a subsequent, up to the valve bore of the second control valve 3 extending first pressure medium channel 26 for receiving an adjustable throttle valve DV, as is principally described in DE 41 32 709 is described.
  • the fifth hydraulic connection X identified by an arrow on the upper side of the housing 1 in the drawing, leads directly into the spring chamber 27 of the first control valve 2.
  • a second pressure medium channel 28 runs from the hydraulic connection P in the housing 1 with a first channel section 28a to the valve bore of the second control valve 3 and from this with a second channel section 28b to the valve bore of the first control valve 2.
  • a third pressure medium channel 29 extends with a first channel section 29a to the valve bore of the second control valve 3, in order to move from there with a second channel section 29b, which is offset in the valve piston direction and aligned with the first pressure medium channel 26, to the valve bore of the second control valve 3 continue the first control valve 2.
  • a fourth pressure medium channel 30 runs from the tank connection T with a first channel section 30a to the valve bore of the second control valve 3 and from this with a second channel section 30b to the valve bore of the first control valve 2.
  • the channel sections 30a and 30b are only in the Longitudinal section of the control valve block, but not shown in the circuit diagram.
  • a fifth pressure medium channel 31 with a throttle point 32 connects a connecting channel 33 connected to the spring chamber 27 of the first control valve 2 to the second channel section 30b of the fourth pressure medium channel 30.
  • a sixth pressure medium channel 34 connects the spring chamber 35 of the second control valve 3 to the first channel sections 30a, 26a and 29a of the pressure medium channels 30, 26 and 29.
  • the valve piston 4 of the first control valve 2 contains three ring channels, which are denoted in the drawing from left to right with the reference numerals 37, 38, 39, a longitudinal bore 40 and a shoulder 41 with the same diameter as the spring plate 10 of the spring pressure part 6 the valve piston in the area of the ring channels.
  • the annular area delimited by the extension 41 on the valve piston 4 delimits a further hydraulic pressure chamber 42 of the first control valve 2, which is connected to the connecting channel 33.
  • the longitudinal bore 40 extends from the left end face of the valve piston 4 in the figure to a radial bore 43 which opens out on the peripheral surface of the extension 41.
  • Another radial bore 44 connects the longitudinal bore 40 to the circumferential surface of the valve piston 4 in the region of the annular channel 37.
  • the radial bore 44 and the section of the longitudinal bore 40 leading from it to the hydraulic pressure chamber 24 provide a connection to the second channel section 28a of the second pressure medium channel 28 represents the first control pressure channel 45.
  • the radial bores 43, 44, the section of the longitudinal bore 40 running between them, represent a second control pressure channel 46 which leads to the further hydraulic pressure chamber 42 and has a throttling effect, as indicated by the throttle 47 shown in the circuit diagram according to FIG. 3B.
  • the valve piston 5 of the second control valve 3 contains three ring channels, which are designated in the drawing from left to right with the reference numerals 48, 49, 50 and a longitudinal bore 51 which extends from the left end face of the valve piston 5 in the figure to one Radial bore 52 extends, which opens out on the peripheral surface of the valve piston 5 in the region of the annular channel 48.
  • the longitudinal bore 51 and the radial bore 52 represent a control pressure channel designated by reference numeral 53, which connects the first channel section 28a of the second pressure medium channel 28 to the hydraulic pressure chamber 25 of the second control valve 3.
  • 3A and 3B is used in the present exemplary embodiment for regulating the flow rate and pressure of an axial piston pump 100 of a hydraulic fan drive (not shown) for the cooling system of an internal combustion engine (not shown).
  • the hydraulic connection P is connected via a connecting line 101 to a working line 102 connected to the outlet of the axial piston pump 100, the hydraulic connection A via a signal pressure line 103 to the hydraulic pressure chamber 104 of an actuating cylinder 105 for adjusting the delivery volume of the axial piston pump 100 and the tank connection T via a relief line 106 is connected to the tank 107.
  • the actuating piston 108 of the actuating cylinder 105 is acted upon by a spring 109 in the direction of reducing the hydraulic pressure chamber 104 and thus increasing the delivery volume of the axial piston pump 100.
  • the working line 102 leads to a hydraulic motor, not shown, which drives a fan wheel, also not shown, which is arranged in the region of the cooler of the internal combustion engine.
  • the compression spring arrangement 15 of the second control valve 3 is set to a higher pressure value than the compression spring arrangement 14 of the first control valve 2, so that the latter control valve 2 is superimposed by the former control valve 3, i.e. performs its flow control function only below the set pressure value of the compression spring arrangement 15.
