EP1076778A1 - 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

Info

Publication number
EP1076778A1
EP1076778A1 EP99948561A EP99948561A EP1076778A1 EP 1076778 A1 EP1076778 A1 EP 1076778A1 EP 99948561 A EP99948561 A EP 99948561A EP 99948561 A EP99948561 A EP 99948561A EP 1076778 A1 EP1076778 A1 EP 1076778A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
chamber
piston
pressure
back pressure
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.)
Granted
Application number
EP99948561A
Other languages
German (de)
French (fr)
Other versions
EP1076778B1 (en
Inventor
Rolf-Günter LITZEL
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.)
Henkel Loctite Deutschland GmbH
Original Assignee
Henkel Loctite Deutschland GmbH
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 Henkel Loctite Deutschland GmbH filed Critical Henkel Loctite Deutschland GmbH
Publication of EP1076778A1 publication Critical patent/EP1076778A1/en
Application granted granted Critical
Publication of EP1076778B1 publication Critical patent/EP1076778B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B11/04—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 a device for path-dependent control of the force generated by a first piston, which runs in a first cylinder, is divided into a first and a second chamber by the first piston, a pressure fluid being conducted into the first chamber.
  • a second cylinder is also provided, in which a second piston runs and which is likewise divided into a first and a second chamber by the second piston.
  • the invention has for its object to control the force generated by a piston in a simple manner as a function of the travel path of the piston. According to the invention, this object is achieved in that the two pistons are coupled, so that the second piston is entrained by the first piston, and in that the second chamber of the first cylinder is connected to the first chamber of the second cylinder, so that in both chambers there is the same pressure.
  • the fluid When the first piston extends, the fluid is displaced from the second chamber of the first cylinder into the first chamber of the second cylinder.
  • the two pistons By coupling the two pistons, they move synchronously, so that the extension of the second chamber of the first cylinder is accompanied by an enlargement of the first chamber of the second cylinder during an extension movement. If the diameter of the second cylinder is now made larger than that of the first cylinder, the total volume of the second chamber of the first cylinder and the first chamber of the second cylinder increases when the first piston extends, so that the back pressure decreases and that of force generated in the first cylinder increases continuously as the first piston moves out.
  • the force generated by the first cylinder decreases continuously during an extension movement.
  • the force generated by the first piston is a largely continuous and linear function of its extension path.
  • the pressure in the second chamber of the second cylinder is controlled so 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 standard cylinders with one piston and the two chambers of each cylinder have the same diameter.
  • the coupling of the two pistons is expediently mechanical and positive.
  • the initial value of the back pressure of the first cylinder can preferably be set, for which purpose its second chamber can be connected to the source of pressure fluid via a regulator, on which the starting value of the back pressure can be set.
  • the compressed fluid is preferably a compressed gas, in particular compressed air, the source of the compressed fluid, the compressed gas or the compressed air being the only energy source of the system.
  • the invention is applicable, for example, to a device for dispensing viscous masses contained in aluminum cartridges with a wavy surface.
  • the viscous mass can be, for example, an adhesive.
  • the cartridge When the mass is dispensed, the cartridge is compressed. The more force the cartridge is pressed, the greater the force required for this.
  • the cartridge In order to output the viscous mass with a volume flow that is constant over time, it is therefore necessary to control the force exerted on the cartridge as a function of the remaining size of the cartridge, and to let it increase.
  • the cartridge can be inserted into an output device in which it is acted upon by the first piston of the device according to the invention.
  • Fig. 1 shows a circuit diagram of the pressure control.
  • a first or output cylinder 10 and a second or control cylinder 20 are arranged parallel to one another.
  • a first or output piston 12 with a piston rod 14 runs in the output cylinder 10 and divides the output cylinder 10 into a first chamber 16 and a second chamber 18, the second chamber 18 being on the side of the piston rod 14.
  • a second or control piston 22 with a piston rod 24 runs in the control cylinder 20 and divides the control cylinder 20 into a first chamber 26 and a second chamber 28, the second chamber 28 being on the side of the piston rod 24.
  • the two piston rods 14, 24 are mechanically positively coupled outside the cylinders 10, 20 by an indicated connection 30, so that they can only move synchronously.
  • the compressed fluid is compressed air, which is fed from a compressed air source 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 into the first chamber 16 of the output cylinder 10.
  • the extension speed of the discharge piston 12 can be adjusted by means of the throttle 38.
  • a parallel 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 their blocking position in FIG. 1. To pass the pressure fluid, both are moved so that there is a connection between the connections 1 and 2 or 1 and 4.
  • the second chamber 18 of the output cylinder 10 is connected to the first chamber 26 of the control cylinder 20 via a second line 42.
  • the initial value of the back pressure prevailing in these two chambers 18, 26 and the second line 42 can be set via a second shut-off valve 44 and a back pressure regulator 46, which is connected to the connection 2 of the slide 36 by means of a third line 48 and which can be connected to the compressed air source 32 by appropriate adjustment of the slide 36.
  • a third line 48 there is a check valve 50 between the back pressure regulator 46 and the connection 2 of the slide 36, which only allows compressed air from the compressed air source 32 to the back pressure regulator 46.
  • the pressure in the second chamber 28 of the control cylinder 20 is 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 brought into its pass-through position.
  • the slide 36 is set so that there is a connection between the connections 1 and 2, so that the back pressure can build up via the back pressure regulator 46 and the second shut-off valve 44, which is in its passage position, for example to 2 bar.
  • the first chamber 16 of the output cylinder 10 is vented via a check valve 56 lying parallel to the throttle 38 and the connection between the connections 4 and 3 of the slide 36.
  • the two pistons 12, 22 return to their starting position, in which the volumes of the first chambers 16, 26 are minimal and those of the second chambers 18, 28 are maximum.
  • the slide 36 is brought into the position in which the connections 1 and 4 are connected, so that compressed air of, for example, 4 bar is passed into the first chamber 16 of the dispensing cylinder 10.
  • the output piston 12 thereby extends (to the left in FIG. 1) and, as a result of the coupling 30, also carries the control piston 22 along.
  • the volume of the second chamber 18 of the dispensing cylinder 10 is thereby reduced.
  • 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 of the output cylinder 10, the total volume of these two chambers 18, 26 connected via the second line 42 increases, so that the back pressure decreases .
  • the extension piston 12 moves outward, it increases generated force in the example corresponding to a resulting pressure increase from 2 to 4 bar.
  • the first shut-off valve 34 is brought into its blocking position, the slide 36 into the position in which the connections 1 and 2 or 3 and 4 are connected, so that the first line 40 is vented.
  • the second line 42 is ventilated, the piston rods 14 and 24 retracted and the chambers 18, 26 and 28 with the regulated initial value of the back pressure, e.g. 2 bar filled. If the second shut-off valve 44 is brought into its venting position as required, the second line 42 is vented.

