EP0066274B1 - Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin - Google Patents

Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin Download PDF

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Publication number
EP0066274B1
EP0066274B1 EP82104683A EP82104683A EP0066274B1 EP 0066274 B1 EP0066274 B1 EP 0066274B1 EP 82104683 A EP82104683 A EP 82104683A EP 82104683 A EP82104683 A EP 82104683A EP 0066274 B1 EP0066274 B1 EP 0066274B1
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EP
European Patent Office
Prior art keywords
valve
passage
fluid
working
bore
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
Application number
EP82104683A
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German (de)
English (en)
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EP0066274A1 (fr
Inventor
Henry Friesen
John Rosbak
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.)
Deere and Co
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Deere and Co
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 Deere and Co filed Critical Deere and Co
Priority to AT82104683T priority Critical patent/ATE15253T1/de
Publication of EP0066274A1 publication Critical patent/EP0066274A1/fr
Application granted granted Critical
Publication of EP0066274B1 publication Critical patent/EP0066274B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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
    • 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
    • F15B2011/0243—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 the regenerative circuit being activated or deactivated automatically
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/75—Control of speed of the output member
    • 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
    • Y10T137/2496—Self-proportioning or correlating systems
    • Y10T137/2544—Supply and exhaust type
    • Y10T137/2554—Reversing or 4-way valve systems

