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DE1601740A1 - Circuit for double-acting hydraulic clamping cylinder - Google Patents

Circuit for double-acting hydraulic clamping cylinder

Info

Publication number
DE1601740A1
DE1601740A1 DE19671601740 DE1601740A DE1601740A1 DE 1601740 A1 DE1601740 A1 DE 1601740A1 DE 19671601740 DE19671601740 DE 19671601740 DE 1601740 A DE1601740 A DE 1601740A DE 1601740 A1 DE1601740 A1 DE 1601740A1
Authority
DE
Germany
Prior art keywords
pressure source
line
piston
circuit
double
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.)
Pending
Application number
DE19671601740
Other languages
German (de)
Inventor
Dieter Dewald
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.)
Langen and Co
Original Assignee
Langen 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 Langen and Co filed Critical Langen and Co
Publication of DE1601740A1 publication Critical patent/DE1601740A1/en
Pending legal-status Critical Current

Links

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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • 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
    • F15B2211/30—Directional control
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/31552—Directional control characterised by the connections of the valve or valves in the circuit being connected to an output member and a return line
    • F15B2211/31558—Directional control characterised by the connections of the valve or valves in the circuit being connected to an output member and a return line having a single output member
    • 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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Landscapes

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

Description

Schaltung für doppeltwirkenden hydraulischen Spannzylinder Die Erfindung bezient sich auf eine Schaltung für eineft doppelt-. wirkenden hydraulischen Spannzylinder, dessen Kolbenraum über ein Wegevontil entweder mit einer Druckquelle oder mit einem Behälter verbunden werden kann und dessen Ringraum über eine Leitung mit der oruckquelle verbunden ist.Circuit for double-acting hydraulic clamping cylinder The invention refers to a circuit for one double. acting hydraulic clamping cylinder, its piston chamber via a directional valve either with a pressure source or with a Container can be connected and its annulus via a line with the oruckquelle connected is.

