WO1999009323A1 - Systeme hydraulique avec verin differentiel et soupape a action rapide, ainsi que soupape a action rapide pour ledit systeme hydraulique - Google Patents

Systeme hydraulique avec verin differentiel et soupape a action rapide, ainsi que soupape a action rapide pour ledit systeme hydraulique Download PDF

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Publication number
WO1999009323A1
WO1999009323A1 PCT/EP1998/003236 EP9803236W WO9909323A1 WO 1999009323 A1 WO1999009323 A1 WO 1999009323A1 EP 9803236 W EP9803236 W EP 9803236W WO 9909323 A1 WO9909323 A1 WO 9909323A1
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WO
WIPO (PCT)
Prior art keywords
connection
valve
pressure
pressure chamber
piston rod
Prior art date
Application number
PCT/EP1998/003236
Other languages
German (de)
English (en)
Inventor
Armin Stellwagen
Original Assignee
Mannesmann Rexroth Ag
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 Mannesmann Rexroth Ag filed Critical Mannesmann Rexroth Ag
Publication of WO1999009323A1 publication Critical patent/WO1999009323A1/fr

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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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance valves

Definitions

  • Hydraulic system with a differential cylinder and a rapid traverse valve and rapid traverse valve for such a hydraulic system
  • the invention is based on a hydraulic system which, according to the preamble of claim 1, has a differential cylinder, a directional control valve, a rapid traverse valve and a pressure limiting valve for securing the pressure of a pressure chamber of the differential cylinder on the piston rod side.
  • From DE 24 02 112 C2 is a hydraulic system with a differential cylinder which has a piston rod and a piston which separates a pressure chamber on the piston rod side and a pressure chamber on the piston rod side, with a directional control valve with two consumer connections, via which the two pressure chambers of the differential cylinder alternately with a pressure medium source and can be connected to a tank, and are known with a rapid traverse valve which has three connections.
  • One of these connections is. connected to the piston rod-side pressure chamber and a second of these connections to the piston rod-side pressure chamber of the hydraulic cylinder.
  • the third connection is connected to a consumer connection of the directional control valve, via which pressure medium can be supplied by a pump from the pressure chamber of the differential cylinder on the piston rod side.
  • a control spool of the rapid traverse valve is centered by two springs in a central position in which all three connections are blocked against each other.
  • the control piston In the sense of a connection of the first connection to the second connection, the control piston is acted upon by the pressure which prevails in the pressure chamber of the differential cylinder on the side away from the piston rod.
  • the control piston of the rapid traverse valve In the opposite direction and in the sense of a connection of the first connection to the third connection, the control piston of the rapid traverse valve is acted upon by the pressure which is present in the connection between the third connection and the already Speaking consumer connection of the directional valve is pending.
  • the directional control valve When the piston rod is extended, the directional control valve is switched in such a way that the pressure medium conveyed by a hydraulic pump flows into the pressure chamber of the differential cylinder on the piston rod side.
  • the rapid traverse valve acts as a brake valve. Its control piston is adjusted in the direction of the middle position and throttles the outflow of pressure medium from the pressure chamber on the piston rod side. In the pressure chamber on the piston rod side, such a pressure is established that the force generated by it on the control piston of the rapid traverse valve corresponds to the counterforce exerted by a compression spring.
  • a hydraulic system with all the features from the preamble of claim 1 is known from DE 39 15 919 AI.
  • the piston rod of the differential tialzylinders extended in a creep speed if you leave the rapid traverse valve in a rest position and controls the differential cylinder with the directional control valve.
  • pressure medium conveyed by a hydraulic pump then flows to the pressure chamber of the differential cylinder on the piston rod side, while the pressure medium displaced from the pressure chamber on the piston rod side flows off to a tank via the directional valve.
  • the rapid traverse valve is actuated for rapid traverse of the differential cylinder.
  • a pressure connection to which pressure medium conveyed by the hydraulic pump can be supplied in parallel with the directional valve, becomes a first consumer connection, which is connected to the pressure chamber of the differential cylinder on the piston rod side, and a second consumer connection, which is connected to the pressure chamber of the differential cylinder away from the piston rod , connected with each other.
  • the pressure medium displaced from the pressure chamber side of the piston rod is now also fed directly to the pressure chamber on the piston rod side.
