EP0066274B1 - Valve arrangement for increasing the operating speed of a working cylinder - Google Patents

Valve arrangement for increasing the operating speed of a working cylinder 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)
French (fr)
Other versions
EP0066274A1 (en
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
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Publication date
Application filed by Deere and Co filed Critical Deere and Co
Priority to AT82104683T priority Critical patent/ATE15253T1/en
Publication of EP0066274A1 publication Critical patent/EP0066274A1/en
Application granted granted Critical
Publication of EP0066274B1 publication Critical patent/EP0066274B1/en
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.

Abstract

A regenerative valve includes a housing having a valve bore therein intersecting with an extension passage interconnecting a pump and a piston extension chamber, a retraction passage interconnecting a sump and a piston retraction chamber, and a regenerative passage for communicating fluid from the retraction to the extension chamber upon extension of the piston. A poppet member is movable in the bore to open and block fluid flow through the extension passage. A shuttle member is movable in the bore to either open or block one or the other of the regenerative and retraction passages. The shuttle member engages the poppet to cause the poppet to open the extension passage when the shuttle moves to close the retraction passage and open the regenerative passage.

Description

Die Erfindung betrifft eine Ventilanordnung zur Erhöhung der Ausfahrgeschwindigkeit eines doppeltwirkenden Arbeitszylinders mit einseitiger Kolbenstange bzw. eines doppeltwirkenden Differentialzylinders, bestehend aus einem entsperrbaren Rückschlagventil und einem federbelasteten Bypassventil, wobei eine zum kolbenbodenseitigen Zylinderraum führende erste Fluidleitung das Rückschlagventil und eine zur Überleitung des aus dem kolbenstangenseitigen Zylinderraum verdrängten Fluides in den kolbendodenseitigen Zylinderraum vorgesehene Fluid-Rückführleitung das Bypassventil aufweisen.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.

Eine derartige Steuereinrichtung für einen Differentialzylinder läßt sich der DE-B-2 648 608 entnehmen. Offenbart ist eine Steuereinrichtung für einen beidseitig mit Druckflüssigkeit beaufschlagbaren ein- oder mehrstufigen Differentialzylinder mit einem nicht völlig leckfrei abgedichteten Kolben, mit einem entsperrbaren Rückschlagventil in der zur Kolbenseite führenden Druckmittelleitung, mit einem zum Zylinder hin öffnenden, in der Druckmittelleitung zur Kolbenstangenseite angeordneten Rückschlagventil und mit einem Wegeventil zur Verbindung der Zylinderräume bei Druckbeaufschlagung der Kolbenseite. Das Wegeventil ist als 2/2-Wegeventil ausgebildet, dessen Steuerglied mit dem kolbenstangenseitigen Rückschlagventilglied verbunden ist. Bei geschlossenem Rückschlagventil ist das Wegeventil geöffnet. Das Rückschlagventilglied ist in Schließrichtung durch den kolbenseitigen Druck beaufschlagt. Durch diese Ventilanordnung soll sichergestellt werden, daß die Zylinderräume außer bei Druckbeaufschlagung der Kolbenstangenseite stets miteinander verbunden sind.Such a control device for a differential cylinder can be found in DE-B-2 648 608. Disclosed is 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.

Aus US-A-2 890 683 läßt sich eine Ventilanordnung entnehmen, bei der der erste Steuerkanal zusammen mit dem ersten Arbeitskanal einen durch das Ventilgehäuse geführten Ausfahrkanal bildet, der eine Druckflüssigkeitsquelle, z. B. eine Pumpe, mit dem kolbenbodenseitigen Zylinderraum eines Arbeitszylinders verbindet. Der zweite Steuerkanal bildet zusammen mit dem zweiten Arbeitskanal einen durch das Ventilgehäuse geführten Einzugskanal, der ein Flüssigkeitsreservoir bzw. einen Sumpf mit dem kolbenstangenseitigen Zylinderraum des Arbeitszylinders verbindet. Der zweite Arbeitskanal bildet zusammen mit dem ersten Arbeitskanal einen durch das Ventilgehäuse geführten Fluid-Rückführkanal, der die beiden genannten Zylinderräume des Arbeitszylinders miteinander verbindet. Die vorstehend genannten Ventilkörper sind starr miteinander verbunden und bilden einen Kolbenschieber, der an seinen gegenüberliegenden Stirnseiten von den beiden in entgegengesetzter Richtung wirkenden Federelementen beaufschlagt wird. Diese halten den Kolbenschieber in seiner ersten Ventilstellung, in der die Strömungsverbindung zwischen dem zweiten Steuerkanal und dem zweiten Arbeitskanal durch den zweiten Ventilkörper unterbrochen ist. Ferner ist bei dieser vorbekannten Ausführungsform ein Richtungssteuerventil vorgesehen, das einerseits an die Druckflüssigkeitsquelle sowie den Sumpf und andererseits an das eine Ende der beiden Steuerkanäle angeschlossen ist.From US-A-2 890 683 it can be seen a valve arrangement in which 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. The 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. Furthermore, in this known embodiment, 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.