  • both control valves 2, 3 are in their respective starting position shown in the drawing: the valve piston 5 of the second control valve 3 connects with its ring channels 48, 49 and 50 the respective channel sections 28a and 28b, 29a and 29b and 30a and 30b of the individual print medium channels 28, 29 and 30 with one another, but without establishing connections between these print medium channels themselves; the valve piston 4 of the first control valve 2 blocks the channel section 28b of the second pressure medium channel 28 and connects the channel sections 29b and 30b of the pressure medium channels 29 and 30 to one another with its ring channel 38.
  • the hydraulic pressure chamber 104 of the actuating cylinder 105 is connected to the working line 102, so that the working pressure prevailing therein displaces the actuating piston 108 against the pressure of the spring 109 as the actuating pressure.
  • the axial piston pump 100 is pivoted back to a smaller delivery volume until the delivery volume flow corresponding to the set pressure value (setpoint) of the compression spring arrangement 14 of the first control valve 2 is reached again.
  • the working pressure in the working line 102 is present via the connecting line 101, the first channel section 28a of the second pressure medium channel 28 and the control pressure channel 53 in the hydraulic pressure chamber 25 of the second control valve 3 and acts on its valve piston 5 against the pressure of the pressure spring arrangement 15.
  • valve piston 5 As soon as the hydraulic force of the working pressure exceeds the force of the compression spring arrangement 15, it shifts the valve piston 5 in the drawing to the right in the direction of the end position until it is in force equilibrium is located and thus assumes a control position corresponding to the working pressure, in which the valve piston 5 connects with its annular channel 48 the channel section 28a of the second pressure medium channel 28 to the channel section 29a of the third pressure medium channel 30, the connection of the channel sections 30a and 30b of the fourth pressure medium channel 30 maintains and blocks the channel section 29b of the third pressure medium channel 29.
  • the hydraulic pressure chamber 104 of the actuating cylinder 105 is connected to the working line 102, so that the working pressure prevailing therein displaces the actuating piston 108 as the actuating pressure against the pressure of the spring 109 while pivoting the axial piston pump 100 back to a smaller delivery volume until the working pressure in the working line 2 corresponding to the set pressure value (target value) of the compression spring arrangement 15 is reached again.
  • the actuating pressure present in the hydraulic pressure chamber 104 of the actuating cylinder 105 can be built up with a delay and thus an abrupt response of the actuating piston 108 can be prevented.
  • an external, preferably electrically controllable pressure relief valve (not shown) is connected to the hydraulic pressure chamber 42 of the first control valve 2, with which the pressure difference acting on the valve piston 4 can be changed in a targeted manner and thus the flow control can be influenced .
  • Figures 1A and 1B show the control valve block according to the invention according to the first embodiment, which differs from the known control valve block according to Figures 3A and 3B with otherwise the same construction by an additional, seventh pressure medium channel 36 and further in that the hydraulic connection X is closed and that second control valve 3 for pressure control is replaced by a pressure relief valve 60.1, as is connected, for example, as an external pressure relief valve via the hydraulic connection X to the control valve block according to FIGS. 3A and 3B.
  • the seventh pressure medium channel 36 connects the bore extension of the valve bore of the second control valve 3 with the section of the fifth pressure medium channel 31 between the spring chamber 27 of the first control valve 2 and the throttle point 32.
  • the pressure relief valve 60.1 is a seat valve, the exchange of which takes place in that after unscrewing the spring pressure part 7 from the bore extension of the valve bore of the second control valve 3 and removing the valve piston 5 from this valve bore, a piston 61 is inserted into the latter and then the pressure relief valve 60.1 is screwed into the bore extension of the valve bore.
  • the pressure relief valve 60.1 comprises a valve housing 62.1, in which a flow channel 65.1 connecting a valve inlet 63 with a valve outlet 64.1 is formed, and a conventional electromechanical control part 66.1 with a proportional magnet 67 screwed onto the valve housing 62.1 and projecting from the bore extension.
  • the valve housing 62.1 blocks the part of the sixth pressure medium channel 34 leading to the first channel section 30a of the fourth pressure medium channel 30.
  • the valve inlet 63 is formed in the valve housing 62.1 at a location such that it is connected to the seventh pressure medium channel 36.
  • the valve housing 62.1 further comprises a conical valve seat 68 through which the flow channel 65.1 passes, a closing element 69.1 in the form of a conical valve body and a spring 70.1 which presses the closing element 69.1 against the valve seat 68 and thus blocks the flow channel 65.1.
  • the spring 70.1 is supported on the piston 61 projecting through the valve outlet 64.1 into a valve housing bore 71, as a result of which the piston 61 is pressed against the closure part 23 and is thus shut down.
