EP1076778B1 - Device for the stroke-dependent adjustment of the force generated by a piston - Google Patents

Device for the stroke-dependent adjustment of the force generated by a piston Download PDF

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Publication number
EP1076778B1
EP1076778B1 EP99948561A EP99948561A EP1076778B1 EP 1076778 B1 EP1076778 B1 EP 1076778B1 EP 99948561 A EP99948561 A EP 99948561A EP 99948561 A EP99948561 A EP 99948561A EP 1076778 B1 EP1076778 B1 EP 1076778B1
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EP
European Patent Office
Prior art keywords
cylinder
chamber
piston
force generated
counterpressure
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP99948561A
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German (de)
French (fr)
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EP1076778A1 (en
Inventor
Rolf-Günter LITZEL
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Henkel Loctite Deutschland GmbH
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Henkel Loctite Deutschland GmbH
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    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/046—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed depending on the position of the working member
    • F15B11/048—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed depending on the position of the working member with deceleration control
    • 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
    • F15B2211/3056—Assemblies of multiple 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3138—Directional control characterised by the positions of the valve element the positions being discrete
    • 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
    • F15B2211/31523—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member
    • F15B2211/31541—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source and an output member having a single pressure source and multiple output members
    • 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • 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
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50554—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure downstream of the pressure control means, e.g. pressure reducing 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5158—Pressure control characterised by the connections of the pressure control means in the circuit being connected to a pressure source and an 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
    • F15B2211/50—Pressure control
    • F15B2211/565—Control of a downstream pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7107—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being mechanically linked
    • 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
    • F15B2211/76—Control of force or torque of the output member