Alle diese mit einem einzigen Kolbenschieber arbeitenden Rückkopplungsventile weisen einen Nachteil auf : Ein plötzlicher Druckanstieg im kolbenstangenseitigen Zylinderraum des Arbeitszylinders, der sich z. B. aus einer starken Belastung des Zylinders ergeben kann, kann die Verschiebung des Kolbenschiebers in seine Fluid-Rückführstellung verhindern oder aber verzögern. Um diesen Nachteil zu beheben wurden aufwendige Steuerventileinrichtungen entwickelt, die eine Kombination einzelner Sperr-und Wechselventile vorsehen. So zeigt z. B. US-A-4144 947 eine Ventilanordnung, bei der Rückschlagventil und Bypass-Ventil koaxial zueinander angeordnet sind. Jedoch ist diese Konstruktion sehr komplex, voluminös und teuer.All of these feedback valves working with a single piston slide have one disadvantage: A sudden pressure increase in the cylinder chamber of the working cylinder on the piston rod side, which z. B. can result from a heavy load on the cylinder, the displacement of the spool in its fluid return position can prevent or delay. In order to remedy this disadvantage, complex control valve devices have been developed which provide a combination of individual check and shuttle valves. So shows z. B. US-A-4144 947 a valve assembly in which the check valve and bypass valve are arranged coaxially with each other. However, this construction is very complex, voluminous and expensive.

Der Erfindung liegt die Aufgabe zugrunde, die eingangs erläuterte Ventilanordnung hinsichtlich ihrer Funktionstüchtigkeit, insbesondere beim Ausfahren der Kolbenstange eines unter hoher Belastung stehenden Arbeitszylinders, zu verbessern.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.

Ausgehend von der eingangs beschriebenen Ventilanordnung wird diese Aufgabe gemäß der Erfindung dadurch gelöst, daß Rückschlagventil und Bypass-Ventil koaxial angeordnet sind. wobei das Bypass-Ventilglied als Entsperrkolben für das Rückschlagventil dient, das in seiner geschlossenen Normalstellung das Nachsaugen von Fluid aus der ersten Fluidleitung zum kolbenbodenseitigen Zylinderraum verhindert.Starting from the valve arrangement described at the outset, 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.

Dabei kann die Ventilanordnung in vorteilhafter Weise folgende Merkmale aufweisen :

  • a) An eine in einem Ventilgehäuse angeordnete Ventilbohrung sind ein erster und zweiter Steuerkanal sowie ein erster und zweiter Arbeitskanal angeschlossen ;
  • b) der erste Steuerkanal bildet zusammen mit dem ersten Arbeitskanal die durch das Ventilgehäuse geführte erste Fluidleitung, die eine Druckflüssigkeitsquelle oder ein Flüssigkeitsreservoir bzw. einen Sumpf mit dem kolbendenseitigen Zylinderraum des Arbeitszlinders verbindet ;
  • c) der zweite Steuerkanal bildet zusammen mit dem zweiten Arbeitskanal eine durch das Ventilgehäuse geführte zweite Fluidleitung, die das Flüssigkeitsreservoir bzw. den Sumpf oder die Druckflüssigkeitsquelle mit dem kolbenstangenseitigen Zylinderraum verbindet ;
  • d) der zweite Arbeitskanal bildet zusammen mit dem ersten Arbeitskanal die durch das Ventilgehäuse geführte Fluid-Rückführleitung ;
  • e) das Rückschlag-Ventilglied ist innerhalb der Ventilbohrung verschiebbar zwischen einer Schließstellung, in der es die Strömungsverbindung zwischen dem ersten Steuerkanal und dem ersten Arbeitskanal unterbricht, und einer Offenstellung, in der es diese Strömungsverbindung öffnet ;
  • f) das Bypass-Ventilglied ist innerhalb der Ventilbohrung verschiebbar zwischen einer ersten Ventilstellung, in der es die Strömungsverbindung zwischen dem zweiten Arbeitskanal und dem ersten Steuerkanal bzw. dem ersten Arbeitskanal unterbricht, und einer zweiten Ventilstellung, in der es die Strömungsverbindung zwischen dem zweiten Arbeitskanal und dem zweiten Steuerkanal unterbricht, aber die Strömungsverbindung zwischen dem zweiten Arbeitskanal und dem ersten Steuerkanal bzw. dem ersten Arbeitskanal freigibt, und
  • g) ein erstes und zweites Federelement sind in der Ventilbohrung angeordnet und drücken die beiden Ventilglieder in derselben Richtung in ihre Schließstellung bzw. erste Ventilstellung.
The valve arrangement can advantageously have the following features:
  • a) A first and second control channel and a first and second working channel are connected to a valve bore arranged in a valve housing;
  • b) the first control channel forms, together with the first working channel, the first fluid line guided through the valve housing, which connects a pressure fluid source or a fluid reservoir or a sump to the piston-side cylinder space of the working cylinder;
  • c) the second control channel forms, together with the second working channel, a second fluid line which is guided through the valve housing and which connects the fluid reservoir or the sump or the pressure fluid source to the cylinder chamber on the piston rod side;
  • d) the second working channel forms, together with the first working channel, the fluid return line led through the valve housing;
  • e) the check valve member is displaceable within the valve bore between a closed position in which it is the flow ver breaks bond between the first control channel and the first working channel, and an open position in which it opens this flow connection;
  • f) the bypass valve member is displaceable within the valve bore between a first valve position in which it interrupts the flow connection between the second working channel and the first control channel or the first working channel, and a second valve position in which it connects the flow connection between the second working channel and interrupts the second control channel, but releases the flow connection between the second working channel and the first control channel or the first working channel, and
  • g) a first and a second spring element are arranged in the valve bore and press the two valve members in the same direction into their closed position or first valve position.