Definitions

  • the invention relates to a valve arrangement for increasing the extension speed of a double-acting working cylinder with a single-sided piston rod or a double-acting differential cylinder, consisting of an unlockable check valve and a spring-loaded bypass valve displaced fluids in the piston-end cylinder chamber provided fluid return line have the bypass valve.
  • Such a control device for a differential cylinder can be found in DE-B-2 648 608.
  • a control device for a single- or multi-stage differential cylinder that can be pressurized with hydraulic fluid on both sides, with a piston that is not completely leak-free sealed, with an unlockable check valve in the pressure medium line leading to the piston side, with a check valve that opens towards the cylinder and is arranged in the pressure medium line on the piston rod side, and with a directional control valve for connecting the cylinder chambers when the piston side is pressurized.
  • the directional control valve is designed as a 2/2-way valve, the control element of which is connected to the check valve element on the piston rod side.
  • the directional control valve is open when the check valve is closed.
  • the check valve member is acted upon in the closing direction by the piston-side pressure. This valve arrangement is intended to ensure that the cylinder spaces are always connected to one another except when the piston rod side is pressurized.
  • the first control channel forms, together with the first working channel, an extension channel which is guided through the valve housing and which forms a pressure fluid source, e.g. B. connects a pump with the piston-side cylinder chamber of a working cylinder.
  • the second control channel forms, together with the second working channel, an intake channel which is guided through the valve housing and which connects a liquid reservoir or a sump to the cylinder chamber of the working cylinder on the piston rod side.
  • the second working channel forms, together with the first working channel, a fluid return channel which is guided through the valve housing and which connects the two cylinder spaces of the working cylinder mentioned to one another.
  • valve bodies mentioned above are rigidly connected to one another and form a piston slide which is acted upon on its opposite end faces by the two spring elements acting in the opposite direction. These hold the piston slide in its first valve position, in which the flow connection between the second control channel and the second working channel is interrupted by the second valve body.
  • a directional control valve is provided, which is connected on the one hand to the pressure fluid source and the sump and on the other hand to one end of the two control channels.
  • the object of the invention is to improve the functionality of the valve arrangement described at the outset, in particular when the piston rod of a working cylinder under high load is extended.
  • this object is achieved according to the invention in that the check valve and the bypass valve are arranged coaxially. wherein the bypass valve member serves as an unlocking piston for the check valve, which prevents the suction of fluid from the first fluid line to the piston-side cylinder chamber in its closed normal position.
  • bypass valve member has a first end face and a second end face which are acted upon by the liquid pressure in the first control channel or the second control channel such that an increase in the pressure in the first control channel via the pressure in the second control channel causes a shift causes the bypass valve member into its second valve position against the action of the second spring element, the bypass valve member displacing the check valve member into its open position during this displacement via a driving device.
  • the new valve arrangement is simple and compact. It works absolutely reliably under all operating conditions.
  • the driving device between the two valve members consists of a driving surface on the bypass valve member and a driving surface on the rear. there is a check valve that comes into mutual contact after a displacement of the bypass valve member.
  • a directional control valve can be provided, which is connected on the one hand to the pressure fluid source and the sump and on the other hand to one end of the two control channels.
  • the hydraulic system shown in Figure 1 comprises a pump 12 and a sump 14 which are connected to a conventional four-way, three-position directional control valve 16.
  • a valve arrangement 18 for increasing the extension speed of the cylinder 20 is connected between this directional control valve 16 and a double-acting hydraulic working cylinder with a one-sided piston rod 20 or a differential cylinder.
  • the valve arrangement 18 consists of a valve housing 22 with a stepped valve bore 24, the wall of which forms a valve seat 26 and an annular shoulder 28 pointing in the axial direction. In the open end of the valve bore 24 is screwed this plug to the outside liquid-sealing plug 30.
  • a first control channel 32 and a second control channel 34 open into the valve bore 24 near the opposite ends of this valve bore and connect them to the corresponding outlets of the directional control valve 16.
  • a first working channel 36 is connected to the head-side chamber 42 of the hydraulic working cylinder 20, which is connected via a Section 40 at the valve seat 26 opens into the valve bore 24.
  • a second working channel 44 is connected to the piston rod-side chamber 48 of the hydraulic working cylinder 20, which has two branches 50, 52 which open into the valve bore 24 via an annular groove 54 and 56, which are separated from one another by an annular web 58.
  • a cylindrical valve body 60 is slidably mounted, which has a central axial bore 62 and an axially directed annular end face 64, which in the first valve position rests with its outer edge against the said annular shoulder 28.
  • an axially rising central section 66 is provided, on which a spring element 68 is inserted, which is supported at one end on this end face of the valve body 60 and at the other end on the sealing plug 30 and presses the valve body 60 with its annular end face 64 against the annular shoulder 28.