Definitions

  • the invention relates to a method and an apparatus for path-dependent control of those generated by a first piston Force that runs in a first cylinder that passes through the first piston divided into a first and a second chamber , whereby a pressure fluid is fed into the first chamber.
  • a second cylinder is also provided, in which a second piston runs and the second piston also is divided into a first and a second chamber.
  • a similarly constructed system is known from DE-A-44 41 098, that acts as a power-assisted actuator.
  • the fluid pressure is generated by a master cylinder and the first chamber of a slave cylinder and the first chamber of a cylinder fed to a translation unit.
  • the System works hydraulically and the slave cylinder and the Cylinders of the translation unit are graduated, the second chambers each have the larger diameter.
  • at Existing external power supply is the translation unit held at rest since the one generated by the master cylinder Pressure is insufficient to move the piston of the translation unit against the pressure of the external power supply acting in its second chamber to postpone. If there is no external power supply this counterforce is eliminated and the piston is displaced, which reduces the size of the second chamber.
  • the thereby pressure built up at the point of entry of the external force is passed into the second chamber of the slave cylinder and thereby supports this.
  • DE-A-1 576 181 describes a method and an apparatus the features of the preamble of claims 1 and 4 known. It is a hydraulic feed device for loading various parts of a machine tool, at the two double-acting cylinders are mechanically coupled.
  • the extension speed of the pistons can be adjusted by valves can be controlled by the pressure fluid either only in one Chamber one of the two cylinders or in the respective on the chambers of both cylinders lying on the same side of the pistons is initiated. If the pressure fluid is only in one chamber of the two cylinders introduced, so are the other chamber this cylinder and the two chambers of the other cylinder with each other and with the speed control trigger of the pressure fluid connected.
  • the invention as set out in claims 1 and 4 is based on the task generated by a piston Force in the simplest possible way depending on the To control the travel path of the piston.
  • the two pistons are coupled so that the second piston of is dragged along with the first piston and the second chamber of the first cylinder is with the first chamber of the second Cylinder connected so that the same in both chambers There is pressure.
  • the fluid from the second chamber of the first cylinder to the first Chamber of the second cylinder moved.
  • the two pistons move synchronously, so that at one Extending the reduction of the second chamber of the first cylinder with an enlargement of the first chamber of the second cylinder goes hand in hand.
  • the diameter of the second cylinder made larger than that of the first cylinder, so increases with an extension movement of the first Piston the total volume of the second chamber of the first Cylinder and the first chamber of the second cylinder so that the back pressure drops and that generated by the first cylinder Force continuously when extending the first piston depending on the distance increases.
  • the force generated by the first piston is one largely continuous and linear function of its extension path.
  • the pressure in the second chamber of the second cylinder becomes like this regulated that it is always equal to the back pressure, i.e. the Pressure in the first chamber of the second cylinder and in the second chamber of the first cylinder.
  • the two cylinder / piston units can be used with standard cylinders be a piston and have the two chambers of each cylinder same diameter.
  • the coupling of the two pistons is expedient mechanical and form-fitting.
  • the initial back pressure value is the first Adjustable cylinder, for which the second chamber via a Regulator on which the initial value of the back pressure can be set is connected to the source of pressure fluid.
  • the pressurized fluid is preferably a pressurized gas, in particular Compressed air, being the source of the pressurized fluid, the pressurized gas or compressed air is the only energy source in the system.
  • the invention is applicable, for example, to a device for dispensing viscous masses in aluminum cartridges with a wavy surface are included.
  • the viscous mass it can be an adhesive, for example. at the cartridge is compressed to dispense the mass.
  • the cartridge can be placed in an output device be inserted into it by the first piston is applied to the device according to the invention.
  • a first or Output cylinder 10 and a second or control cylinder 20 in parallel arranged side by side.
  • the output cylinder 10 runs a first or output piston 12 with a piston rod 14, the output cylinder 10 in a first chamber 16 and divides a second chamber 18, the second chamber 18 is on the side of the piston rod 14.
  • the control cylinder 20 runs in a corresponding manner second or control piston 22 with a piston rod 24, the the control cylinder 20 into a first chamber 26 and a second Chamber 28 divided, with the second chamber 28 on the side the piston rod 24 is located.
  • the two piston rods 14, 24 are outside the cylinder 10, 20 mechanically positively by means of an indicated connection 30 coupled so that they only move synchronously can.
  • Compressed air from a compressed air source serves as the pressurized fluid 32 via a shut-off valve 34, a manually operated slide 36 with three positions and a throttle 38 by means of a line 40 passed into the first chamber 16 of the dispensing cylinder 10 becomes.
  • the extension speed is by means of the throttle 38 of the output piston 12 adjustable.
  • a parallel one Check valve 56 is used to quickly vent the first Chamber 16 of the discharge cylinder 10.
  • the shut-off valve 34 and the slide 36 are shown in Fig. 1 in their locked position. To pass the pressure fluid, both are shifted so that a connection between the connections 1 and 2 or 1 and 4 exists.
  • the second chamber is via a second line 42 18 of the dispensing cylinder 10 with the first chamber 26 of the Control cylinder 20 connected.
  • the initial value of these two chambers 18, 26 and the second line 42 prevailing Back pressure can be a second shut-off valve 44 and Back pressure regulator 46 can be set by means of a third line 48 connected to the terminal 2 of the slide 36 and by adjusting the slide accordingly 36 can be connected to the compressed air source 32.
  • a third line 48 is located between the back pressure regulator 46 and the connection 2 of the slide 36 a check valve 50, the compressed air only from the compressed air source 32 to the back pressure regulator 46 passes.
  • connection 2 with the second chamber 28 of the control cylinder 20 By means of a linear regulator 52, the connection 2 with the second chamber 28 of the control cylinder 20, the control signal connection 4 with the second line 42 and its connection 1 via a check valve 54 and the shut-off valve 34 with the Compressed air source 32 is connected and its connection 3 free is, the pressure in the second chamber 28 of the control cylinder 20 regulated so that it is equal to the pressure in the first Chamber 26 of the control cylinder 20 and thus equal to the back pressure in the output cylinder 10.
  • the first shut-off valve 34 is in its Brought forward position.
  • the slide 36 is set so that a connection between the connections 1 and 2 there is, so that the back pressure on the back pressure regulator 46 and the second shut-off valve 44, which is in its pass-through position stands, can build, e.g. to 2 bar.
  • In this position becomes the first chamber 16 of the dispensing cylinder 10 via a check valve lying parallel to the throttle 38 56 and the connection between the terminals 4 and 3 of the Slider 36 vented.
  • the two pistons 12, 22 thereby move back to their starting position, in which the volumes of the first chambers 16, 26 minimal and those of the second chambers 18, 28 are maximum.
  • the first shut-off valve 34 is used to vent the device brought into its locked position, the slide 36 in the position, in which the connections 1 and 2 or 3 and 4 are connected are, so that the first line 40 is vented.
  • the second Line 42 is aerated, the piston rods 14 and 24th retracted and the chambers 18, 26 and 28 with the regulated Initial value of the back pressure, e.g. 2 bar filled. Will if necessary the second shut-off valve 44 in its venting position brought, the second line 42 is vented.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Steering Control In Accordance With Driving Conditions (AREA)
  • Actuator (AREA)

Abstract

The aim of the invention is to adjust the force generated by a first piston (12) in accordance with its stroke. Said first piston (12) is displaced in a first cylinder (10) which by the first piston (12) is divided into a first and a second chamber (16, 18). A fluid under pressure (32) is fed into the first chamber (16). The invention provides for a second cylinder (20) in which a second piston (22) is displaced and which by said second piston (22) is also divided into a first and a second chamber (26, 28). The two pistons (12, 22) are mechanically coupled (30) so that the second piston (22) is driven by the first piston (12). The second chamber (18) of the first cylinder (10) is connected via a line (42) with the first chamber (26) of the second cylinder (20) so that the same pressure prevails in both chambers (18, 26). The pressure in the second chamber (28) of the second cylinder (20) is appropriately adjusted in such a way that it is always equal to the back pressure in the first chamber (26) of the second cylinder (20) and the second chamber (18) of the first cylinder (10). The initial value of the back pressure in the second chamber (18) of the first cylinder (10) can be adjusted. If the diameter of the second cylinder (20) is greater (smaller) than that of the first cylinder (10), the back pressure falls (rises) when the first piston (12) is displaced outward and the force produced by the first piston (12) rises (falls) linearly according to the piston stroke.

