EP0717817B1 - Bloc a soupapes hydrauliques de commande - Google Patents

Bloc a soupapes hydrauliques de commande Download PDF

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Publication number
EP0717817B1
EP0717817B1 EP94926905A EP94926905A EP0717817B1 EP 0717817 B1 EP0717817 B1 EP 0717817B1 EP 94926905 A EP94926905 A EP 94926905A EP 94926905 A EP94926905 A EP 94926905A EP 0717817 B1 EP0717817 B1 EP 0717817B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
hydraulic
control
control valve
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
EP94926905A
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German (de)
English (en)
Other versions
EP0717817A1 (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

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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 Claim 1.
  • DE-A-3 443 265 discloses a control valve in which no throttle is provided. A flow control according to the control principle described above is therefore not possible with the control valve known from this publication.
  • DE-A-3 914 485 discloses another hydraulic circuit and requires that Use of a total of three valves, namely a flow control valve, one Check valve and a pilot valve.
  • the seat valve can additionally be used for electrical control with the prevailing at its valve input hydraulic inlet pressure in the direction of the open position.
  • the control part of switching or proportionally acting Be execution and against a seat valve in the closed position act spring, which expediently such a characteristic has that when their 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 magnets opposite directions of action, one of which the Valve body of the seat valve is subjected to force in the direction of the closed position and thus, if necessary with a likewise acting in the closed position, relative weak spring, determines the pressure value at which the hydraulic inlet pressure the seat valve switches from the closed to the open position; of the other proportional magnet acts on the valve body of the seat valve in Towards open position.
  • the valve piston can either be fixed by the seat valve or be shut down by a piston exchanged for him, which the Actuation of the said pressure chamber with the control pressure blocks.
  • This piston is preferably shut down by a spring Position held, which can be supported on the valve body of the seat valve.
  • the spring expediently acts on the valve body of the seat valve in Direction of the closed position.
  • FIG. 3A and FIG. 3B the control valve block known from practice is shown in FIG. 3A and FIG. 3B because it represents the basic construction from which by easy retrofitting and retrofitting with the additional pressure medium channel Control valve blocks according to FIGS. 1A, 1B, 2A and 2B emerge.
  • 3A shows a longitudinal section of the known control valve block
  • FIG. 3B Circuit diagram of the control valve block according to Fig. 3A.
  • the control valve block according to Fig. 3A comprises a housing 1, a first Control valve 2 and a second control valve 3, both as throttling 3/2-way valves are formed and one continuous in the housing 1 Valve bore, one each slidably guided in the valve bore Valve piston 4 or 5 and each include a spring pressure part 6 or 7.
  • Each spring pressure part 6, 7 is in each one on the right in the drawing End face of the housing 1 opening bore extension of the valve bore screwed in and includes a spring housing 8 and 9, one between two Spring plates 10, 11 or 12, 13 clamped in the spring housing 8 or 9 Helical compression spring arrangement 14 or 15 and an adjusting member 16 or 17 consisting of a tensioning piston 18 or 19 with external thread, which on the in the drawing right, housing outer spring plate 11 or 13 attacks, and a screw arrangement 20 screwed onto the tensioning piston 18 or 19 or 21 for changing the pretension of the helical compression spring arrangement 14 and 16.
  • Both spring pressure parts 6, 7 thus act on the valve pistons 4 or 5 in the direction of the closed by a closure member 22 or 23 Opening of the respective valve bore on the left in the figure End face of the housing 1, between each closure member 22 and 23 and the end of the associated 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 in Fig. 3A shown) with a subsequent, up to the valve bore of the second control valve 3 extending first pressure medium channel 26 Inclusion of an adjustable throttle valve DV, as it is in principle in the DE 41 32 709 is described.