  • valve body 70 has a valve head 72 with a conical sealing surface 74 which, in the closed position of this valve body, bears against the valve seat 26.
  • the valve head 72 is coaxially attached to one end of a cylindrical valve rod 76 which extends through the Axial bore 62 extends in the other valve body 60.
  • a cylindrical flange 78 with a recess 79 is fastened on the valve rod 76 in a section of smaller diameter such that the valve body 60 lies between the valve head 72 and the flange 78 of the valve body 70.
  • the radially outer portion of the flange 78 is flanged in the axial direction and directed away from the valve body 60, so that the flange 78 together with the valve rod 76 forms an annular socket for receiving one end of a spring 80, the other end of which rests against the sealing plug 30 is supported so that the spring 80 presses the valve head 72 against the valve seat 26.
  • Both springs 68, 80 press the valve bodies 60, 70 to the left in relation to the figures.
  • the plug 30 has a blind bore 90 into which one end of the valve rod 76 is immersed and into which one end of the spring 80 is inserted.
  • An annular collar 92 encloses the open end of the blind bore 90 and is overlapped by one end of the spring 68.
  • the two valve bodies 60, 70 together with the wall of the valve bore 24 form a first and a second valve chamber 82, 84.
  • the first valve chamber 82 communicates with the control channel 32 and via the section 40 with the first working channel 36, while the second valve chamber 84 is connected to the second control channel 34 and via the branch 50 and the annular groove 54 to the second working channel 44.
  • the valve chambers 82, 84 are never in a fluid-exchanging connection with one another. This is ensured by the fact that only one of the two ring grooves 54, 56, but never both, are opened at the same time via the valve body 60 with respect to the valve bore 24.
  • the working channels 36, 44 can be connected via branch lines 37, 45 to other hydraulic motors or the like which are not shown in the drawing. These branch lines can be inside or outside the valve housing 22.
  • the directional control valve 16 is actuated so that the control channel 34 is connected to the pump 12 or to a pressure fluid source and the control channel 32 to the sump 14 or a fluid reservoir .
  • the relatively high fluid pressure in the control channel 34 compared to the control channel 32 holds the valve body 60 pressed against the annular shoulder 28, so that liquid can flow from the control channel 34 via the valve bore 24, the branch 50 and the working channel 44 into the piston rod-side chamber 48.
  • the hydraulic motor 20 is retracted; the piston of this motor or of the hydraulic working cylinder 20 is shifted to the left (refer to FIG.
  • the control channel 32 are connected to the pump 12 and the control channel 34 to the sump 14 via the directional control valve 16.
  • a high load in the direction of the extension of the cylinder piston leads to an increase in pressure in the chamber 48 on the piston rod side, which counteracts movement of the valve body 60 to the right in the valve chamber 84.
  • the valve head 72 is still in contact with the valve seat 26 and thus prevents a flow outflow from the valve chamber 82.
  • an increase in pressure is generated in this valve chamber 82 which very quickly rises in the valve chamber 84 prevailing pressure.
  • valve chamber 84 since the valve chamber 84 is connected directly to the sump 14 via the control line 34 and the directional control valve 16. Under the effect of the pressure difference between the end faces 64, 66 of the valve body 60, the latter is displaced in the valve bore 24 relative to the valve body 70 from its position shown in FIG. 1 to the right. While the valve body 70 maintains its closing position, the valve body 60 first slides over the annular groove 54 and thereby closes the branch 50, but at the same time keeps the branch 52 still closed. As a result, the connection between the working channel 44 and the control channel 34 is interrupted, so that an outflow of liquid from the chamber 48 on the piston rod side is temporarily prevented.
  • valve chamber 84 is only connected to the sump 14 via the control channel 34, so that the pressure difference between the valve chambers 82, 84 increases further.
  • valve body 60 By moving the valve body 60 further to the right pushes, it strikes with its right end face against the flange 78 and takes the valve body 70 with it during its further displacement, so that its valve head 72 lifts off the valve seat 27.
  • the valve body 60 releases the annular groove 56 and thereby opens a flow connection between the piston rod-side chamber 48 and the head-side chamber 42 via a fluid return line, which is composed of sections of the working channel 44, the branch 52, the valve bore 24, the valve chamber 82 , the channel section 40 and the working channel 36.
  • valve body 60 and thus also the valve body 70 to the right is prevented when the end of the valve rod 76 abuts against the bottom of the blind bore 90 in the sealing plug 30.
  • the two valve bodies 60, 70 are in their return position, in which the liquid coming from the pump 12 flows via the control channel 32, the valve chamber 82 and the working channel 40, 36 into the head-side chamber 42, into which liquid also flows at the same time flows out of the piston rod-side chamber 48 via the feedback channel.
  • the piston of the hydraulic cylinder 20 moves to the right, the liquid displaced from the chamber 48 on the piston rod side is returned directly to the chamber 42 on the head side.
  • This additional amount of liquid directed into the head-side chamber 42 compensates for the fact that the head-side chamber 42 has a larger volume than the piston rod-side chamber 48; this additional amount of liquid reduces the amount of liquid required by the pump 12 during the extension of the piston, so that the extension of the hydraulic working cylinder 20 is accelerated.