Description

Die Erfindung betrifft ein Verfahren und eine Vorrichtung zum wegabhängigen Steuern der von einem ersten Kolben erzeugten Kraft, der in einem ersten Zylinder läuft, der durch den ersten Kolben in eine erste und eine zweite Kammer unterteilt wird, wobei ein Druckfluid in die erste Kammer geleitet wird. Es ist ferner ein zweiter Zylinder vorgesehen, in dem ein zweiter Kolben läuft und der durch den zweiten Kolben ebenfalls in eine erste und eine zweite Kammer unterteilt wird.The invention relates to a method and an apparatus for path-dependent control of those generated by a first piston Force that runs in a first cylinder that passes through the first piston divided into a first and a second chamber , whereby a pressure fluid is fed into the first chamber. A second cylinder is also provided, in which a second piston runs and the second piston also is divided into a first and a second chamber.

Aus DE-A-44 41 098 ist ein ähnlich aufgebautes System bekannt, das als fremdkraftunterstützte Betätigungsvorrichtung wirkt. Der Fluiddruck wird von einem Geberzylinder erzeugt und der ersten Kammer eines Nehmerzylinders und der ersten Kammer eines Zylinders einer Übersetzungseinheit zugeführt. Das System arbeitet hydraulisch und der Nehmerzylinder und der Zylinder der Übersetzungseinheit sind abgestuft, wobei die zweiten Kammern jeweils den größeren Durchmesser haben. Bei bestehender Fremdkraftversorgung ist die Übersetzungseinheit in Ruhestellung gehalten, da der vom Geberzylinder erzeugte Druck nicht ausreicht, um den Kolben der Übersetzungseinheit gegen den in ihrer zweiten Kammer wirkenden Druck der Fremdkraftversorgung zu verschieben. Bei fehlender Fremdkraftversorgung entfällt diese Gegenkraft und der Kolben wird verschoben, wodurch die zweite Kammer verkleinert wird. Der dadurch am Einspeisungspunkt der Fremdkraft aufgebaute Druck wird in die zweite Kammer des Nehmerzylinders geleitet und unterstützt diesen dadurch. A similarly constructed system is known from DE-A-44 41 098, that acts as a power-assisted actuator. The fluid pressure is generated by a master cylinder and the first chamber of a slave cylinder and the first chamber of a cylinder fed to a translation unit. The System works hydraulically and the slave cylinder and the Cylinders of the translation unit are graduated, the second chambers each have the larger diameter. at Existing external power supply is the translation unit held at rest since the one generated by the master cylinder Pressure is insufficient to move the piston of the translation unit against the pressure of the external power supply acting in its second chamber to postpone. If there is no external power supply this counterforce is eliminated and the piston is displaced, which reduces the size of the second chamber. The thereby pressure built up at the point of entry of the external force is passed into the second chamber of the slave cylinder and thereby supports this.

Aus DE-A-1 576 181 ist ein Verfahren und eine Vorrichtung mit den Merkmalen des Oberbegriffs der Ansprüche 1 bzw. 4 bekannt. Es handelt sich hierbei um eine hydraulische Speisevorrichtung zum Beschicken verschiedener Teile einer Werkzeugmaschine, bei der zwei doppelwirkende Zylinder mechanisch gekoppelt sind. Durch Ventile kann die Ausfahrgeschwindigkeit der Kolben gesteuert werden, indem das Druckfluid entweder nur in eine Kammer eines der beiden Zylinder oder in die jeweils auf der gleichen Seite der Kolben liegende Kammern beider Zylinder eingeleitet wird. Wird das Druckfluid nur in eine Kammer eines der beiden Zylinder eingeleitete, so sind die andere Kammer dieses Zylinders und die beiden Kammern des anderen Zylinders miteinander und mit dem die Geschwindigkeit steuernden Abzug des Druckfluids verbunden.DE-A-1 576 181 describes a method and an apparatus the features of the preamble of claims 1 and 4 known. It is a hydraulic feed device for loading various parts of a machine tool, at the two double-acting cylinders are mechanically coupled. The extension speed of the pistons can be adjusted by valves can be controlled by the pressure fluid either only in one Chamber one of the two cylinders or in the respective on the chambers of both cylinders lying on the same side of the pistons is initiated. If the pressure fluid is only in one chamber of the two cylinders introduced, so are the other chamber this cylinder and the two chambers of the other cylinder with each other and with the speed control trigger of the pressure fluid connected.