Ferner ist es vorteilhaft, wenn das Bypass-Ventilglied eine erste Stirnfläche und eine zweite Stirnfläche aufweist, die vom Flüssigkeitsdruck im ersten Steuerkanal bzw. dem zweiten Steuerkanal so beaufschlagt sind, daß ein Ansteigen des Drucks im ersten Steuerkanal über den Druck im zweiten Steuerkanal eine Verschiebung des Bypass-Ventilgliedes in seine zweite Ventilstellung gegen die Wirkung des zweiten Federelementes bewirkt, wobei das Bypass-Ventilglied bei dieser Verschiebung über eine Mitnahmeeinrichtung das Rückschlag-Ventilglied in dessen Offenstellung verschiebt.It is also advantageous if the 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.

Die neue Ventilanordnung ist einfach und kompakt aufgebaut. Sie arbeitet unter allen Betriebsbedingungen absolut zuverlässig.The new valve arrangement is simple and compact. It works absolutely reliably under all operating conditions.

Ferner kann es zweckmäßig sein, wenn die Mitnameeinrichtung zwischen den beiden Ventilgliedern aus einer Mitnehmerfläche am Bypass-Ventilglied und einer Mitnehmerfläche am Rück-. schlagventil besteht, die nach einem Verschiebeweg des Bypass-Ventilgliedes zur gegenseitigen Anlage kommen.Furthermore, it can be expedient if 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.

- Ferner kann ein Richtungssteuerventil vorgesehen sein, das einerseits an die Druckflüssigkeitsquelle sowie den Sumpf und andererseits an das eine Ende der beiden Steuerkanäle angeschlossen ist. Durch dieses Richtungssteuerventil können die Anschlüsse zwischen Druckflüssigkeitsquelle und Sumpf einerseits sowie kolbenbodenseitigen und kolbenstangenseitigen Zylinderraum des Arbeitszylinders andererseits vertauscht werden, so daß der doppeltwirkende Arbeitszylinder ausgefahren bzw. eingezogen werden kann.- Furthermore, 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. By means of this directional control valve, the connections between the pressure fluid source and the sump on the one hand and the piston chamber side and piston rod side cylinder space of the working cylinder on the other hand can be exchanged, so that the double-acting working cylinder can be extended or retracted.

Weitere Merkmale der Erfindung sin Gegenstand der Unteransprüche und werden zusammen mit der Wirkungsweise der erfindungsgemäßen Ventilanordnung anhand eines Ausführungsbeispieles näher erläutert.Further features of the invention are the subject of the subclaims and are explained in more detail together with the mode of operation of the valve arrangement according to the invention using an exemplary embodiment.

In der Zeichnung ist eine als Beispiel dienende Ausführungsform der Erfindung dargestellt. Es zeigen :

  • Figur 1 eine hydraulische Steuerventileinrichtung in schematischer Darstellung mit einem Längsschnitt durch eine erfindungsgemäße Ventilanordnung, die sich in neutraler Arbeitsstellung befindet ;
  • Figur 2 die Darstellung gemäß Figur 1, wobei sich die Ventilanordnung in seiner der Einziehbewegung der Kolbenstange des Hydraulikarbeitszylinders zugeordneten Stellung befindet und
  • Figur 3 die Darstellung gemäß Figur 1, wobei sich die Ventilanordnung in seiner der Ausfahrbewegung der Kolbenstange zugeordneten Stellung befindet.
In the drawing, an exemplary embodiment of the invention is shown. Show it :
  • 1 shows a hydraulic control valve device in a schematic representation with a longitudinal section through a valve arrangement according to the invention, which is in the neutral working position;
  • FIG. 2 shows the representation according to FIG. 1, the valve arrangement being in its position assigned to the retracting movement of the piston rod of the hydraulic working cylinder and
  • 3 shows the representation according to FIG. 1, the valve arrangement being in its position assigned to the extension movement of the piston rod.

Das in Figur 1 dargestellte Hydrauliksystem umfaßt eine Pumpe 12 und einen Sumpf 14, die an ein übliches Vierwege, Drei-Stellungs-Richtungssteuerventil 16 angeschlosses sind. Zwischen diesem Richtungssteuerventil 16 und einem doppelwirkenden Hydraulikarbeitszylinder mit einseitiger Kolbenstange 20 bzw. einem Differentialzylinder ist eine Ventilanordnung 18 zur Erhöhung der Ausfahrgeschwindigkeit des Zylinders 20 geschaltet.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.