In der Hydraulik ist eine solche Schaltung auch unter dem Namen Differentialschaltung bekannti Ihr Zweck besteht darint beim Ausfahren des Kolbens eine höhere Geschwindigkeit zu erzielen als mit dem Förderstrom der Druckquelle allein erreichbar wäre. Das geschieht dadurch, daß die aus dem Ringraum verdrängte Flüssigkeit zusätzlich in den Kolbenraum gelangt. Wenn das Flächenverhältnis von Kolbenfläche und Ringfläche 2 : 1 ist, ergeben'sich bei einer solchen Schaltung gleiche Kolbengeschwindigkeiten beim Aus- und Linfahren des Kolbens. Diesem*Vorteil steht aber als Nachteil gegenüberg daß beim*Ausfahren des Kolbens als wirksame Fläche nur die Kolbenstangenfläche zur Ve"rftigüng steht, da durch die Druckgleichileit im Kolben- und Ringraum die Ringfläche von der Kolbenfläche subtrahiert werden muß. Diese Tatsache ist besonders bei Spann- und Preßvorgängen nachteiligt da der Zylinder nicht voll ausgenutzt worden kann. Es ist zwar möglich, In die Leitung vom Ringraum zur Druckquelle ein zweites Wegevontil einzubauen, doch es bedarf weiteren Aufwandes? um ein Umschalten' dieses iventils zur richtigen Zeit zu erreichen. En ist daher Aufgabe der Windunge mit geringem Aufwand die beschriebene Schaltung sezu ergänzen,- daß die Cha'rakterlatik einer-Differentialschaltung erhalten bleibt und zusätzlich ein Spannen oder Pressen mit der ganzen Kolbenfläche alt wirksame Ylgohe erfolgt, wobei auf die Anbringung zusätzlicher Wegavontilog Endochalter und dergleichen verzichtei worden soll. Die Lösung dieser Aufgabe erfolgt erfindungsgemäß dadurch, daß der Ringraum über eine Leitung mit einem weiteren Anschluß des Wegeventils verbunden ist, wobei dieser Anschluß mit dem Be-11,1älter verbunden ist, wenn der l,'olbenraur-i riit der Druckquelle in Verbindung steht und umgekehrt, und in die Leitung zwischen Wegeventil und Ringraum ein in Richtung Ringraum öffnendes Rückschlagventil geschaltet ist, das durch eine parallel geschaltete Drossel umgangen werden kann, und ein weiteres, in Richtung Druckquelle öffnendes Rückschlagventil in die Leitung zwischen Ringrauni und Druckquelle eingebaut ist. Der Vorteil dieser Schaltung liegt darin, daß durch Verwendung eines Rückschlagventils und eines Drosselrückschlagvont ils kein zusätzlicher Raumbedarf entsteht, da handelsübliche Elemente dieser Art in die Rohrleitung eingebaut werden können. Da es sich um konstruktiv einfache Teile hande lt, bleiben auch die Kosten gering. Anhand eines mit Hydrauliksymbolen dargestellten Schaltplanes wird die Erfindung näher erläutert. In einem Zylinder 1 gleitet ein Kolben 2, der mit einer Kolbenstange 3 verbunden ist. Die Kolbenstange 3 drUckt ein WerkstUck gegen einen Anschlag 5. Der Kolbenraum 6 des Zylindars 1 ist Über eine Leitung 7 mit dem Anschluß A eines Wegeventils 8 verbunden, das Über einen Anschluß P mit einer Druckguelle 9 und über einen Anschluß T mit einem Behälter lo verbunden ist. Von einem vierten Anschluß B zweigt eine Leitung 11 zum Ringraum 12 ab. In die Leitung 11 1,st ein Rückschlagventil 13 geschaltet# welchen in Richtung Ringraum 12 öffnet und dem eine Drossel 14 parallel geschaltet ist. Eine Leitung 15f in die ein in Richtung Druckquelle öffnendes Rückschlagventil 16 eingebaut ist, schafft eine Verbindung vom Ringraum 12 zur Druckquelle 9. Wenn das Wegeventil 8 auf "parallele Pfeile" geschaltet ist, wird der Kolbenraum 6 mit der Druckquelle 9 verbunden, und der Kolben 2 fährt aus. Weil die Kolbenfläche F größer als die Ringfläche 9 ist, entsteht eine DruckUbernetzung derart#,daß.der der Druck in. Ringraum größer wird. Unter Voraussetzung, daß die Drossel 14 nur aus einer sehr kleinen Öffnung besteht, wirdan dieser Stelle auch'nur eine sehr geringe, unbedeutende Flüs:-sigkeitsmenje durchströmen. Der Hauptanteil strömt daher durch die Leitung 15, öffnet aufgrund des Druckunterschiedes das Rückschlagventil 16 und gelangt über die Anschlüsse P und A des Wegeventils sowie die Leitung 7 in den Kolbenraum 6., Diese 31fferentialwirkung bleibt solange bestehen, bis die Kolbenstange 3 auf das Werkstück 4 stößt. Da nunmehr nach einen. eventuellen, geringen Spannhub 'Keine Bewegung, des Kolbens mehr stattfindet, fließt auch keine nennenswerte Flüssigkeitsr-iienge mehr aus-dem Ringraum IZ. Infolgedessen kann sich der Druck im R#ng-raun 12 über die Drossel 14, die"j,a über die Leitung 11 und das Wegeventil 3 mit den, Behälter la verbunden ist,-abbauen. Das Rückschlagventil 16 schließt sich- aufgrund der nunmehr einseitigen Druckbeaufschlagung von, der Druckquelle 9 her. Durch den Druckabbau in Ringraum 12 wird der Kolben 2 auf seiner vollen Fläche F belastet. Diese Belastung erfolgt automatisch bei Beendigung der Vorschubbewegung unabhängig von dem zurückgelegten Weg. Dies ermöglicht Z.B. die Spannung verschieden dicker Werkstücke ohne Änderung der Spannvorrichtung. Das Umschalten des Wegeventils kann dann beispielsweise elektrisch bei Beendigung eines B6arbeitungsvorgangs erfolgen-. Grundsätzrlich ist die Art der Wegeventilbetätigung aber freigestellt. Bei Schaltung- des Viegeventils 8 #uf "gekreuzte Pfeile" wird der Kolbenraum 6 mit dem Behälter la verbunden, während der Ringraum 12 über die Leitung 11, das nurLmehr frei durchströmte Rückschlagventil 13 und das Wegeventil 8 mit der Druckquelle 9 verbunden wird. Bei einem Verhältnis von F : f = 2 : 1 erfolgt das Linfahren des Kolbens 2 etwa so schnell wie das Ausfahren.. Besonders bei großen, sperrigen WerkstÜcken, dic einen großen