Der Erfindung, wie sie in den Ansprüchen 1 und 4 angegeben ist, liegt die Aufgabe zugrunde die von einem Kolben erzeugte Kraft auf möglichst einfache Weise in Abhängigkeit von dem Fahrweg des Kolbens zu steuern.The invention as set out in claims 1 and 4 is based on the task generated by a piston Force in the simplest possible way depending on the To control the travel path of the piston.

Die beiden Kolben sind gekoppelt, so daß der zweite Kolben von dem ersten Kolben mitgeschleppt wird, und die zweite Kammer des ersten Zylinders ist mit der ersten Kammer des zweiten Zylinders verbunden, so daß in beiden Kammern der gleiche Druck herrscht.The two pistons are coupled so that the second piston of is dragged along with the first piston and the second chamber of the first cylinder is with the first chamber of the second Cylinder connected so that the same in both chambers There is pressure.

Bei einer Ausfahrbewegung des ersten Kolbens wird das Fluid aus der zweiten Kammer des ersten Zylinders in die erste Kammer des zweiten Zylinders verschoben. Durch die Koppelung der beiden Kolben bewegen sie sich synchron, so daß bei einer Ausfahrbewegung die Verkleinerung der zweiten Kammer des ersten Zylinders mit einer Vergrößerung der ersten Kammer des zweiten Zylinders einhergeht. Wird nun der Durchmesser des zweiten Zylinders größer gemacht als der des ersten Zylinders, so vergrößert sich bei einer Ausfahrbewegung des ersten Kolbens das Gesamtvolumen der zweiten Kammer des ersten Zylinders und der ersten Kammer des zweiten Zylinders, so daß der Gegendruck sinkt und die von dem ersten Zylinder erzeugte Kraft beim Ausfahren des ersten Kolbens wegabhängig kontinuierlich zunimmt.When the first piston extends, the fluid from the second chamber of the first cylinder to the first Chamber of the second cylinder moved. Through the coupling of the two pistons they move synchronously, so that at one Extending the reduction of the second chamber of the first cylinder with an enlargement of the first chamber of the second cylinder goes hand in hand. If the diameter of the second cylinder made larger than that of the first cylinder, so increases with an extension movement of the first Piston the total volume of the second chamber of the first Cylinder and the first chamber of the second cylinder so that the back pressure drops and that generated by the first cylinder Force continuously when extending the first piston depending on the distance increases.

Hat der zweite Zylinder dagegen einen kleineren Durchmesser, so sinkt die von dem ersten Zylinder erzeugte Kraft bei einer Ausfahrbewegung kontinuierlich.If the second cylinder has a smaller diameter, so the force generated by the first cylinder drops at one Extending movement continuously.

In jedem Fall ist die von dem ersten Kolben erzeugt Kraft eine weitgehend stetige und lineare Funktion seines Ausfahrweges.In any case, the force generated by the first piston is one largely continuous and linear function of its extension path.

Der Druck in der zweiten Kammer des zweiten Zylinders wird so geregelt, daß er stets gleich dem Gegendruck ist, d.h. dem Druck in der ersten Kammer des zweiten Zylinders und in der zweiten Kammer des ersten Zylinders.The pressure in the second chamber of the second cylinder becomes like this regulated that it is always equal to the back pressure, i.e. the Pressure in the first chamber of the second cylinder and in the second chamber of the first cylinder.

Die beiden Zylinder/Kolben-Einheiten können Normzylinder mit einem Kolben sein und die beiden Kammern jedes Zylinders haben gleichen Durchmesser. Die Koppelung der beiden Kolben ist zweckmäßig mechanisch und formschlüssig. The two cylinder / piston units can be used with standard cylinders be a piston and have the two chambers of each cylinder same diameter. The coupling of the two pistons is expedient mechanical and form-fitting.

Vorzugsweise ist der Anfangswert des Gegendrucks des ersten Zylinders einstellbar, wozu dessen zweite Kammer über einen Regler, an dem der Anfangswert des Gegendrucks einstellbar ist, mit der Quelle für Druckfluid verbindbar ist.Preferably the initial back pressure value is the first Adjustable cylinder, for which the second chamber via a Regulator on which the initial value of the back pressure can be set is connected to the source of pressure fluid.

Das Druckfluid ist vorzugsweise ein Druckgas, insbesonder Druckluft, wobei die Quelle für das Druckfluid, das Druckgas oder die Druckluft die einzige Energiequelle des.Systems ist.The pressurized fluid is preferably a pressurized gas, in particular Compressed air, being the source of the pressurized fluid, the pressurized gas or compressed air is the only energy source in the system.