Die Ventilanordnung 18 besteht aus einem Ventilgehäuse 22 mit einer abgesetzten Ventilbohrung 24, deren Wandung einen Ventilsitz 26 sowie eine in axialer Richtung weisende Ringschulter 28 bildet. In das offene Ende der Ventilbohrung 24 ist ein diese Bohrung nach außen flüssigkeitsabdichtender Verschlußstopfen 30 eingeschraubt. Ein erster Steuerkanal 32 und ein zweiter Steuerkanal 34 münden in die Ventilbohrung 24 nahe der sich gegenüberliegenden Enden dieser Ventilbohrung und verbinden diese mit den entsprechenden Auslässen des Richtungssteuerventils 16. An die kopfseitige Kammer 42 des Hydraulikarbeitszylinders 20 ist ein erster Arbeitskanal 36 angeschlossen, der über einen Abschnitt 40 beim Ventilsitz 26 in die Ventilbohrung 24 mündet. An die kolbenstangenseitige Kammer 48 des Hydraulikarbeitszylinders 20 ist ein zweiter Arbeitskanal 44 angeschlossen, der zwei Abzweigungen 50, 52 aufweist, die in die Ventilbohrung 24 über eine Ringnut 54 bzw. 56 münden, die über einen Ringsteg 58 voneinander getrennt sind.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.

In der Ventilbohrung 24 ist ein zylindrischer Ventilkörper 60 verschiebbar gelagert, der eine mittige Axialbohrung 62 sowie eine axial gerichtete ringförmige Stirnfläche 64 aufweist, die in der ersten Ventilstellung mit ihrem äußeren Rand gegen die genannte Ringschulter 28 anliegt. Auf der gegenüberliegenden Stirnseite des Ventilkörpers 60 ist ein sich in axialer Richtung erhebender zentraler Abschnitt 66 vorgesehen, auf das ein Federelement 68 gesteckt ist, das sich mit seinem einen Ende an dieser Stirnfläche des Ventilkörpers 60 und mit seinem anderen Ende an dem Verschlußstopfen 30 abstützt und den Ventilkörper 60 mit seiner ringförmigen Stirnfläche 64 gegen die Ringschulter 28 drückt.In the valve bore 24, 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. On the opposite end of the valve body 60, 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.

Ein weiterer Ventilkörper 70 weist einen Ventilkopf 72 mit einer konischen Abdichtfläche 74 auf, die in Schließstellung dieses Ventilkörpers an dem Ventilsitz 26 anliegt. Der Ventilkopf 72 ist koaxial an dem einen Ende einer zylindrischen Ventilstange 76 befestigt, die sich durch die Axialbohrung 62 im anderen Ventilkörper 60 erstreckt. Ein zylindrischer Flansch 78 mit einer Ausnehmung 79 ist auf der Ventilstange 76 in einem Abschnitt geringeren Durchmessers so befestigt, daß der Ventilkörper 60 zwischen dem Ventilkopf 72 und dem Flansch 78 des Ventilkörpers 70 liegt. Der radial außenliegende Abschnitt des Flansches 78 ist in axialer Richtung umgebördelt und weggerichtet von dem Ventilkörper 60, so daß der Flansch 78 zusammen mit der Ventilstange 76 einen ringförmigen Stutzen zur Aufnahme des einen Endes einer Feder 80 bildet, deren anderes Ende sich gegen den Verschlußstopfen 30 abstützt, so daß die Feder 80 den Ventilkopf 72 gegen den Ventilsitz 26 drückt. Beide Federn 68, 80 drücken die Ventilkörper 60, 70 bezogen auf die Figuren nach links. Der Verschlußstopfen 30 weist eine Sackbohrung 90 auf, in die das eine Ende der Ventilstange 76 eintaucht, und in die das eine Ende der Feder 80 eingeschoben ist. Ein ringförmiger Bund 92 umfaßt das offene Ende der Sackbohrung 90 und wird von dem einen Ende der Feder 68 übergriffen.Another 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.

Die beiden Ventilkörper 60, 70 bilden zusammen mit der Wandung der Ventilbohrung 24 eine erste und eine zweite Ventilkammer 82, 84. Die erste Ventilkammer 82 steht mit dem Steuerkanal 32 und über den Abschnitt 40 mit dem ersten Arbeitskanal 36 in Verbindung, während die zweite Ventilkammer 84 mit dem zweiten Steuerkanal 34 und über die Abzweigung 50 und die Ringnut 54 mit dem zweiten Arbeitskanal 44 in Verbindung steht. Unabhängig von der jeweiligen Stellung der Ventilkörper 60, 70 stehen die Ventilkammern 82, 84 niemals in flüssigkeitsaustauschender Verbindung miteinander. Dies ist dadurch sichergestellt, daß immer nur eine der beiden Ringnuten 54, 56, niemals aber beide gleichzeitig über den Ventilkörper 60 gegenüber der Ventilbohrung 24 geöffnet sind.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. Regardless of the respective position of the valve bodies 60, 70, 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.

Die Arbeitskanäle 36, 44 können über Abzweigleitungen 37, 45 an weitere, in der Zeichnung jedoch nicht dargestellte Hydraulikmotoren o. dgl. angeschlossen werden. Diese Abzweigleitungen können innerhalb oder außerhalb des Ventilgehäuses 22 liegen.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.