  • Both pressure chambers of the differential cylinder are protected with a pressure relief valve, which is set to a pressure in the range of 250 bar.
  • the known hydraulic system works flawlessly, even if in rapid traverse, in which only the cross-sectional area of the piston rod is available to support a load acting against the extension of the piston rod, the pressure in the pressure chamber of the differential cylinder on the piston rod side is not greater than the maximum pressure set on the corresponding pressure relief valve have to be. If the rapid traverse valve is actuated when the load is large and already raised, there is a risk that the load will fall.
  • the invention is therefore based on the endeavor to provide a hydraulic system with the features from the preamble of the Proverb 1 to develop so that regardless of the size of the load that is moved with the differential cylinder and counteracts the extension of the piston rod, the arbitrary actuation of the rapid traverse valve is possible without endangering people and without the risk of damage to the machine.
  • this aim is achieved according to the invention by a check valve which is arranged in the connection between the two pressure chambers of the differential cylinder which can be established via the rapid traverse valve and which blocks from the piston rod-side pressure chamber to the piston rod-side pressure chamber.
  • the invention is based on the consideration that in
  • rapid traverse on the other hand, the same pressure is present in both pressure chambers, so that the piston surface is pressure-equalized up to the cross-section of the piston rod and the pressure in the pressure-rod-side pressure chamber can only support the load on a surface that corresponds to the cross-section of the piston rod.
  • the pressure in rapid traverse must be three times as high as in creep speed in order to support the same load.
  • Claims 3 and 4 relate to how the check valve can be accommodated in a simple manner and inserted into the pressure medium paths.
  • a particularly preferred embodiment of a hydraulic system contains claim 5. This embodiment is particularly favorable if a load change occurs on the differential cylinder during extension of the piston rod, that is if the load has to be pushed over part of the way by pressure in the pressure chamber on the piston rod side and pull the piston rod and piston out of the differential cylinder housing on another part of the way.
  • a brake valve is provided, through which the pressure medium displaced from the piston rod-side pressure chamber can flow off to the tank and which is acted upon by a spring in the sense of opening a cross-section from the pressure prevailing in the piston rod-side pressure chamber and in the sense of closing the cross-section .
  • the brake valve only allows so much pressure medium to flow out of the piston rod-side pressure chamber that a pressure equivalent to the force of the spring is maintained in the piston rod-side pressure chamber.
  • the spring on the brake valve is now set so that its force equivalent pressure is greater than the pressure that is equivalent to the force of a spring that acts on the valve member of the rapid traverse valve in the sense of the connection of the piston rod-side pressure chamber with the brake valve. Then, in rapid traverse and with pulling load, the spring of the rapid traverse valve determines the pressure in the pressure chamber of the differential cylinder on the piston rod side, so that the brake valve is closed and the load change has no influence has the rapid traverse.
  • a hydraulic system according to claim 5 can be used with advantages even without the features from the preceding claims.
  • the invention also relates to a rapid traverse valve for use in a hydraulic system with a differential cylinder and with the possibility of extending the piston rod of the differential cylinder in a creep speed or in a rapid traverse.
  • the input valve contains in the connection between a first connection, which is provided for connection to a piston rod-side pressure chamber of the differential cylinder, and a second connection, which is provided for connection to a piston rod-side pressure chamber of the differential cylinder, and which by a into a Ven - Tilbohrung the housing movable valve member is open and closed, a check valve that blocks from the first port to the second port. This reliably prevents a load from falling.
  • the closing member of the check valve is arranged in the valve member designed as a hollow piston. No additional installation space is therefore required.
  • the embodiment according to claim 8 is particularly advantageous because the rapid traverse valve can be switched over without generating a pressure peak or a pressure drop in the pressure chamber of the differential cylinder on the piston rod side.
  • FIG. 1 shows the hydraulic circuit diagram of the first embodiment.
  • Example in which the inflow of pressure medium from a hydraulic pump into the pressure chamber of the differential cylinder on the piston rod side occurs both in rapid and creep speed via a directional control valve
  • Figure 2 shows a section through a rapid speed valve, as it is except for a slight change in the pilot control during execution is used according to Figure 1