  • the piston 61 contains three ring channels, which are designated in the drawing from left to right with the reference numerals 72, 73 and 74 and the first channel sections 28a, 30a and 29a of the second and third pressure medium channels 28 and 29 with their second channel sections 28b , 30b and 29b and the latter connect to the first pressure medium channel 26. Since the valve bore in the control valve block housing 1 and the valve housing bore 71 have the same diameter, the annular channel 74, which is open up to its front side on the right in the drawing, that is to say only limited on one side by the piston part 75 of larger diameter, forms the part of the flow channel 65.1 extending in the valve housing bore 71 and one in the valve bore of the control valve block housing 1 fourth pressure medium channel 30 opening connection channel 76.
  • a longitudinal through bore 77 in the piston 61 is used to leak oil that accumulates between the closure member 23 and the abutting end face of the piston 61, via the spring chamber 78 of the pressure relief valve 60.1 and the annular channel 74 to the fourth pressure medium - Discharge channel 30 and thus to tank 107.
  • the end of the closing element 69.1 facing away from the piston 61 projects into a pressure chamber 79 formed by an expansion of the flow channel 65.1 and has a smaller cross-sectional area than an actuating plunger 80.1 of the control part 66.1, against which the closing element 69.1 bears under the pressure of the spring 70.1.
  • the control part 66.1 can be arbitrary and / or depending on various parameters, such as a control current proportional to the temperature of the coolant for the internal combustion engine or the working pressure in the working line 102.
  • the control block according to FIGS. 1A and 1B like that according to FIGS. 3A and 3B, with its hydraulic connections P, A and T can be connected to the connecting line 101, the actuating pressure line 103 or the relief line 106 and for flow rate and pressure control the axial piston pump 100 are used.
  • the closing element 69.1 which is only acted upon by the spring 70.1, blocks the flow channel 65.1 of the pressure limiting valve 60.1 and in this way prevents relief of the control pressure present in the hydraulic pressure chamber 42 of the first control valve 42 and thus a change in the valve piston 4 of this control valve acting pressure difference.
  • the latter is thus still a measure of the delivery volume flow of the axial piston pump 100 and consequently enables the delivery flow control already described above by the first control 1 valve 2.
  • the actuating plunger 80.1 When the control part 66.1 is actuated, the actuating plunger 80.1 is extended by the magnetic field built up in the proportional magnet 67 and 5 shifts the closing element 69.1 by a distance proportional to the strength of the control current in the direction of the open position.
  • the hydraulic pressure chamber 42 of the first control valve 2 is connected to the tank 107 via the seventh pressure medium channel 36, the pressure relief valve 60.1, the connecting channel 76, the first channel section 30a of the fourth pressure medium channel 30 and the "L Q relief line 106
  • the control pressure in the pressure chamber 42 is reduced and the delivery flow control carried out with the first control valve 2 is changed.
  • the second control valve 3 in the control valve block according to FIGS. 3A and 3B carries out the pressure control.
  • FIGS. 2A and 2B show a control valve block, which differs from the control valve block according to FIGS. 1A and 1B with otherwise the same
  • the control part 66.2 of the pressure relief valve 60.2 comprises a double stroke magnet, ie two proportional magnets 81, 82 with opposite directions of action, and an actuating plunger 80.2
  • the closing element 69.2 of the pressure-limiting valve 60.2 comprises a measuring surface 83 that can be acted upon by the pressure medium in the pressure chamber 79.
  • the pressure-limiting valve 60.2 comprises
  • valve 60.1 a modified valve housing 62.2 and a weaker spring 70.2.
  • the spring 70.2 is supported on the valve housing 62.2, which presses the valve piston 5 against the closure part 23 and thereby stops it.
  • the actuating plunger 80.2 is connected to the closing element 69.2.
  • the proportional magnet 81 has the same direction of action and function as the proportional magnet 67 according to Fig. 1A, i.e. the magnetic field that he builds up when actuated moves the actuating plunger 80.2 and thus the closing element 69.2 by a distance corresponding to the strength of the control current in the direction of the open position.
  • the pressure relief valve 60.2 can thus be partially or fully opened and the flow control carried out by the first control valve 2 when the pressure relief valve 60.2 is blocked can thus be influenced or switched to pressure control.
  • the proportional magnet 82 has the opposite direction of action as the proportional magnet 81 and, when the proportional magnet 81 is not actuated, serves to press the closing element 69.2 against the valve seat 68 with a force corresponding to the control current, i.e.
  • the closing element 69.2 opens completely and thereby switches the first control valve 2 from the flow control to the pressure control when the hydraulic force of the input pressure acting on the measuring surface 83 is the force exceeds, with which the controlled proportional magnet 82 presses the closing element 69.2 against the valve seat 68.
  • the changeover from the flow control to the pressure control is thus carried out in the same way as with the control valve block according to FIGS. 3A and 3B under the direct influence of the working pressure (neglecting the relatively small pressure difference at the throttle 47).
  • the connecting channel 76 is omitted; instead, the flow channel 65.2 is connected via the valve outlet 64.2 to the sixth pressure medium channel 34 leading to the tank connection T.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Safety Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Servomotors (AREA)