Die Erfindung ist beispielsweise anwendbar für eine Vorrichtung zur Ausgabe viskoser Massen, die in Aluminium-Kartuschen mit welliger Oberfläche enthalten sind. Bei der viskosen Masse kann es sich beispielsweise um einen Klebstoff handeln. Bei der Ausgabe der Masse wird die Kartusche zusammengedrückt. Die dafür erforderliche Kraft ist um so größer, je weiter die Kartusche bereits zusammengedrückt ist. Um die viskose Masse mit zeitlich konstantem Volumenstrom auszugeben, ist es daher notwendig, die auf die Kartusche ausgeübte Kraft in Abhängigkeit von der Rest-Größe der Kartusche zu steuern, und zwar ansteigen zu lassen. Die Kartusche kann dazu in eine Ausgabevorrichtung eingelegt werden, in der sie durch den ersten Kolben der erfindungsgemäßen Vorrichtung beaufschlagt wird.The invention is applicable, for example, to a device for dispensing viscous masses in aluminum cartridges with a wavy surface are included. With the viscous mass it can be an adhesive, for example. at the cartridge is compressed to dispense the mass. The the further the cartridge, the greater the force required is already compressed. To the viscous mass with output constant volume flow over time, it is therefore necessary the force exerted on the cartridge depending to control the remaining size of the cartridge, and increase allow. For this purpose, the cartridge can be placed in an output device be inserted into it by the first piston is applied to the device according to the invention.

Ein Ausführungsbeispiel der Erfindung wird nachfolgend anhand der Zeichnung erläutert, wobei

Fig. 1
ein Schaltbild der Drucksteuerung zeigt.
An embodiment of the invention is explained below with reference to the drawing, wherein
Fig. 1
shows a circuit diagram of the pressure control.

In dem dargestellten Ausführungsbeispiel sind ein erster oder Ausgabezylinder 10 und ein zweiter oder Steuerzylinder 20 parallel nebeneinander angeordnet. In dem Ausgabezylinder 10 läuft ein erster oder Ausgabekolben 12 mit einer Kolbenstange 14, der den Ausgabezylinder 10 in eine erste Kammer 16 und eine zweite Kammer 18 unterteilt, wobei die zweite Kammer 18 auf der Seite der Kolbenstange 14 liegt. In the illustrated embodiment, a first or Output cylinder 10 and a second or control cylinder 20 in parallel arranged side by side. In the output cylinder 10 runs a first or output piston 12 with a piston rod 14, the output cylinder 10 in a first chamber 16 and divides a second chamber 18, the second chamber 18 is on the side of the piston rod 14.

In entsprechender Weise läuft in dem Steuerzylinder 20 ein zweiter oder Steuerkolben 22 mit einer Kolbenstange 24, der den Steuerzylinder 20 in eine erste Kammer 26 und eine zweite Kammer 28 unterteilt, wobei die zweite Kammer 28 auf der Seite der Kolbenstange 24 liegt.The control cylinder 20 runs in a corresponding manner second or control piston 22 with a piston rod 24, the the control cylinder 20 into a first chamber 26 and a second Chamber 28 divided, with the second chamber 28 on the side the piston rod 24 is located.

Die beiden Kolbenstangen 14, 24 sind außerhalb der Zylinder 10, 20 durch eine angedeutete Verbindung 30 mechanisch formschlüssig gekoppelt, so daß sie sich nur synchron bewegen können.The two piston rods 14, 24 are outside the cylinder 10, 20 mechanically positively by means of an indicated connection 30 coupled so that they only move synchronously can.

Als Druckfluid dient Druckluft, die von einer Druckluftquelle 32 über ein Absperrventil 34, einen handbetätigten Schieber 36 mit drei Stellungen und eine Drossel 38 mittels einer Leitung 40 in die erste Kammer 16 des Ausgabezylinders 10 geleitet wird. Mittels der Drossel 38 ist die Ausfahrgeschwindigkeit des Ausgabekolbens 12 einstellbar. Ein parallel liegendes Rückschlagventil 56 dient zum schnellen Entlüften der ersten Kammer 16 des Ausgabezylinders 10. Das Absperrventil 34 und der Schieber 36 sind in Fig. 1 in ihrer Sperrstellung gezeigt. Zur Durchleitung des Druckfluids werden beide so verschoben, daß eine Verbindung zwischen den Anschlüssen 1 und 2 bzw. 1 und 4 besteht. Über eine zweite Leitung 42 ist die zweite Kammer 18 des Ausgabezylinders 10 mit der ersten Kammer 26 des Steuerzylinders 20 verbunden. Der Anfangswert des in diesen beiden Kammern 18, 26 und der zweiten Leitung 42 herrschenden Gegendrucks kann über ein zweites Absperrventil 44 und einen Gegendruck-Regler 46 eingestellt werden, der mittels einer dritten Leitung 48 mit dem Anschluß 2 des Schiebers 36 verbunden ist und der durch entsprechende Einstellung des Schiebers 36 mit der Druckluftquelle 32 verbindbar ist. In der dritten Leitung 48 befindet sich zwischen dem Gegendruckregler 46 und dem Anschluß 2 des Schiebers 36 ein Rückschlagventil 50, das Druckluft nur von der Druckluftquelle 32 zu dem Gegendruck-Regler 46 durchläßt. Compressed air from a compressed air source serves as the pressurized fluid 32 via a shut-off valve 34, a manually operated slide 36 with three positions and a throttle 38 by means of a line 40 passed into the first chamber 16 of the dispensing cylinder 10 becomes. The extension speed is by means of the throttle 38 of the output piston 12 adjustable. A parallel one Check valve 56 is used to quickly vent the first Chamber 16 of the discharge cylinder 10. The shut-off valve 34 and the slide 36 are shown in Fig. 1 in their locked position. To pass the pressure fluid, both are shifted so that a connection between the connections 1 and 2 or 1 and 4 exists. The second chamber is via a second line 42 18 of the dispensing cylinder 10 with the first chamber 26 of the Control cylinder 20 connected. The initial value of these two chambers 18, 26 and the second line 42 prevailing Back pressure can be a second shut-off valve 44 and Back pressure regulator 46 can be set by means of a third line 48 connected to the terminal 2 of the slide 36 and by adjusting the slide accordingly 36 can be connected to the compressed air source 32. In the third line 48 is located between the back pressure regulator 46 and the connection 2 of the slide 36 a check valve 50, the compressed air only from the compressed air source 32 to the back pressure regulator 46 passes.