  • Figure 3 shows the hydraulic circuit diagram of a second embodiment of a hydraulic system according to the invention.
  • a constant pump 10 draws pressure medium from a tank 11 and discharges it into an inlet line 12, which leads to a control block 13 and runs through a plurality of valve disks from which the control block is composed.
  • the feed line 12 enters the control block 13 at an input disk 14.
  • a directional valve disk 15 with a directional valve 16 and with a pressure compensator 17 for actuating one or two differential cylinders 18 connected in parallel to one another.
  • a disk the housing 19 of a rapid traverse valve 20, depending on the position of which the differential cylinder 18 is actuated in a creep speed or in a rapid traverse.
  • another disk 21 with valves for the control oil supply to the electrohydraulically actuated directional valve 16.
  • the input disk 14 contains a bypass pressure compensator 25, the outlet of which is connected to a tank line 26 passing through the disks.
  • the regulating piston 27 of the pressure compensator 25 is acted upon in the opening direction by the pressure in the feed line 12, which likewise passes through all the disks, and in the closing direction by a compression spring 28 and by the load pressure of the differential cylinder 18. It allows just enough of the pressure medium conveyed by the constant pump 10 to flow from the inlet line 12 into the tank line 26 that the pressure in the inlet line 12 is reduced by one of the forces of the compression spring 28 equivalent pressure difference is above the load pressure acting on the control piston 27 in the closing direction.
  • the pressure compensator 25 is connected to a so-called load reporting line 30.
  • the pressure acting on the control piston in the “closing” direction is limited to a maximum value by a pressure limiting valve 31, so that the pressure in the feed line 12 is also limited.
  • the directional control valve 16 has, as working connections, a pressure connection 31, upstream of which the pressure compensator 17 is connected, a tank connection 32, which is connected to the tank line, a consumer connection 33, from which channels 34 and 35 in the disks 15 and 19 and a line 36 lead to a pressure chamber 37 of the differential cylinder 18 remote from the piston rod, and a consumer connection 38 which is connected to a connection 39 of the rapid traverse valve 20.
  • the directional control valve 16 also has a load-sensing chamber 40 which is connected to the tank connection 32 in the central position of the directional control valve piston 22 and to the consumer connection 33 and the consumer connection 38 via a nozzle 41 in a lateral working position of the directional control valve piston.
  • the load pressure present in the load-sensing chamber 40 acts together with a compression spring 42 in the opening direction on the control piston of the pressure compensator 17, while the pressure upstream of a measuring orifice 43 of the directional control valve which is open in a lateral working position acts on the control piston in the closing direction.
  • the load pressure passes from the load reporting chamber 40 into the load reporting line 30 and from there to the bypass pressure compensator 25 and to the pressure limiting valve 31.
  • a brake valve 44 or 45 is also integrated in the directional control valve 16, which is located in the discharge flow path from a consumer connection 33 or 38 to the tank connection 32 of the directional control valve 16.
  • the brake valve 44 is in the opening direction by the pressure in the consumer port 38 and the brake valve 45 in the opening direction of pressure from the pressure in the consumer port 33.
  • a compression spring 46 acts in the closing direction of the brake valves 44 and 45, the force of which is equivalent to a pressure of, for example, 30 bar in the consumer connections.
  • the directional control valve piston 22 is spring-centered in a central position, in which all work connections are shut off from one another. With the help of electromagnetically actuated pilot valves 47 and 48, it can be adjusted into a working position in opposite directions.
  • the pilot valves 47 and 48 are switching valves in the exemplary embodiment, so that the directional valve piston 22 assumes a single working position in each direction.
  • electrohydraulically proportionally adjustable pressure reducing valves can also be used as pilot valves, so that a proportional adjustment of the directional valve piston 22 and a proportional opening of the measuring orifices 43 is possible.
  • design of a directional valve disc 15 reference is expressly made here to the applicant's older German patent application 196 51 967.5.
  • two pressure relief valves 55 and 56 are also installed, of which the pressure relief valve 55 is connected with its input to the consumer connection 33 and the pressure relief valve 56 with its input to the consumer connection 38. Both pressure relief valves have a maximum pressure of e.g. 250 bar set.
  • the housing 19 of the rapid traverse valve 20 has a first outer connection 60, from which the line 36 leads to the pressure chamber 37 of the differential cylinder 18 on the piston rod side, and a second outer connection 61, from which a line 62 is connected to the pressure chamber 63 of the differential cylinder 18 on the piston rod side.