  • a second pressure medium channel runs from the hydraulic connection P in the housing 1 28 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 for valve bore of the first control valve 2.
  • a third pressure medium channel 29 extends from the hydraulic connection A. with a first channel section 29a to the valve bore of the second Control valve 3 to move from there with one in the valve piston direction offset, second aligned with the first pressure medium channel 26 Channel section 29b up to the valve bore of the first control valve 2 to continue.
  • 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 passage portions 30a and 30b are only in the longitudinal section of the control valve block, but not in the circuit diagram, shown.
  • a fifth pressure medium channel 31 with a throttle point 32 connects one connected to the spring chamber 27 of the first control valve 2 connecting channel 33 with the second channel section 30b of the fourth print medium channel 30th
  • a sixth pressure medium channel 34 connects the spring chamber 35 of the second Control valve 3 with the first channel sections 30a, 26a and 29a Media channels 30, 26, and 29.
  • the valve piston 4 of the first control valve 2 contains three ring channels in the drawing from left to right with the reference numerals 37, 38, 39 are designated, a longitudinal bore 40 and one on the spring plate 10 of the Spring pressure part 6 adjacent shoulder 41 with the same diameter as the Valve piston in the area of the ring channels.
  • the one limited by approach 41 Annular surface 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 is.
  • the longitudinal bore 40 runs from the left end face in the figure of the valve piston 4 up to a radial bore 43 which at the Circumferential surface of the approach 41 opens out.
  • Another radial bore 44 connects the longitudinal bore 40 with the peripheral surface of the valve piston 4 in Area of the annular channel 37.
  • the radial bore 44 and from this to hydraulic pressure chamber 24 leading section of the longitudinal bore 40 provides one to the second channel section 28a of the second print medium channel 28 connected first control pressure channel 45.
  • Section of the longitudinal bore 40 is a second control pressure channel 46 which for leads another hydraulic pressure chamber 42 and has a throttling effect, as shown by the throttle 47 shown in the circuit diagram of FIG. 3B is indicated.
  • the valve piston 5 of the second control valve 3 contains three ring channels in the drawing from left to right with the reference numerals 48, 49, 50 are designated and a longitudinal bore 51, which differs from that in the figure left end face of the valve piston 5 up to a radial bore 52 extends on the circumferential surface of the valve piston 5 in the region of Ring channel 48 opens out.
  • the longitudinal bore 51 and the radial bore 52 represent a control pressure channel designated by reference numeral 53, which the first channel section 28a of the second pressure medium channel 28 with the hydraulic pressure chamber 25 of the second control valve 3 connects.
  • FIGS. 3A and 3B The control valve block of FIGS. 3A and 3B is described herein Embodiment for flow rate and pressure control of an axial piston pump 100 of a hydraulic fan drive, not shown, for the Cooling system of an internal combustion engine (not shown) used.
  • the purpose is the hydraulic connection P 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 connected to the tank 107.
  • the actuating piston 108 of the actuating cylinder 105 is by a spring 109 in the direction of reducing the hydraulic Pressure chamber 104 and thus increase in the delivery volume of the axial piston pump 100 applied.
  • the work line 102 leads to a not shown Hydraulic motor, which is arranged in the area of the cooler of the internal combustion engine, also drives the fan wheel, not shown.
  • the compression spring arrangement 15 of the second control valve 3 is at a higher level Pressure value as the compression spring arrangement 14 of the first control valve 2 set so that the latter control valve 2 of the former control valve 3rd is superimposed, i.e. only below the set pressure value of Compression spring assembly 15 performs its flow control function.
  • both control valves are located 2, 3 in their respective starting position shown in the drawing:
  • the valve piston 5 of the second control valve 3 connects to his 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 each other, but without connections between these pressure medium channels self-made;
  • the valve piston 4 of the first control valve 2 locks the channel section 28b of the second pressure medium channel 28 and connects to its ring channel 38, the channel sections 29b and 30b of the pressure medium channels 29 and 30 with each other.
  • the working pressure in the working line 102 is 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 on and acts on its valve piston 5 against the pressure of the compression spring arrangement 15.
  • Via the hydraulic connection X of the control valve block described above is at the hydraulic pressure chamber 42 of the first control valve 2 external, preferably electrically controllable pressure relief valve (not shown) connected with which the acting on the valve piston 4 Pressure difference specifically changed and thus affects the flow control can be.
  • FIGS. 1A and 1B show the control valve block according to the invention the first embodiment, which differs from the known control valve block 3A and 3B with otherwise the same construction by a additional, seventh print medium channel 36 and further distinguished by that the hydraulic connection X is closed and the second control valve 3 for the pressure control is replaced by a pressure relief valve 60.1, as it is, for example, as an external pressure relief valve via the hydraulic connection X on the control valve block according to Figures 3A and 3B connected.
  • 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 replacement thereof takes place that after unscrewing the spring pressure member 7 from the bore extension the valve bore of the second control valve 3 and removing the Valve piston 5 from this valve bore a piston 61 in the latter used and then the pressure relief valve 60.1 in the bore extension the valve bore is screwed in.
  • the pressure relief valve 60.1 comprises a valve housing 62.1 in which a a flow channel connecting a valve inlet 63 with a valve outlet 64.1 65.1, and a screwed onto the valve housing 62.1, Outstanding, conventional from the bore extension electromechanical control part 66.1 with a proportional magnet 67.
  • Das Valve housing 62.1 blocks the first channel section 30a of the fourth Media channel 30 leading part of the sixth media channel 34.
  • Der Valve inlet 63 is at such a point in valve housing 62.1 formed to be in communication with the seventh pressure medium channel 36 stands.
  • 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 the Closing element 69.1 presses against the valve seat 68 and thus the flow channel 65.1 blocks.
  • the spring 70.1 is supported by the valve outlet 64.1 in a valve housing bore 71 protruding piston 61, whereby this is pressed against the closure part 23 and in this way is shut down.
  • the piston 61 contains three ring channels, which in the drawing from left to right are designated by the reference numerals 72, 73 and 74 and the first channel sections 28a, 30a and 29a of the second and third, respectively Print medium channels 28 and 29 with their second channel sections 28b, 30b or 29b and the latter connect to the first pressure medium channel 26.
  • the valve bore in the control valve block housing 1 and the valve housing bore 71 have the same diameter, which forms up to it in the drawing right end face open, so only one side of the piston part 75 larger Diameter-limited ring channel 74 in the valve housing bore 71 extending part of the flow channel 65.1 and in the valve bore of the Control valve block housing 1 in the fourth pressure medium channel 30 opening connecting channel 76.
  • a longitudinal through hole 77 in Piston 61 serves to leak oil that is between the closure member 23 and the adjacent face of the piston 61 accumulates via the spring chamber 78 of the Pressure relief valve 60.1 and the ring channel 74 to the fourth pressure medium channel 30 and thus to be discharged to tank 107.
  • the end of the closing element 69.1 facing away from the piston 61 projects into one pressure space 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, on which the closing element 69.1 under the Pressure of spring 70.1 is present.
  • the control part 66.1 can be arbitrary and / or depending on various parameters, e.g. one of the temperature of the coolant for the internal combustion engine or the working pressure in the working line 102 proportional control current.