Mittels eines Linear-Reglers 52, dessen Anschluß 2 mit der zweiten Kammer 28 des Steuerzylinders 20, dessen Steuersignal-Anschluß 4 mit der zweiten Leitung 42 und dessen Anschluß 1 über ein Rückschlagventil 54 und das Absperrventil 34 mit der Druckluftquelle 32 verbunden ist und dessen Anschluß 3 frei ist, wird der Druck in der zweiten Kammer 28 des Steuerzylinders 20 so geregelt, daß er gleich dem Druck in der ersten Kammer 26 des Steuerzylinders 20 und damit gleich dem Gegendruck im Ausgabezylinder 10 ist.By means of a linear regulator 52, the connection 2 with the second chamber 28 of the control cylinder 20, the control signal connection 4 with the second line 42 and its connection 1 via a check valve 54 and the shut-off valve 34 with the Compressed air source 32 is connected and its connection 3 free is, the pressure in the second chamber 28 of the control cylinder 20 regulated so that it is equal to the pressure in the first Chamber 26 of the control cylinder 20 and thus equal to the back pressure in the output cylinder 10.

Für den Betrieb wird das erste Absperrventil 34 in seine Durchleitungsstellung gebracht. Der Schieber 36 wird so eingestellt, daß eine Verbindung zwischen den Anschlüssen 1 und 2 besteht, so daß sich der Gegendruck über den Gegendruck-Regler 46 und das zweite Absperrventil 44, das dazu in seiner Durchleitungsstellung steht, aufbauen kann, z.B. auf 2 bar. In dieser Stellung wird die erste Kammer 16 des Ausgabezylinders 10 über ein zur Drossel 38 parallel liegendes Rückschlagventil 56 und die Verbindung zwischen den Anschlüssen 4 und 3 des Schiebers 36 entlüftet. Die beiden Kolben 12, 22 fahren dadurch in ihre Ausgangsposition zurück, in der die Volumina der ersten Kammern 16, 26 minimal und die der zweiten Kammern 18, 28 maximal sind. Zum Ausfahren des Ausgabekolbens 12 wird der Schieber 36 in die Stellung gebracht, in der die Anschlüsse 1 und 4 verbunden sind, so daß Druckluft von beispielsweise 4 bar in die erste Kammer 16 des Ausgabezylinders 10 geleitet wird. Der Ausgabekolben 12 fährt dadurch aus (in Fig. 1 nach links) und schleppt in Folge der Kopplung 30 den Steuerkolben 22 mit. Das Volumen der zweiten Kammer 18 des Ausgabezylinders 10 verringert sich dadurch. Gleichzeitig vergrößert sich dadurch das Volumen der ersten Kammer 26 des Steuerzylinders 20. Da der Durchmesser des Steuerzylinders 20 größer ist als der des Ausgabezylinders 10, vergrößert sich das Gesamtvolumen dieser beiden über die zweite Leitung 42 verbundenen Kammern 18, 26, so daß der Gegendruck sinkt. Mit fortschreitender Ausfahrbewegung des Ausgabekolbens 12 steigt dadurch die von ihm erzeugte Kraft im Beispielsfall entsprechend einem resultierenden Druckanstieg von 2 auf 4 bar.For operation, the first shut-off valve 34 is in its Brought forward position. The slide 36 is set so that a connection between the connections 1 and 2 there is, so that the back pressure on the back pressure regulator 46 and the second shut-off valve 44, which is in its pass-through position stands, can build, e.g. to 2 bar. In this position becomes the first chamber 16 of the dispensing cylinder 10 via a check valve lying parallel to the throttle 38 56 and the connection between the terminals 4 and 3 of the Slider 36 vented. The two pistons 12, 22 thereby move back to their starting position, in which the volumes of the first chambers 16, 26 minimal and those of the second chambers 18, 28 are maximum. To extend the discharge piston 12 Slide 36 brought into the position in which the connections 1 and 4 are connected so that compressed air of, for example, 4th bar passed into the first chamber 16 of the dispensing cylinder 10 becomes. The discharge piston 12 thereby extends (in FIG. 1) left) and drags the control piston as a result of the coupling 30 22 with. The volume of the second chamber 18 of the dispensing cylinder 10 is reduced. At the same time, this increases the volume of the first chamber 26 of the control cylinder 20. Since the diameter of the control cylinder 20 is larger than that the output cylinder 10, the total volume increases of these two chambers connected via the second line 42 18, 26 so that the back pressure drops. With progressive extension movement the output piston 12 thereby increases that of it generated force in the example according to a resulting Pressure increase from 2 to 4 bar.