  • the third connection 39 is an internal connection which is formed by a channel which starts from a side face of the housing 19 which bears against the directional valve disk 15.
  • a valve bore 64 passes through the housing 19 and is surrounded by three axially spaced control chambers 65, 66 and 67.
  • the control chamber 65 is connected to the external connection 60 via a slightly inclined bore 68 and to the channel 34 of the directional valve disc 15 via a bore 69 running perpendicular to the cutting plane.
  • the control chamber 66 is connected to the external connection 61 via a bore 70.
  • the channel 39 which is regarded as the third, but internal connection of the rapid traverse valve 20, opens into the third control chamber 67.
  • a control piston 75 is axially displaceable in the valve bore 64 and is acted upon by a helical compression spring 76 located in a spring chamber 79 in the direction of an end position in which the two control chambers 66 and 67 are connected to one another in a wide open manner via an annular groove 77 in the control piston 75 are.
  • the force that can be exerted by the helical compression spring 76 is adjustable.
  • the spring chamber 79, in which the helical compression spring 76 is located, is also connected to the external connection 60 via a nozzle 80.
  • a 2/2-way pilot valve 81 is connected to the spring chamber 79, which assumes a blocking position under the action of a compression spring and can be brought into a passage position by actuating an electromagnet 82, in which the spring chamber 79 is relieved towards the tank line 26 .
  • the spring chamber 79 is permanently connected to the tank line 26.
  • the pressure chamber 78 is connected to the tank line 26 via the nozzle 80 and can be acted upon with the pressure prevailing in the external connection 60 by means of the pilot valve 81.
  • the control piston 75 is opposed by the pressure prevailing in the pressure chamber 78 against the force of the screw compression spring 76 loaded. This is set so that a pressure of about 10 bar is sufficient to move the control piston 75 against the spring.
  • This pressure is less than the pressure which is necessary for adjusting the brake valve 45 against the compression spring 46.
  • the control piston 75 is partially designed as a hollow piston, into which a blind hole 83 is made, from the end facing away from the spring 76, which ends at a certain distance in front of the annular groove 77.
  • a first connection between the blind hole and the outside of the control piston 75 is established by a first star of four radial bores 84 near the end of the blind hole 83, which is otherwise sealed by a screw plug 89.
  • a second connection between the blind hole and the outside of the control piston is formed at a greater distance from the end of the blind hole by a second star of radial bores 85.
  • the radial bores 84 are through a housing web between the two
  • Control chambers 65 and 66 are closed, while the radial bores 85 are open towards the control chamber 65.
  • the blind hole 83 tapers conically and there forms a seat for the closing element 86 of a check valve 87.
  • the closing element is moved towards its seat by a weak compression spring 88, which closes the blind hole between it and the blind hole Locking screw 89 is clamped, and the pressure that prevails in the control chamber 65 and is guided via a small transverse bore 90 and an axial bore 91 in the closing member into the spring chamber receiving the compression spring 88.
  • the axial distance between the radial bores 84 and the control chamber 66 is smaller than the axial distance between the one end wall of the annular groove 77 and the housing web between the two control chambers 66 and 67, so that the radial Dial bores 84 are opened to the control chamber 66 rather than it is closed to the control chamber 67.
  • Differential cylinder 18 is displaced.
  • the pressure in the pressure chamber 37 therefore does not rise, so that the pressure relief valve 55 does not respond even under high loads. Only a small amount of control oil flows out of the pressure chamber 37 via the nozzle 80 and the pilot valve 81 into the tank line 26, so that the
  • the rapid traverse valve becomes by switching the pilot valve 81 into its second position brought, in which the radial bores 84 are open to the outer connection 61, the pressure in the pressure chamber 63 rises during the further movement of the piston 9 until it is slightly above the pressure in the pressure chamber 37. He is then able to open the check valve 87 so that the pressure medium which is displaced from the pressure chamber 63 can flow directly into the pressure chamber 37 via the rapid traverse valve 20. However, the entire pressure level has now increased significantly.
  • the effective effective area for the pressure in the pressure chamber 37 is now only the cross-sectional area of the piston rod 8.
  • the pressure for moving the same load as in creep speed is now three times higher necessary.