Die hydraulische Steuerventileinrichtung arbeitet wie folgt :

  • Wenn sich das Richtungssteuerventil 16 in seiner neutralen Stellung (kein Strömungsfluß) befindet, nimmt die Ventilanordnung 18 die in Figur 1 dargestellte Stellung ein. In dieser Stellung hält die Feder 68 den Ventilkörper 60 in Anlage an der Ringschulter 28, so daß die Strömungsverbindung zwischen Steuerkanal 34 und Arbeitskanal 44 offen, zwischen Arbeitskanal 44 und Steuerkanal 32 ebenso wie zwischen Arbeitskanal 44 und Arbeitskanal 36 jedoch geschlossen ist. Die Feder 80 hält den Ventilkopf 72 des Ventilkörpers 70 in leichter Anlage am Ventilsitz 26.
The hydraulic control valve device works as follows:
  • When the directional control valve 16 is in its neutral position (no flow flow), the valve assembly 18 assumes the position shown in FIG. In this position, the spring 68 holds the valve body 60 in contact with the annular shoulder 28, so that the flow connection between the control channel 34 and the working channel 44 is open, but between the working channel 44 and the control channel 32 as well as between the working channel 44 and the working channel 36 is closed. The spring 80 holds the valve head 72 of the valve body 70 in slight contact with the valve seat 26.

Soll der Hydraulikantrieb bzw. die Kolbenstange des Hydraulikarbeitszylinders 20 eingefahren bzw. zurückgezogen werden, wird das Richtungssteuerventil 16 so betätigt, daß der Steuerkanal 34 an die Pumpe 12 bzw. an eine Druckflüssigkeitsquelle und der Steuerkanal 32 an den Sumpf 14 bzw. ein Flüssigkeitsreservoir angeschlossen werden. Der gegenüber der Steuerkanal 32 verhältnismäßig hohe Flüssigkeitsdruck im Steuerkanal 34 hält den Ventilkörper 60 gegen die Ringschulter 28 gedrückt, so daß Flüssigkeit vom Steuerkanal 34 über die Ventilbohrung 24, die Abzweigung 50 und den Arbeitskanal 44 in die kolbenstangenseitige Kammer 48 strömen kann. Dadurch wird der Hydraulikmotor 20 zurückgefahren ; der Kolben dieses Motors bzw. des Hydraulikarbeitszylinders 20 wird nach links verschoben (bezogen auf Figur 1), und drückt dadurch Flüssigkeit aus der kopfseitigen Kammer 42, die dann durch den Arbeitskanal 36 in den Kanalabschnitt 40 strömt und hier den Ventilkopf 72 gegen die Wirkung der Feder 80 sowie den Flüssigkeitsdruck in der Ventilkammer 84 vom Ventilsitzt 86 abhebt, so daß die aus der kopfseitigen Kammer 42 kommende Flüssigkeit über die Ventilbohrung 24, den Steuerkanal 32 und das Richtungssteuerventil 16 in den Sumpf 14 ablaufen kann (siehe Figur 2).If the hydraulic drive or the piston rod of the hydraulic working cylinder 20 are to be retracted or withdrawn, 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. As a result, 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. 1), and thereby presses liquid from the head-side chamber 42, which then flows through the working channel 36 into the channel section 40 and here the valve head 72 against the action of Spring 80 and the liquid pressure in the valve chamber 84 lifts from the valve seat 86, so that the liquid coming from the head-side chamber 42 can drain into the sump 14 via the valve bore 24, the control channel 32 and the directional control valve 16 (see FIG. 2).