Da über den Linearregler 52 der Druck in beiden Kammern 26, 28 des Steuerzylinders gleichgehalten wird, erzeugt dieser Zylinder nahezu keine Kraft. Dadurch, daß sich die zweite Kammer 28 auf der Seite der Kolbenstange 24 befindet ist die druckbeaufschlagte Fläche auf dieser Seite des Steuerkolbens 22 etwas kleiner, so daß der Steuerkolben 22 eine geringe in Ausfahrrichtung zeigende Kraft erzeugt. Diese Kraft dient jedoch lediglich der Überwindung der Reibung in beiden Zylindern 10, 20 beim Ausfahren der Kolbenstangen.Since the pressure in both chambers 26, 28 of the control cylinder is kept equal, this cylinder produces almost no power. The fact that the second chamber 28th on the side of the piston rod 24 is the pressurized Surface on this side of the spool 22 somewhat smaller, so that the control piston 22 a little in the extension direction generating force. However, this force only serves overcoming the friction in both cylinders 10, 20 when extending the piston rods.

Zum Entlüften der Vorrichtung wird das erste Absperrventil 34 in seine Sperrstellung gebracht, der Schieber 36 in die Stellung, in der die Anschlüsse 1 und 2 bzw. 3 und 4 verbunden sind, so daß die erste Leitung 40 entlüftet wird. Die zweite Leitung 42 wird dabei belüftet, die Kolbenstangen 14 und 24 eingefahren und die Kammern 18, 26 und 28 mit dem geregelten Anfangswert des Gegendrucks, z.B. 2 bar gefüllt. Wird bei Bedarf das zweite Absperrventil 44 in seine Entlüftungsstellung gebracht, wird die zweite Leitung 42 entlüftet.The first shut-off valve 34 is used to vent the device brought into its locked position, the slide 36 in the position, in which the connections 1 and 2 or 3 and 4 are connected are, so that the first line 40 is vented. The second Line 42 is aerated, the piston rods 14 and 24th retracted and the chambers 18, 26 and 28 with the regulated Initial value of the back pressure, e.g. 2 bar filled. Will if necessary the second shut-off valve 44 in its venting position brought, the second line 42 is vented.

Claims (6)