Abstract

Un bloc standard à soupapes hydrauliques de commande comprend une première soupape de commande (2) et une deuxième soupape de commande (3) en communication avec la première soupape par l'intermédiaire de conduites de fluide hydraulique (28-31, 33) et qui coopère avec la première soupape. La deuxième soupape de commande (3) comprend un piston de soupape (5) commandé, d'une part, par une pression hydraulique de commande dans une chambre de pression (25), et, d'autre part, par une partie de pression montée sur ressort (7). Afin de simplifier la construction et le montage du bloc à soupapes de commande sans affecter son fonctionnement et en utilisant une soupape à siège télécommandée, une conduite supplémentaire de fluide hydraulique (36) est montée dans le bloc à soupapes de commande, et la partie de pression à ressort (7) de la deuxième soupape de commande (3) est remplacée par une soupape à siège (60.1; 60.2) à commande électrique. La soupape à siège (60.1; 60.2) comprend une partie de commande électromécanique (66.1; 66.2) et au moins deux raccords hydrauliques (63.1; 64.1) qui servent d'admission (63) et de sortie (64.1; 64.2) de la soupape. Le piston (5) de la deuxième soupape de commande (3) est au repos, de sorte qu'un (64.1; 64.2) des deux raccords hydrauliques (63, 64.1; 64.2) de la soupape à siège (60.1; 60.2) soit en même temps raccordé à un raccord hydraulique existant (T) et que l'autre raccord hydraulique (63) soit raccordé à la conduite supplémentaire de fluide hydraulique (36).
EP94926905A 1993-08-30 1994-08-29 Bloc a soupapes hydrauliques de commande Expired - Lifetime EP0717817B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4329164A DE4329164C2 (de) 1993-08-30 1993-08-30 Hydraulischer Steuerventilblock
DE4329164 1993-08-30
PCT/EP1994/002857 WO1995006818A1 (fr) 1993-08-30 1994-08-29 Bloc a soupapes hydrauliques de commande

Publications (2)

Publication Number Publication Date
EP0717817A1 true EP0717817A1 (fr) 1996-06-26
EP0717817B1 EP0717817B1 (fr) 1998-04-15

Family

ID=6496359

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94926905A Expired - Lifetime EP0717817B1 (fr) 1993-08-30 1994-08-29 Bloc a soupapes hydrauliques de commande

Country Status (5)

Country Link
US (1) US5778924A (fr)
EP (1) EP0717817B1 (fr)
JP (1) JPH09502008A (fr)
DE (2) DE4329164C2 (fr)
WO (1) WO1995006818A1 (fr)

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DE102014202412A1 (de) 2014-02-11 2015-08-13 Robert Bosch Gmbh Elektrisch angesteuertes Druckregelventil für eine verstellbare hydrostatische Pumpe und verstellbare hydrostatische Pumpe mit einem Druckregelventil
DE102016215993A1 (de) 2016-08-25 2018-03-01 Robert Bosch Gmbh Hydraulische Regelvorrichtung
DE102017222355A1 (de) * 2017-12-11 2019-06-13 Robert Bosch Gmbh Ansteuervorrichtung mit elektroproportionalem Regelverhalten und Doppel-Magnetspule

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Also Published As

Publication number Publication date
JPH09502008A (ja) 1997-02-25
US5778924A (en) 1998-07-14
DE4329164A1 (de) 1995-03-09
EP0717817B1 (fr) 1998-04-15
DE4329164C2 (de) 1998-02-19
DE59405730D1 (de) 1998-05-20
WO1995006818A1 (fr) 1995-03-09

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