Soll jedoch der Kolben des Hydraulikarbeitszylinders 20 aus der in Figur 1 gezeigten Neutralstellung ausgefahren werden (siehe Figur 3). werden über das Richtungssteuerventil 16 der Steuerkanal 32 an die Pumpe 12 und der Steuerkanal 34 an dem Sumpf 14 angeschlossen. Eine hohe Belastung in Richtung des Ausfahrens des Zylinderkolbens führt in der kolbenstangenseitigen Kammer 48 zu einem Druckanstieg, der in der Ventilkammer 84 einer Bewegung des Ventilkörpers 60 nach rechts entgegenwirkt. Gelangt nun aber die Flüssigkeit vom Steuerkanal 32 in die Ventilkammer 82, liegt der Ventilkopf 72 noch am Ventilsitz 26 an und verhindert so einen Strömungsabfluß aus der Ventilkammer 82. Hierdurch wird in dieser Ventilkammer 82 ein Druckanstieg erzeugt, der sehr schnell den in der Ventilkammer 84 herrschenden Druck übersteigt. da die Ventilkammer 84 über die Steuerleitung 34 und das Richtungssteuerventil 16 unmittelbar mit dem Sumpf 14 verbunden ist. Unter Wirkung der sich so ergebenden Druckdifferenz zwischen den Stirnflächen 64, 66 des Ventilkörpers 60 wird letzterer in der Ventilbohrung 24 relativ gegenüber dem Ventilkörper 70 aus seiner in Figur 1 dargestellten Stellung nach rechts verschoben. Während der Ventilkörper 70 seine Schlie- ßsteIlung beibehält, schiebt sich der Ventilkörper 60 zuerst über die Ringnut 54 und verschließt dadurch die Abzweigung 50, hält aber gleichzeitig die Abzweigung 52 noch verschlossen. Dadurch ist die Verbindung zwischen Arbeitskanal 44 und Steuerkanal 34 unterbrochen, so daß zeitweise ein Abfluß von Flüssigkeit aus der kolbenstangenseitigen Kammer 48 unterbunden wird. In dieser Stellung ist die Ventilkammer 84 über den Steuerkanal 34 nur mit dem Sumpf 14 verbunden, so daß die Druckdifferenz zwischen den Ventilkammern 82, 84 weiter zunimmt. Indem sich der Ventilkörper 60 weiter nach rechts verschiebt, schlägt er mit seiner rechten Stirnfläche gegen den Flansch 78 an und nimmt den Ventilkörper 70 bei seiner weiteren Verschiebung mit, so daß dessen Ventilkopf 72 vom Ventilsitz 27 abhebt. Schließlich gibt der Ventilkörper 60 die Ringnut 56 frei und öffnet dadurch eine Strömungsverbindung zwischen der kolbenstangenseitigen Kammer 48 und der kopfseitigen Kammer 42 über eine Fluid-Rückführleitung, der sich zusammensetzt aus Abschnitten des Arbeitskanals 44, der Abzweigung 52, der Ventilbohrung 24, der Ventilkammer 82, des Kanalabschnitts 40 und des Arbeitskanals 36. Eine weitere Verschiebung des Ventilkörpers 60 und damit auch des Ventilkörpers 70 nach rechts wird unterbunden, wenn das Ende der Ventilstange 76 gegen den Boden der Sackbohrung 90 im Verschlußstopfen 30 anschlägt. In dieser Position befinden sich die beiden Ventilkörper 60, 70 in ihrer Rückführstellung, in der die von der Pumpe 12 kommende Flüssigkeit über den Steuerkanal 32, die Ventilkammer 82 und den Arbeitskanal 40, 36 in die kopfseitige Kammer 42 strömt, in die gleichzeitig auch Flüssigkeit aus der kolbenstangenseitigen Kammer 48 über den Rückkopplungskanal strömt. Bewegt sich also der Kolben des Hydraulikzylinders 20 nach rechts, wird die aus der kolbenstangenseitigen Kammer 48 verdrängte Flüssigkeit unmittelbar in die Kopfseitige Kammer 42 zurückgeführt. Diese zusätzliche, in die kopfseitige Kammer 42 geleitete Flüssigkeitsmenge ist eine Kompensation dafür, daß die kopfseitige Kammer 42 ein größeres Volumen aufweist als die kolbenstangenseitige Kammer 48 ; durch diese zusätzliche Flüssigkeitsmenge wird die von der Pumpe 12 während des Ausfahrens des Kolbens benötigte Flüssigkeitsmenge verringert, so daß das Ausfahren des Hydraulikarbeitszylinders 20 beschleunigt wird.However, if the piston of the hydraulic working cylinder 20 is to be extended from the neutral position shown in FIG. 1 (see FIG. 3). 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. However, if the liquid from the control channel 32 reaches the valve chamber 82, the valve head 72 is still in contact with the valve seat 26 and thus prevents a flow outflow from the valve chamber 82. As a result, an increase in pressure is generated in this valve chamber 82 which very quickly rises in the valve chamber 84 prevailing pressure. 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. In this position, the 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. 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. Finally, 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. A further displacement of the 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. In this position, 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. Thus, if 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.

Claims (11)