  1. Method for the path-dependent control of the force generated by a first piston (12), the first piston (12) travelling in a first cylinder (10) that is divided into a first and second chamber (16, 18) by the first piston (12), a pressure fluid (32) being conducted into the first chamber (16), a second cylinder (20) being provided in which a second piston (22) is travelling and that is also divided by the second piston (22) into a first and a second chamber (26, 28), the two pistons (12, 22) being coupled (30) so that the second piston (22) is pulled along by the first piston (12), the pistons (12, 22) move synchronously and a reduction of the second chamber (18) of the first cylinder (10) is accompanied by an enlargement of the first chamber (26) of the second cylinder (20), and the second chamber (18) of the first cylinder (10) being connected to the first chamber (26) of the second cylinder (20) so that the same pressure prevails in both chambers (18 and 26), characterized by
    the pressure in the second chamber (28) of the second cylinder (20) being regulated such that it is always equal to the counterpressure in the first chamber (26) of the second cylinder (20) and the second chamber (18) of the first cylinder (10); and
    the arrangement being such that the counterpressure falls and the force generated by the first cylinder (10) increases continuously in a path-dependent manner during an extension movement of the first piston (12) in case the diameter of the second cylinder (20) is greater than that of the first cylinder (10) and, due to that, the overall volume of the second chamber (18) of the first cylinder (10) and the first chamber (26) of the second cylinder (20) increases when the first piston (12) performs an extension movement, and that the force generated by the first cylinder (10) falls continuously during an extension movement in case the second cylinder (20) has a smaller diameter.
  2. Method according to claim 1, characterized in that the initial value of the counterpressure in the second chamber (18) of the first cylinder (10) is adjustable.
  3. Method according to claim 1 or 2, characterized in that the diameter of the second cylinder (20) is greater than that of the first cylinder (10) so that the counterpressure sinks when the first piston (12) performs an extension movement and in that the force generated by the piston (12) thereby increases path-dependent linearly.
  4. Apparatus for carrying out the method according to any one of claims 1 to 3, comprising a source (32) for a pressure fluid, a first cylinder (10) in which a first piston (12) is travelling and which is divided into a first and second chamber (16, 18) by the first piston (12), the pressure fluid (32) being conducted into the first chamber (16), a second cylinder (20) in which a second piston (22) is travelling and which is also divided by the second piston (22) into a first and second chamber (26, 28), a line (42) that connects the second chamber (18) of the first cylinder (10) to the first chamber (26) of the second cylinder (20), and a coupling (30) of the two pistons (12, 22) so that the second piston (22) is pulled along by the first piston (12), the pistons (12, 22) move synchronously and a reduction of the second chamber (18) of the first cylinder (10) is accompanied by an enlargement of the first chamber (26) of the second cylinder (20); characterized
    by a linear regulator (52) which regulates the pressure in the second chamber (28) of the second cylinder (20) such that it is always equal to the counterpressure in the first chamber (26) of the second cylinder (20) and the second chamber (18) of the first cylinder (10),
    the arrangement being such that the counterpressure falls and the force generated by the first cylinder (10) increases continuously in a path-dependent manner during an extension movement of the first piston (12) in case the diameter of the second cylinder (20) is greater than that of the first cylinder (10) and, due to that, the overall volume of the second chamber (18) of the first cylinder (10) and the first chamber (26) of the second cylinder (20) increases when the first piston (12) performs an extension movement, and that the force generated by the first cylinder (10) falls continuously during an extension movement in case the second cylinder (20) has a smaller diameter.
  5. Apparatus according to claim 4, characterized by the initial value of the counterpressure in the second chamber (18) of the first cylinder (10) being adjustable.
  6. Apparatus according to claim 4 or 7, characterized in that the diameter of the second cylinder (20) is greater than that of the first cylinder (10) so that the counterpressure sinks when the first piston (12) performs an extension movement and in that the force generated by the piston (12) thereby increases path-dependent linearly.
EP99948561A 1998-05-06 1999-05-06 Device for the stroke-dependent adjustment of the force generated by a piston Expired - Lifetime EP1076778B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE29808049U 1998-05-06
DE29808049U DE29808049U1 (en) 1998-05-06 1998-05-06 Device for the path-dependent control of the force generated by a piston
PCT/EP1999/003111 WO1999057443A1 (en) 1998-05-06 1999-05-06 Device for the stroke-dependent adjustment of the force generated by a piston

Publications (2)

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EP1076778A1 EP1076778A1 (en) 2001-02-21
EP1076778B1 true EP1076778B1 (en) 2003-02-26

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US (1) US6397726B1 (en)
EP (1) EP1076778B1 (en)
AU (1) AU4258499A (en)
DE (2) DE29808049U1 (en)
WO (1) WO1999057443A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105179356A (en) * 2015-08-27 2015-12-23 徐州重型机械有限公司 Auxiliary boom control valve, auxiliary boom hydraulic control system and crane

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DE19959569A1 (en) * 1999-12-10 2001-06-13 Mannesmann Rexroth Ag Hydraulic control arrangement for controlling two differently high pressures on a hydraulic consumer, in particular of two differently high clamping pressures for holding a workpiece in a machine tool
NL1020593C2 (en) * 2002-05-14 2003-11-17 Lely Entpr Ag Operating method for actuator cylinder, especially hydraulic cylinder in agricultural machine, involves automatically controlling amount of fluid between piston and valve

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Publication number Priority date Publication date Assignee Title
GB1110872A (en) 1964-07-25 1968-04-24 Williams Holdings Ltd Edward Hydraulic drives
US4255930A (en) 1979-08-10 1981-03-17 Natalie Adam J Power device
DE4234535A1 (en) 1992-10-14 1994-04-21 Abb Henschel Waggon Union Running gear for rail vehicles
DE4441098C2 (en) 1994-11-18 1996-09-26 Porsche Ag Actuator supported by external power

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105179356A (en) * 2015-08-27 2015-12-23 徐州重型机械有限公司 Auxiliary boom control valve, auxiliary boom hydraulic control system and crane

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AU4258499A (en) 1999-11-23
DE29808049U1 (en) 1998-07-30
EP1076778A1 (en) 2001-02-21
US6397726B1 (en) 2002-06-04
WO1999057443B1 (en) 2000-01-20
WO1999057443A1 (en) 1999-11-11
DE59904374D1 (en) 2003-04-03

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