  • the piston rod 8 is now extended in rapid traverse. Changes the direction of the load by the load so that it now tries to pull the piston rod 8 out of the housing of the differential cylinder 18, the pressure in the pressure chamber 37 and thus also at the external connection 60 and in the pressure chamber 78 of the rapid traverse valve 20 drops.
  • the spring 76 is now able to move the control piston 75 of the rapid traverse valve in the direction of its end position shown in FIG.
  • the pressure of 10 bar in the pressure chamber 37 of the differential cylinder 18 is not capable of braking valve 45 against the force of compression spring 46, which is only overcome by a pressure in the range of 30 bar. to open. This means that the rapid traverse is retained even after a load change.
  • the pilot valves 48 and 81 can be electrically locked so that the pilot valve 81 cannot be actuated when the pilot valve 48 is actuated. Then the load is prevented from falling when the piston rod is retracted and a negative load that the piston rod attempts to insert.
  • the hydraulic system according to FIG. 3 is based on a throttle control rather than a load-sensing control. It points accordingly, a 6-way valve 95 with a circulation channel 96, which passes through the entire control block 13.
  • this directional valve like the directional valve according to FIG. 1, has a pressure connection 31, a tank connection 32 and a consumer connection 33, which is connected directly to the pressure chamber 37 of a differential cylinder 18 on the piston rod side, and a consumer connection 38, which is connected directly to the piston rod side Pressure chamber 63 of the differential cylinder 18 is connected.
  • the pressure connection 31 is connected to an inlet line 12 which is led through the control block 13, while the tank connection 32 is connected to a tank line which leads through the control block 13 26 stands.
  • a rapid traverse valve 97 has a pressure connection 31, a tank connection 32 and a consumer connection 33 and a consumer connection 38.
  • the pressure connection 31 is connected to the feed line 12, the tank connection 32 to the tank line 26 and the consumer connection 33 to the pressure chamber 37 of the differential cylinder 18 connected.
  • a non-return valve 87 is arranged, which opens to the consumer port 38 of the rapid traverse valve 97.
  • the rapid traverse valve assumes a rest position in which the circulation channel 96 to the tank line 26 is open and the four connections 31, 32, 33 and 38 are shut off from one another.
  • the rapid traverse valve can be brought into a second position by electrohydraulic actuation, in which the two consumer connections 33 and 38 and the pressure connection 31 are internally connected to one another.
  • the check valve 87 prevents the load from falling.
  • the pressure in the pressure chamber 63 is not exactly as large as the pressure in the pressure chamber 37 due to the check valve 87, but in turn assumes a value that it generates a force on the annular surface of the piston 9 facing the pressure chamber 63, which together with the load of the Compressive force maintains the equilibrium that the pressure of 250 bar prevailing in the pressure chamber 37 generates on the piston surface.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Système hydraulique qui possède un vérin différentiel (18) doté d'une tige (8) de piston et d'un piston (9) séparant une chambre sous pression (63) située au-dessus du piston d'une chambre sous pression (37) située au-dessous du piston, un distributeur (16) doté de deux connexions (33, 38) pour consommateurs par l'intermédiaire desquelles les deux chambres sous pression (37, 63) du vérin différentiel peuvent être connectées en alternance avec une source (10) de fluide sous pression et un réservoir (11), une soupape à action rapide (20) à actionnement arbitraire par l'intermédiaire de laquelle, indépendamment du distributeur, la chambre sous pression située au-dessus du piston peut être connectée à la chambre sous pression située au-dessous du piston du vérin différentiel, et une soupape (55) de limitation de pression destinée à protéger de la surpression la chambre sous pression située au-dessous du piston. Selon la présente invention, une chute de la charge lors de l'actionnement de la soupape à action rapide dans une position de repos, ou dans une position de travail du distributeur dans laquelle un fluide sous pression provenant de la source de fluide sous pression est amené dans la chambre sous pression située au-dessous du piston, est empêchée par une soupape de non-retour (87) qui est placée dans la liaison constituée par la soupape à action rapide entre les deux chambres sous pression du vérin différentiel et ferme ladite liaison entre la chambre sous pression située au-dessus du piston et la chambre sous pression située au-dessous du piston. Selon la présente invention, la soupape à action rapide se caractérise par le fait que la soupape de non-retour est intégrée dans la soupape à action rapide.
PCT/EP1998/003236 1997-08-16 1998-05-29 Systeme hydraulique avec verin differentiel et soupape a action rapide, ainsi que soupape a action rapide pour ledit systeme hydraulique WO1999009323A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19735482.3 1997-08-16
DE19735482A DE19735482B4 (de) 1997-08-16 1997-08-16 Hydraulisches System mit einem Differentialzylinder und einem Eilgangventil