1. Valve arrangement (18) for increasing the extension speed of a double-acting working cylinder (20) with one-sided piston rod or of a double-acting differential cylinder, respectively, comprising an unlockable check valve (70) and a springloaded bypass valve (60-66); said check valve (70) being positioned in a first fluid passage (32) leading to the head end chamber (42) of said cylinder, and said bypass valve (60-66) being positioned in a fluid back-leading passage (44, 52, 40, 36) for passing over the fluid removed from the rod end chamber (48) of said cylinder to said head end chamber (42), characterized in that, check valve (70) and bypass valve (60-66) are arranged coaxially, whereby the bypass valve member (60) is used as an unlock piston for said check valve (70) which, in its closed normal position, prevents the suction of fluid from fluid passage (32) to said head end chamber (42).
2. Valve arrangement according to claim 1, characterized by the following features :
a) A first and second control passage (32, 34) as well as a first and second working passage (36, 44) are connected to a valve bore (24) arranged in a valve housing (22) ;
b) said first control passage (32) forms together with the first working passage (36) the first fluid passage (32, 82, 24, 40, 36) led through said valve housing (22), said first fluid passage interconnecting a pressure fluid source (12) or a fluid reservoir or a sump (14), respectively, and the head end chamber (42) of said working cylinder (20) ;
c) said second control passage (34) forms together with the second working channel (44) a second fluid passage (34, 84, 24, 54, 50, 44) led through said valve housing (22); said second fluid passage interconnecting said fluid reservoir or said sump (14), respectively, or said pressure fluid source (12) and said rod end chamber (48) of the cylinder ;
d) said second working passage (44) forms together with said first working passage (36) the fluid back-leading passage (44, 52, 24, 82, 40, 36) led through said valve housing (22) ;
e) a check valve member (72) is movable within said valve bore (24) between a closed position, in which it interrupts the fluid flow between said first control passage (32) and said first working passage (36), and an open position in which it permits this fluid flow ;
f) said bypass valve membre (60) is movable within said valve bore (24) between a first valve position, in which it interrupts the fluid flow between said second working passage (44) and said first control passage (32) or the first working passage (36), respectively, and a second valve position in which it interrupts the fluid flow between said second working passage (44) and said second control passage (34), but permitting flow communication between said second working passage (44) and said first control passage (32) or said first working passage (36), respectively ; and
g) first and second resilient means (80, 68) are positionned in the valve bore (24) and bias the two valve members (72, 60) in the same direction in its closed position of first valve position, respectively.
3. Valve arrangement according to claim 2, wherein said bypass valve member (60) has a first end face (64) and a second end face (66) being actuated by the fluid pressure in said first control passage (32) or in said second control passage (34), respectively, in such a way that an increase of the pressure in said first control passage over the pressure in the second control passage effects a movement of the bypass valve member (60) toward its second valve position against the bias of the second resilient means (68), whereby the bypass valve member (60) when being moved toward the second valve position is moving the check valve member (72) to the open position via follower means (66, 78).
4. Valve arrangement according to claim 3, wherein said follower means (66, 78) between both valve members (60, 72) comprises a carrier 'surface (66) on the bypass valve member (60) and a carrier surface (78) on the check valve (70), being engageable with each other after a movement path of the bypass valve member (60).
5. Valve arrangement according to one of the preceding claims 2 to 4, characterized by the following features :
a) said bypass valve member (60) cooperates with the wall of valve bore (24) to separate the valve bore into first and second valve chambers (82, 84) therein ;
b) said first control passage (32) as well as said first working passage (36) are communicated with said first valve chamber (82), and said second control passage (34) as well as said second working passage (44) are communicated with said second valve chamber (84) ;
c) said fluid back-leading passage (44, 52, . 24, 82, 40, 36) connects the first valve chamber (82) with the rod end chamber (48) of said working cylinder (20) ;
d) said bypass valve member (60) is movable in response to a differential fluid pressure in both valve chambers (82, 84) ; and
e) said first resilient means (80) urges said check valve member (72) toward a valve seat (26) formed by the wall of the valve bore (24).
6. Valve arrangement according to one of the preceding claims, wherein said bypass valve member (60) or said check valve member (72) includes a valve stem (76) coaxially and slidably received by a corresponding bore (62) in the other valve member (60).
7. Valve arrangement according to claim 6, characterized by the following features :
a) Said bypass valve member (60) comprises a cylindrical body with said bore (62) and an annular end face (64) which abuts an annular shoulder (28) of said valve bore (24) when the bypass valve member is in its first valve position ;
b) said check valve (70) comprises a valve head (72) having a sealing surface (74) engageable with said valve seat (26), a flange (78) forming said carrier surface, and said valve rod (76) rigidly interconnecting said valve head and said flange ; and
c) said bypass valve member (60) is positioned between valve head (72) and flange (78) of said check valve (70).
8. Valve arrangement according to claim 5, 6 or 7, wherein said bypass valve member (60) moves away from said valve seat (26) when moving from its first to its second valve position.
9. Valve arrangement according to claim 7 or 8, wherein said flange (78) and a portion of said valve rod (76) cooperate to form an annular socket for receiving one end of said first resilient means (80), the other end of which engaging the valve housing (22).
10. Valve arrangement according to one of the preceding claims 2 to 9, wherein the second resilient means (68) engages with its one end the valve housing (22) and with its second end the carrier surface of said bypass valve member (60).
11. Valve arrangement according to one of the preceding claims 2 to 10, having a directional control valve (16) coupled to said pressure fluid source (12) and said sump (14) as well as to one end of said first and second control passages (32, 34).
EP82104683A 1981-06-01 1982-05-28 Valve arrangement for increasing the operating speed of a working cylinder Expired EP0066274B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82104683T ATE15253T1 (en) 1981-06-01 1982-05-28 VALVE ASSEMBLY FOR INCREASING THE EXTENSION SPEED OF A POWER CYLINDER.