  • the control block according to FIGS. 1A and 1B can, like that according to FIGS 3A and 3B with its hydraulic connections P, A and T to the Connection line 101, the signal pressure line 103 or the relief line 106 connected and for flow and pressure control of the Axial piston pump 100 can be used.
  • the actuating plunger 80.1 is actuated by the magnetic field built up in the proportional magnet 67 is extended and shifts the closing element 69.1 by one of the strength of the control current proportional distance in the direction of the open position.
  • the hydraulic pressure chamber 42 of the first control valve 2 via the seventh Pressure medium channel 36, the pressure relief valve 60.1, the connection channel 76, the first channel section 30a of the fourth print medium channel 30 and Relief line 106 connected to the tank 107.
  • Degree of opening of the pressure relief valve 60.1 is the control pressure in the Pressure chamber 42 is reduced and thus that with the first control valve 2 performed flow control changed.
  • Control part 66.1 is fully opened, the control pressure in the Pressure chamber 42 to zero, so that the first control valve 2 only from that Working pressure in the working line 102 proportional control pressure in the hydraulic pressure chamber 24 is controlled and thus in the same way as the second control valve 3 in the control valve block according to FIGS. 3A and 3B Pressure control.
  • FIGS 2A and 2B show a control valve block, which differs from Control valve block according to Figures 1A and 1B with otherwise the same Construction by using the valve piston 5 of FIG. 3A instead of Piston 61 and a modified pressure relief valve 60.2 differs.
  • the control part 66.2 of the pressure relief valve 60.2 includes one Double solenoids, i.e. two proportional magnets 81, 82 with each other opposite directions of action, and an actuating plunger with 80.2 smaller cross-sectional area than the actuating plunger 80.1 according to FIG. 1A.
  • the closing element 69.2 of the pressure relief valve 60.2 comprises: Formation with a larger cross-sectional area than the closing element 69.1 1A shows a measuring surface 83 which can be acted upon by the pressure medium in the pressure chamber 79.
  • the pressure relief valve 60.2 comprises in comparison to the pressure relief valve 60.1 a modified valve housing 62.2 and a weaker one Spring 70.2.
  • the spring 70.2 is supported on the valve housing 62.2, which holds the valve piston 5 presses against the closure part 23 and thereby stops.
  • the proportional magnet 81 has the same direction of action and function as the proportional magnet 67 after Fig. 1A, i.e. the magnetic field he sets up when actuated moves the Actuating plunger 80.2 and thus the closing element 69.2 by one of the strengths distance corresponding to the control current in the direction of the open position.
  • the pressure limiting valve 60.2 can thus partially control the strength of the control current or fully open and thus the one of the first control valve 2 when locked Pressure limiting valve 60.2 influences the flow control or can be switched to pressure control.
  • the proportional magnet 82 has the opposite direction of action as that Proportional magnet 81 and is used when the proportional magnet is not activated 81 to the closing element 69.2 against the valve seat 68 with a To press the corresponding control force, i.e.
  • the closing element 69.2 against the pressure of the Spring 70.2 opens; because the spring 70.2 has a relatively low stiffness has and thus serves as a switching spring, the closing element 69.2 opens completely and switches the first control valve 2 from the flow control to the pressure control when the hydraulic force on the Measuring surface 83 acting input pressure exceeds the force with which controlled proportional solenoid 82, the closing element 69.2 to the valve seat 68 presses. Switching from flow control to pressure control thus takes place in the same way as in the control valve block according to FIG. 3A and 3B under the direct influence of the working pressure (neglecting the relatively small pressure difference at the throttle 47).
  • connection channel is omitted 76; instead, the flow channel is 65.2 via the valve outlet 64.2 connected to the sixth pressure medium channel 34 leading to the tank connection T.