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  • Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Valve Device For Special Equipments (AREA)
  • Actuator (AREA)
  • Hydraulic Control Valves For Brake Systems (AREA)
  • Forklifts And Lifting Vehicles (AREA)
  • Compressor (AREA)
  • External Artificial Organs (AREA)
  • Chemical And Physical Treatments For Wood And The Like (AREA)
  • Control Of Presses (AREA)

Claims (11)

1. Système de valve (18) pour augmenter la vitesse de sortie d'un vérin à double effet (20) comportant une tige de piston d'un seul côté ou d'un cylindre ou vérin différentiel à double effet, constitué . par une soupape ou un clapet de retenue déverrouillable (70) et une soupape de dérivation (60-66) soumise à une sollicitation d'un ressort, la soupape de retenue (70) étant montée dans un premier conduit de fluide (32) débouchant dans une chambre (42) du cylindre disposée du côté du fond du piston, tandis que la soupape de dérivation (60-66) est montée dans un conduit de retour du fluide (44, 52, 40, 36) prévu pour transférer le fluide refoulé à partir de la chambre (48) du cylindre située du côté de la tige de piston jusque dans la chambre (42) du cylindre disposée du côté du fond du piston, caractérisé en ce que la soupape de retenue (70) et la soupape de dérivation (60-66) sont diposées coaxialement, l'élément obturateur (60) de la soupape de dérivation servant de piston de déverrouillage pour la soupape de retenue (70) qui, dans sa position fermée normale, empêche l'aspiration de fluide à partir du premier conduit de fluide (32) en direction de la chambre (42) disposée du côté du fond du piston.
2. Système de valve suivant la revendication 1, caractérisé par les particularités suivantes :
a) un premier et un second canaux de commande (32, 34) et un premier et un second canaux de travail (36, 44) sont raccordés à un alésage de valve (24) ménagé dans un corps ou boisseau de valve (22) ;
b) le premier canal de commande (32) forme avec le premier canal de travail (36) le premier conduit de liquide (32, 82, 24, 40, 36) passant à travers le corps de valve (22), qui relie une source de liquide sous pression (12) ou un réservoir de liquide ou carter (14) à la chambre de cylindre (42) du vérin (20) située du côté du fond du piston ;
c) le second canal de commande (34) forme avec le second canal de travail (44) un second conduit de fluide (34, 84, 24, 54, 50, 44) passant à travers le corps de valve (22), qui relie le réservoir de liquide ou carter (14) ou bien la source de liquide sous pression (12) à la chambre de cylindre (48) située du côté de la tige de piston ;
d) le second canal de travail (44) forme avec le premier canal de travail (36) le conduit de retour du liquide (44, 52, 24, 82, 40, 36) passant à travers le corps de valve (22) ;
e) l'élément obturateur (72) de la soupape de retenue est déplaçable par coulissement à l'intérieur de l'alésage (24) de la valve entre une position de fermeture dans laquelle il interrompt' la communication entre le premier canal de commande (32) et le premier canal de travail (36), et une position d'ouverture dans laquelle il établit cette communication ;
f) l'élément obturateur (60) de la soupape de dérivation est déplaçable par coulissement à l'intérieur de l'alésage (24) de la valve entre une première position dans laquelle il interrompt la communication entre le second canal de travail (44) et le premier canal de commande (32) ou bien le premier canal de travail (36), et une seconde position dans laquelle il interrompt la communication entre le second canal de travail (44) et le second canal de commande (34), tout en établissant la communication entre le second canal de travail (44) et le premier canal de commande (32) ou le premier canal de travail (36);
g) un premier et un second organes élastiques sont disposés dans l'alésage (24) de la valve et sollicitent les deux éléments obturateurs (72, 50) dans le même sens en direction de leur position de fermeture ou première position.
3. Système de valve suivant la revendication 2, caractérisé en ce que l'élément obturateur (60) de la soupape de dérivation présente une première face terminale (64) et une seconde face terminale (66) qui sont soumises à l'action de la pression de liquide régnant dans le premier canal de commande (32) ou dans le second canal de commande (34), de façon telle qu'une élévation de la pression dans le premier canal de commande au-delà de la pression dans le second canal de commande provoque un déplacement de l'élément obturateur (60) de la soupape de dérivation jusque dans sa seconde position en antagonisme à l'action du second organe élastique ou ressort (68), l'élément obturateur (60) de la soupape de dérivation déplaçant lors de ce mouvement l'élément obturateur (72) de la soupape de retenue jusque dans sa position d'ouverture. par l'intermédiaire d'un dispositif d'entraînement (66, 78).
4. Système de valve suivant la revendication 3, caractérisé en ce que le dispositif d'entraînement (66, 78) prévu entre les deux éléments obturateurs (60, 72) est constitué par une surface d'entraînement (66) ménagée sur l'élément obturateur (60) de la soupape de dérivation et par une surface d'entraînement (78) prévue sur la soupape de retenue (70), ces surfaces venant dans une position de contact réciproque après une certaine course de l'élément obturateur (60) de la soupape de dérivation.
5. Système de valve suivant l'une quelconque des revendications 2 à 4, caractérisé par les particularités suivantes :
a) l'élément obturateur (60) de la soupape de dérivation divise, en combinaison avec la paroi de l'alésage (24) de la valve, cet alésage en une première et une seconde chambres (82, 84),
b) le premier canal de commande (32) ainsi que le premier canal de travail (36) sont raccordés à la première chambre (82) de la valve tandis que le second canal de commande (34) ainsi que le second canal de travail (44) sont raccordés à la seconde chambre (84) ;
c) le conduit de retour du fluide (44, 52. 24, 82. 40, 36) relie la première chambre (82) de la valve à la chambre (48) du vérin (20) correspondant à la tige de piston ;
d) le déplacement de l'élément obturateur (60) de la soupape de dérivation est assuré en raison d'une différence de pression de liquide dans les deux chambres (82, 84) de la valve ; et
e) l'élément obturateur (72) de la soupape de retenue est pressé par le premier organe élastique (80) contre un siège de soupape (26) formé par la paroi de l'alésage (24) de la valve.
6. Système de valve suivant l'une quelconque des revendications précédentes, caractérisé en ce que l'élément obturateur (60) de la soupape de dérivation ou l'élément obturateur (72) de la soupape de retenue comporte une tige de soupape (76) qui est guidée coaxialement de façon coulissante dans un alésage (62) de l'autre élément obturateur (60).
7. Système de valve suivant la revendication 6. caractérisé par les particularités suivantes :
a) l'élément obturateur (60) de la soupape de dérivation a une forme cylindrique, il est muni de l'alésage précité (62), et il présente une face terminale annulaire (64) par laquelle il s'applique, dans sa première position, contre un épaulement annulaire (28) de l'alésage (24) de la valve ;
b) la soupape de retenue (70) comporte une tête (72) munie d'une surface d'obturation étanche (74) conjuguée au siège de soupape précité (26), une bride (78) formant la surface d'entraînement précitée, ainsi qu'une tige de soupape (76) reliant rigidement ensemble cette tête et cette bride ; et
c) l'élément obturateur (60) de la soupape de dérivation est disposé entre la tête (72) et la bride (78) de la soupape de retenue (70).
8. Système de valve suivant la revendication 5, 6 ou 7, caractérisé en ce que le sens de déplacement de l'élément obturateur (60) de la soupape de dérivation pour passer de sa première à sa seconde position est orienté à l'opposé du siège de soupape précité (26). -
9. Système de valve suivant la revendication 7 ou 8, caractérisé en ce que la bride précitée (78) forme, avec une partie de la tige de soupape (76). une cuvette annulaire pour la réception d'une extrémité du premier organe élastique (80), dont l'autre extrémité prend appui sur le corps (22) de la valve.
10. Système de valve suivant l'une quelconque des revendications 2 à 9, caractérisé en ce que le second organe élastique (68) prend appui par une extrémité sur le corps (22) de la valve et par son autre extrémité sur la surface d'entraînement (66) de l'élément obturateur (60) de la soupape de dérivation.
11. Système de valve suivant l'une quelconque des revendications 2 à 10, caractérisé par une valve de commande de sens (16) qui est raccordée d'une part, à la source de liquide sous pression (12) ainsi qu'au réservoir ou carter (14) et, d'autre part, à une extrémité de deux canaux de commande (32, 34).
EP82104683A 1981-06-01 1982-05-28 Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin Expired EP0066274B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82104683T ATE15253T1 (de) 1981-06-01 1982-05-28 Ventilanordnung zur erhoehung der ausfahrgeschwindigkeit eines arbeitszylinders.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US06/269,110 US4397221A (en) 1981-06-01 1981-06-01 Regenerative valve
US269110 1981-06-01