Hub des Kolbens 2 erfordern., ergibt sich so eine beträchtliche Zeitersparnis-.In hydraulics, such a circuit is also known as a differential circuit. Its purpose is to achieve a higher speed when the piston is extended than could be achieved with the flow of the pressure source alone. This happens because the liquid displaced from the annular space also enters the piston space. If the area ratio of the piston area and the ring area is 2 : 1 , the piston speeds when the piston is extended and retracted are the same with such a circuit. This advantage is opposed to the disadvantage that when the piston is extended, only the piston rod surface is available as the effective surface, since the pressure equilibrium in the piston and ring chamber means that the ring surface must be subtracted from the piston surface. This fact is particularly important with clamping -.?. and pressing operations at a disadvantage because the cylinder can not been fully utilized, it is possible to incorporate into the line from the annular space to the pressure source a second Wegevontil, but it requires additional expenses by switching to achieve 'this iventils the right time En is Therefore, the task of the winding to supplement the circuit described with little effort, - that the cha'rakterlatik of a differential circuit is retained and in addition a clamping or pressing with the entire piston surface old effective Ylgohe takes place, with the attachment of additional Wegavontilog Endochalter and the like been dispensed with This problem is solved in accordance with the invention according to the fact that the annular space is connected via a line to a further connection of the directional control valve, this connection being connected to the container when the oil is connected to the pressure source and vice versa, and in the line between the directional control valve and the annulus is connected to a check valve that opens in the direction of the annulus, which can be bypassed by a throttle connected in parallel, and another check valve that opens towards the pressure source is installed in the line between the annulus and the pressure source. The advantage of this circuit is that no additional space is required by using a check valve and a throttle check valve, since commercially available elements of this type can be built into the pipeline. Since these are structurally simple parts, the costs also remain low. The invention is explained in more detail using a circuit diagram shown with hydraulic symbols. A piston 2, which is connected to a piston rod 3 , slides in a cylinder 1. The piston rod 3 presses a workpiece against a stop 5. The piston chamber 6 of the cylinder 1 is connected via a line 7 to the connection A of a directional control valve 8 , which is connected via a connection P to a pressure source 9 and via a connection T to a container lo is. A line 11 branches off from a fourth connection B to the annular space 12. A check valve 13 is connected in line 11 1, which opens in the direction of the annular space 12 and to which a throttle 14 is connected in parallel. A line 15f in which a check valve 16 opening in the direction of the pressure source is installed creates a connection from the annular space 12 to the pressure source 9. If the directional control valve 8 is switched to "parallel arrows", the piston chamber 6 is connected to the pressure source 9 , and the piston 2 extends. Because the piston area F is larger than the ring area 9 , pressure cross-linking occurs in such a way that the the Pressure in. Annular space becomes larger. Provided that the Throttle 14 consists only of a very small opening, only a very small, insignificant amount of liquid will flow through at this point. Therefore, the major proportion flows through the line 15 opens due to the pressure difference, the check valve 16 and passes via the ports P and A of the directional valve and the line remains 7 6 into the piston chamber, this 31fferentialwirkung exist until the piston rod 3 to the workpiece 4 bumps. Since now after a. possible "small clamping stroke" No movement, the piston takes place any more, and no more liquid streams worth mentioning flows out of the annular space IZ. As a result, the pressure in the ring 12 can be reduced via the throttle 14, which is connected to the container la via the line 11 and the directional valve 3. The check valve 16 now closes due to the unilateral pressurization from the pressure source 9. Due to the pressure reduction in the annular space 12, the piston 2 is loaded over its full area F. This loading takes place automatically at the end of the feed movement regardless of the distance covered the clamping device. the switching of the directional control valve may then, for example, electrically erfolgen- upon completion of B6arbeitungsvorgangs. Grundsätzrlich the type of directional valve actuation in integrated circuit of Viegeventils but is optional. 8 #uf "crossed arrows" of the piston chamber 6 to the container la is connected, while the annular space 12 via the line 11, the non-return valve 13, through which flow is now free, and the directional control valve 8 is connected to the pressure source 9 . At a ratio of F : f = 2 : 1 , the piston 2 is moved about as quickly as it is extended. Particularly in the case of large, bulky workpieces that require a large stroke of the piston 2, this results in considerable time savings.