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  • 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).

Claims (7)

  1. Bloc de soupapes hydrauliques de commande comportant un premier raccord hydraulique (P) pour le raccordement à une conduite de travail (102), un raccord de réservoir (T) pour le raccordement à un réservoir (107), un deuxième raccord hydraulique (A) pour le raccordement à une conduite de pression de réglage (103), une soupape de commande (2) avec une première chambre de pression hydraulique (24), reliée au premier raccord hydraulique (P), et une deuxième chambre de pression hydraulique (42), reliée au raccord de réservoir (T), par un point d'étranglement (32), qui, suivant la position d'un piston de soupape (4) mobile, placé entre les chambres de pression hydrauliques (24, 42), relie le premier raccord hydraulique (P) ou le raccord de réservoir (T) au deuxième raccord hydraulique (A), un organe d'étranglement (47) prévu entre la première chambre de pression hydraulique (24) et la deuxième chambre de pression hydraulique (42) de la soupape de commande (2) et une soupape de limitation de pression (60.1; 60.2), placée entre la deuxième chambre de pression hydraulique (42) de la soupape de commande (2) et le raccord de réservoir (T), avec une partie de commande (66.1 ; 66.2), actionnant un élément de fermeture (69.1 ; 69.2), pendant la commande de la partie de commande (66.1 ; 66.2), l'élément de fermeture (69.1 ; 69.2) étant déplacé en direction de sa position d'ouverture et la soupape de limitation de pression (60.1; 60.2) reliant ainsi la deuxième chambre de pression hydraulique (42) de la soupape de commande (2) au réservoir (107), par le raccord de réservoir (T).
  2. Bloc de soupapes hydrauliques de commande selon la revendication 1, caractérisé en ce que la soupape de limitation de pression est une soupape à siège (60.1 ; 60.2).
  3. Bloc de soupapes hydrauliques dc commande selon la revendication 2, caractérisé en ce qu'un ressort (70.1) sollicite l'élément de fermeture (69.1) de la soupape de limitation de pression (60.1), conformée en soupape à siège (60.1), en direction de la position de fermeture.
  4. Bloc de soupapes hydrauliques de commande selon la revendication 2 ou 3, caractérisé en ce que la soupape à siège (60.1 ; 60.2) est raccordée, par son entrée de soupape (63), à un canal de fluide sous pression (36) supplémentaire et par sa sortie de soupape (64.1 ; 64.2), au raccord de réservoir (T).
  5. Bloc de soupapes hydrauliques de commande selon la revendication 4, caractérisé en cc que la soupape de commande (2) est une soupape de pression différentielle, commandable par deux canaux de pression de commande (45, 46), avec deux pressions de commande différentes, donnant une pression différentielle et en ce que le canal de fluide sous pression (36) supplémentaire est raccordé au canal de pression de commande (46), menant à la soupape de commande (2), avec la pression de commande plus basse.
  6. Bloc de soupapes hydrauliques de commande selon l'une des revendications 2 à 5, caractérisé en ce que l'élément de fermeture (69.2) de la soupape à siège (60.2) est sollicité en direction de la position d'ouverture, en supplément à la commande par la partie de commande (66.2), par une pression d'entrée hydraulique de la soupape à siège (60.2).
  7. Bloc de soupapes hydrauliques de commande selon l'une des revendications 2 à 6, caractérisé en ce que la partie de commande (66.2) comprend deux aimants proportionnels (81, 82) avec deux sens d'action opposés l'un à l'autre, dont un (82) sollicite par force, en direction de la position de fermeture, l'élément de fermeture (69.2) de la soupape de limitation de pression, conformée en soupape à siège (60.2) et dont l'autre (81) agit en direction de la position d'ouverture, sur l'élément de fermeture (69.2) de la soupape de limitation de pression, conformé en soupape à siège (60.2).
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
DE4329164 1993-08-30
DE4329164A DE4329164C2 (de) 1993-08-30 1993-08-30 Hydraulischer Steuerventilblock
PCT/EP1994/002857 WO1995006818A1 (fr) 1993-08-30 1994-08-29 Bloc a soupapes hydrauliques de commande

Publications (2)

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

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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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DE10219850B3 (de) * 2002-05-03 2004-02-05 Brueninghaus Hydromatik Gmbh Regeleinrichtung mit Grenzwertregelventil
DE102010048070A1 (de) * 2010-04-16 2011-10-20 Robert Bosch Gmbh Druck-Förderstromregler
DE102012218903B4 (de) * 2012-10-17 2023-02-16 Robert Bosch Gmbh Hydraulische Ventilanordnung und hydraulische Maschinenanordnung mit einer derartigen Ventilanordnung
DE102014202413A1 (de) 2014-02-11 2015-08-13 Robert Bosch Gmbh Elektrisch angesteuertes Regelventil für eine verstellbare hydrostatische Pumpe und verstellbare hydrostatische Pumpe
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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DE3316212A1 (de) * 1983-05-04 1984-11-15 Robert Bosch Gmbh, 7000 Stuttgart Hydraulisches stromregelventil
DE3346184A1 (de) * 1983-12-21 1985-07-04 Mannesmann Rexroth GmbH, 8770 Lohr Steuerblock mit mehreren wegeventilen
DE3443265A1 (de) * 1984-11-28 1986-06-12 Mannesmann Rexroth GmbH, 8770 Lohr Regelventil fuer eine verstellpumpe
JP2658432B2 (ja) * 1988-12-01 1997-09-30 ダイキン工業株式会社 油圧制御装置
DE3914485A1 (de) * 1989-05-02 1990-11-08 Bosch Gmbh Robert Einrichtung zur regelung des foerderstroms und foerderdrucks einer verstellbaren pumpe
JPH0390678A (ja) * 1989-06-05 1991-04-16 Sanyo Chem Ind Ltd 繊維用処理剤

Also Published As

Publication number Publication date
EP0717817A1 (fr) 1996-06-26
US5778924A (en) 1998-07-14
DE59405730D1 (de) 1998-05-20
JPH09502008A (ja) 1997-02-25
DE4329164A1 (de) 1995-03-09
WO1995006818A1 (fr) 1995-03-09
DE4329164C2 (de) 1998-02-19

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