Publications (2)

Publication Number Publication Date
EP0066274A1 EP0066274A1 (fr) 1982-12-08
EP0066274B1 true EP0066274B1 (fr) 1985-08-28

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ID=23025843

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Application Number Title Priority Date Filing Date
EP82104683A Expired EP0066274B1 (fr) 1981-06-01 1982-05-28 Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin

Country Status (8)

Country Link
US (1) US4397221A (fr)
EP (1) EP0066274B1 (fr)
AT (1) ATE15253T1 (fr)
CA (1) CA1169742A (fr)
DE (1) DE3265820D1 (fr)
ES (1) ES8306235A1 (fr)
FI (1) FI70302C (fr)
ZA (1) ZA823823B (fr)

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Publication number Priority date Publication date Assignee Title
US4723476A (en) * 1982-02-22 1988-02-09 The Cessna Aircraft Company Regenerative valve
US5014734A (en) * 1990-08-31 1991-05-14 Caterpillar Inc. Quick drop valve
US5251705A (en) * 1992-03-19 1993-10-12 Deere & Company Electrical trigger for quick drop valve
US5233909A (en) * 1992-07-21 1993-08-10 Decatur Cylinder, Inc. Integral regenerative fluid system
US5226348A (en) * 1992-12-14 1993-07-13 Caterpillar Inc. Electro-hydraulic quick drop circuit
US5370038A (en) * 1992-12-21 1994-12-06 Caterpillar Inc. Regeneration circuit for a hydraulic system
FR2726343B1 (fr) * 1994-10-28 1997-01-24 Kuhn Sa Valve a quatre orifices de raccordement et deux positions
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Also Published As

Publication number Publication date
FI70302B (fi) 1986-02-28
EP0066274A1 (fr) 1982-12-08
ATE15253T1 (de) 1985-09-15
ZA823823B (en) 1984-01-25
DE3265820D1 (en) 1985-10-03
FI821849A0 (fi) 1982-05-24
FI70302C (fi) 1986-09-15
ES512689A0 (es) 1983-05-01
CA1169742A (fr) 1984-06-26
US4397221A (en) 1983-08-09
ES8306235A1 (es) 1983-05-01

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