Claims (1)

Patentanspruch: Schaltung für einen doppeltwirkenden hydraulischen Spannzylinder, dessen Kolbenraum über ein Wegeventil entweder mit einer Druckquelle oder mit einem Behälter verbunden werden kann und dessen Ringraum über eine Leitung mit der Druckquelle verbunden ist# dadurch gekennzeichnet, daß der Ringraum (12) über eine Leitung (11) mit einem weiteren Anschluß (13) des Wegeventils (8) verbunden ist, wobei dieser Anschluß (B) mit dent Behälter (lo) verbunden ist, wenn der Kolbänraunt (6) mit der Druckquelle (9) in Verbindung steht und =gekehrt, und in die Leitung (11) zwischen Wegeventil (3) unü Rincjrauni (12) ein in Richtung Ringraum (12) öffnendes Rückschlagventil (13) geschaltet ist, das durch eine parallel geschaltete Drossel (14) umgangen werden kann, und ein weiteres, in Richtung Druckquelle (9) öffnendes Rückschlagventil (16) in die Leitung (15) zwischen Ringraum (12) und Druckquelle (9) eingebaut ist.Claim: Circuit for a double-acting hydraulic clamping cylinder, the piston chamber of which can be connected to either a pressure source or to a container via a directional valve and the annular chamber of which is connected to the pressure source via a line # characterized in that the annular chamber (12) is connected via a line ( 11) is connected to a further connection (13) of the directional valve (8) , this connection (B) being connected to the container (lo) when the Kolbänraunt (6) is connected to the pressure source (9) and = turned , and in the line (11) between the directional valve (3) and Rincjrauni (12) a non-return valve (13 ) which opens in the direction of the annular space (12) and which can be bypassed by a throttle (14) connected in parallel, and another, check valve (16 ) opening in the direction of the pressure source (9) is installed in the line (15) between the annular space (12) and the pressure source (9).
DE19671601740 1967-02-15 1967-02-15 Circuit for double-acting hydraulic clamping cylinder Pending DE1601740A1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEL0055751 1967-02-15

Publications (1)

Publication Number Publication Date
DE1601740A1 true DE1601740A1 (en) 1971-01-14

Family

ID=7277202

Family Applications (1)

Application Number Title Priority Date Filing Date
DE19671601740 Pending DE1601740A1 (en) 1967-02-15 1967-02-15 Circuit for double-acting hydraulic clamping cylinder

Country Status (1)

Country Link
DE (1) DE1601740A1 (en)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2714722A1 (en) * 1976-04-01 1977-10-06 Smedby Mk Verkstad Ab Double acting crane ram valve mechanism - has throttle valve in return passage with bypass pipe
WO1999067537A1 (en) * 1998-06-24 1999-12-29 Bae Systems Plc Actuator system for aerospace controls and functions
WO2018056036A1 (en) * 2016-09-21 2018-03-29 Smc Corporation Driving method and driving device of fluid pressure cylinder
CN109790859A (en) * 2016-09-21 2019-05-21 Smc 株式会社 Fluid pressure cylinder
US20190277310A1 (en) * 2016-09-21 2019-09-12 Smc Corporation Driving method and driving device of fluid pressure cylinder

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2714722A1 (en) * 1976-04-01 1977-10-06 Smedby Mk Verkstad Ab Double acting crane ram valve mechanism - has throttle valve in return passage with bypass pipe
WO1999067537A1 (en) * 1998-06-24 1999-12-29 Bae Systems Plc Actuator system for aerospace controls and functions
WO2018056036A1 (en) * 2016-09-21 2018-03-29 Smc Corporation Driving method and driving device of fluid pressure cylinder
CN109790859A (en) * 2016-09-21 2019-05-21 Smc 株式会社 Fluid pressure cylinder
US20190277310A1 (en) * 2016-09-21 2019-09-12 Smc Corporation Driving method and driving device of fluid pressure cylinder
US20200025224A1 (en) * 2016-09-21 2020-01-23 Smc Corporation Fluid pressure cylinder
CN109790859B (en) * 2016-09-21 2020-08-25 Smc 株式会社 Fluid pressure cylinder
RU2731783C1 (en) * 2016-09-21 2020-09-08 СМСи КОРПОРЕЙШН Method and device for hydraulic (pneumatic) cylinder drive
US10883523B2 (en) 2016-09-21 2021-01-05 Smc Corporation Fluid pressure cylinder
US10927857B2 (en) 2016-09-21 2021-02-23 Smc Corporation Driving method and driving device of fluid pressure cylinder
RU2731783C9 (en) * 2016-09-21 2021-06-22 СМСи КОРПОРЕЙШН Driving method and driving device for fluid pressure cylinder

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