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Publication Number Publication Date
WO1999009323A1 true WO1999009323A1 (fr) 1999-02-25

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WO (1) WO1999009323A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012065692A1 (fr) * 2010-11-17 2012-05-24 Hydac Filtertechnik Gmbh Dispositif à soupape hydraulique

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3622142B2 (ja) * 1999-08-04 2005-02-23 新キャタピラー三菱株式会社 作業機械の作業腕制御装置
JP4532725B2 (ja) * 2000-12-11 2010-08-25 ヤンマー株式会社 掘削旋回作業車のブーム用方向切換弁
DE10135298A1 (de) * 2001-07-24 2003-02-13 Bosch Rexroth Ag Ventilanordnung
DE10224740B4 (de) * 2002-06-04 2014-09-04 Linde Material Handling Gmbh Hydraulische Steuerventileinrichtung mit einer Stromregeleinrichtung
DE102006061305B3 (de) 2006-12-22 2008-07-10 Hydac Filtertechnik Gmbh Ansteuereinrichtung für hydraulische Verbraucher
DE102009058371A1 (de) * 2009-12-15 2011-06-16 Hydac Filtertechnik Gmbh Ventilanordnung zur Ansteuerung eines Verbrauchers
DE102016215311A1 (de) * 2016-08-17 2018-02-22 Voith Patent Gmbh Hydraulischer Antrieb
WO2024027913A1 (fr) * 2022-08-03 2024-02-08 Xcmg European Research Center Gmbh Ensemble soupape pour commander au moins un raccordement d'une charge hydraulique

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3357451A (en) * 1965-05-24 1967-12-12 Hydraulic Unit Specialities Co Speed and directional control valve for double-acting lift cylinder
DE2402112C2 (de) 1973-03-16 1986-02-20 Caterpillar Tractor Co., Peoria, Ill. Eilgang-Steuerventil für einen Arbeitszylinder
EP0206934A1 (fr) * 1985-06-20 1986-12-30 Sanyokiki Kabushiki Kaisha Dispositif de commande sélective pour plusieurs sortes de dispositifs d'actionnement hydrauliques
GB2199115A (en) * 1986-11-27 1988-06-29 Michael David Baxter Spool valve
DE3915919A1 (de) 1989-05-16 1990-11-22 Rexroth Mannesmann Gmbh Ventilanordnung
JPH07158607A (ja) * 1993-12-09 1995-06-20 Hitachi Constr Mach Co Ltd 再生回路用弁装置
JPH08219107A (ja) * 1995-02-13 1996-08-27 Hitachi Constr Mach Co Ltd 油圧機械の油圧再生装置
DE19651967A1 (de) 1996-12-13 1998-06-18 Mannesmann Rexroth Ag Wegeventil zur lastunabhängigen Steuerung eines hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3601643A1 (de) * 1986-01-21 1987-07-23 Schrupp Gmbh Hydraulische steuervorrichtung fuer den schnellgang von verbrauchern
JP3609127B2 (ja) * 1994-10-25 2005-01-12 日清紡績株式会社 油圧プレスのラム駆動用油圧回路

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3357451A (en) * 1965-05-24 1967-12-12 Hydraulic Unit Specialities Co Speed and directional control valve for double-acting lift cylinder
DE2402112C2 (de) 1973-03-16 1986-02-20 Caterpillar Tractor Co., Peoria, Ill. Eilgang-Steuerventil für einen Arbeitszylinder
EP0206934A1 (fr) * 1985-06-20 1986-12-30 Sanyokiki Kabushiki Kaisha Dispositif de commande sélective pour plusieurs sortes de dispositifs d'actionnement hydrauliques
GB2199115A (en) * 1986-11-27 1988-06-29 Michael David Baxter Spool valve
DE3915919A1 (de) 1989-05-16 1990-11-22 Rexroth Mannesmann Gmbh Ventilanordnung
JPH07158607A (ja) * 1993-12-09 1995-06-20 Hitachi Constr Mach Co Ltd 再生回路用弁装置
JPH08219107A (ja) * 1995-02-13 1996-08-27 Hitachi Constr Mach Co Ltd 油圧機械の油圧再生装置
DE19651967A1 (de) 1996-12-13 1998-06-18 Mannesmann Rexroth Ag Wegeventil zur lastunabhängigen Steuerung eines hydraulischen Verbrauchers hinsichtlich Richtung und Geschwindigkeit

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 095, no. 009 31 October 1995 (1995-10-31) *
PATENT ABSTRACTS OF JAPAN vol. 096, no. 012 26 December 1996 (1996-12-26) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012065692A1 (fr) * 2010-11-17 2012-05-24 Hydac Filtertechnik Gmbh Dispositif à soupape hydraulique

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