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 (en) 1982-12-08
EP0066274B1 true EP0066274B1 (en) 1985-08-28

Family

ID=23025843

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82104683A Expired EP0066274B1 (en) 1981-06-01 1982-05-28 Valve arrangement for increasing the operating speed of a working cylinder

Country Status (8)

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

Families Citing this family (19)

* Cited by examiner, † Cited by third party
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 (en) * 1994-10-28 1997-01-24 Kuhn Sa VALVE WITH FOUR CONNECTION HOLES AND TWO POSITIONS
US6094910A (en) * 1995-12-22 2000-08-01 Maritime Hydraulics As Apparatus and method for raising and lowering a piston in a piston cylinder arrangement in a derrick
DE59707059D1 (en) * 1996-02-28 2002-05-23 Bucher Hydraulics Ag Neuheim SAFETY CHECK BRAKE VALVE
US5682955A (en) * 1996-09-06 1997-11-04 Caterpillar Inc. Blade control system for an earthmoving blade
US5960814A (en) * 1997-09-12 1999-10-05 Ngt, Llc. Counter balanced locking valve
KR100611713B1 (en) * 2004-10-14 2006-08-11 볼보 컨스트럭션 이키프먼트 홀딩 스웨덴 에이비 Hydraulic control valve with regeneration function
US20100090143A1 (en) * 2008-08-28 2010-04-15 Kot Norbert J Dual locking valve
US8262058B2 (en) * 2008-08-28 2012-09-11 Kot Norbert J Balanced pilot operated check valve
WO2014171953A1 (en) * 2013-04-19 2014-10-23 Cascade Corporation Clamping attachment with regenerative hydraulic circuit
US9611871B2 (en) 2013-09-13 2017-04-04 Norbert J. Kot Pneumatic valve assembly and method
US10550863B1 (en) 2016-05-19 2020-02-04 Steven H. Marquardt Direct link circuit
US10914322B1 (en) 2016-05-19 2021-02-09 Steven H. Marquardt Energy saving accumulator circuit
US11015624B2 (en) 2016-05-19 2021-05-25 Steven H. Marquardt Methods and devices for conserving energy in fluid power production

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4144947A (en) * 1976-12-10 1979-03-20 David Brown Tractors Limited Power steering systems
DE2648608B2 (en) * 1976-10-27 1979-03-29 Walter Hunger Kg, 8770 Lohr Control device for a differential cylinder

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR694928A (en) * 1929-04-27 1930-12-09 Waterbury Tool Co Improvements to machine tool control mechanisms
US2379180A (en) * 1940-02-10 1945-06-26 Vickers Inc Hydraulic retractor control
US2267284A (en) * 1941-03-10 1941-12-23 Livers Carlos Benjamin By-pass valve
US2367682A (en) * 1943-04-09 1945-01-23 Adel Prec Products Corp Landing gear by-pass valve
US2376519A (en) * 1943-07-29 1945-05-22 French Oil Mill Machinery Valve control for presses and the like
US2694384A (en) * 1949-06-21 1954-11-16 Carroil L Evans Control mechanism for hydraulic rams with automatic and adjustable selfstopping mechanism
US2590454A (en) * 1949-09-13 1952-03-25 John S Pilch Hydraulic by-pass system and valve therefor
US2628731A (en) * 1949-09-17 1953-02-17 Bucyrus Erie Co Hydraulically operated tractor shovel
US2646025A (en) * 1951-02-07 1953-07-21 Bendix Aviat Corp By-pass valve for hydraulic motors
US2890683A (en) * 1952-02-06 1959-06-16 John S Pilch Fluid actuated control valve means for fluid motors
US3237636A (en) * 1962-01-22 1966-03-01 Hough Co Frank Controlled pressure by pass valve
US3234957A (en) * 1963-04-22 1966-02-15 Fawick Corp Adjustable, metered directional flow control arrangement
US3319653A (en) * 1963-11-21 1967-05-16 Borg Warner Flow control valves
US3267961A (en) * 1964-04-16 1966-08-23 New York Air Brake Co Valve
US3335739A (en) * 1964-12-03 1967-08-15 New York Air Brake Co Valve
US3439583A (en) * 1966-04-14 1969-04-22 Parker Hannifin Corp Flow control valve having a pressure limiting tubular valve member
US3448685A (en) * 1967-08-01 1969-06-10 Caterpillar Tractor Co Quick drop valve for bulldozer blade hydraulic controls
US3465788A (en) * 1967-09-01 1969-09-09 Koehring Co Hydraulic control valve with void prevention means
US3474708A (en) * 1968-01-17 1969-10-28 Parker Hannifin Corp Valve assembly for fluid motors and the like
US3474824A (en) * 1968-01-17 1969-10-28 Deere & Co Dump valve for hydraulic control system
US3497032A (en) * 1968-07-01 1970-02-24 Allis Chalmers Mfg Co Balanced hydraulic steering system
US3568707A (en) * 1968-12-16 1971-03-09 Int Harvester Co Quick drop valve
US3654835A (en) * 1970-05-25 1972-04-11 Ato Inc Regeneration valve
US3795177A (en) * 1971-11-04 1974-03-05 Caterpillar Tractor Co Fluid motor control circuit providing selective fast motion
JPS5730483Y2 (en) * 1976-06-10 1982-07-05
US4216702A (en) * 1978-05-01 1980-08-12 Eaton Yale Ltd. Pressure sensing regenerative hydraulic system

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2648608B2 (en) * 1976-10-27 1979-03-29 Walter Hunger Kg, 8770 Lohr Control device for a differential cylinder
US4144947A (en) * 1976-12-10 1979-03-20 David Brown Tractors Limited Power steering systems

Also Published As

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

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