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)

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

Vorrichtung zur wegabhängigen Steuerung der von einem Kolben erzeugten Kraft Device for the path-dependent control of the force generated by a piston
Beschreibungdescription
Die Erfindung betrifft ein Verfahren und eine Vorrichtung zum wegabhängigen Steuern der von einem ersten Kolben erzeugten Kraft, der in einem ersten Zylinder läuft, durch den ersten Kolben in eine erste und eine zweite Kammer unterteilt wird wobei ein Druckfiuid 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 a device for path-dependent control of the force generated by a first piston, which runs in a first cylinder, is divided into a first and a second chamber by the first piston, a pressure fluid being conducted into the first chamber. A second cylinder is also provided, in which a second piston runs and which is likewise divided into a first and a second chamber by the second piston.
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 Sys- tem 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 Fremdkra tversorgung zu verschieben. Bei fehlender Fremdkraftversorgung entfällt diese Gegenkraft und der Kolben wird verschoben, wodurch die zweite Kammer verkleinert wird. Der dadurch am Ein- speisungspunkt der Fremdkraft aufgebaute Druck wird in die zweite Kammer des Nehmerzylinders geleitet und unterstützt diesen dadurch.From DE-A-44 41 098 a similarly constructed system is known which acts as a power-assisted actuating device. The fluid pressure is generated by a master cylinder and fed to the first chamber of a slave cylinder and the first chamber of a cylinder of a translation unit. The system works hydraulically and the slave cylinder and the cylinder of the transmission unit are graduated, with the second chambers each having the larger diameter. With existing external power supply, the translation unit is held in the rest position, since the pressure generated by the master cylinder is not sufficient to move the piston of the translation unit against the pressure of the external power supply acting in its second chamber. If there is no external power supply, this counterforce is eliminated and the piston is displaced, reducing the size of the second chamber. The pressure built up at the feed point of the external force is directed into the second chamber of the slave cylinder and supports it.
Der Erfindung liegt die Aufgabe zugrunde die von einem Kolben erzeugte Kraft auf möglichst einfache Weise in Abhängigkeit von dem Fahrweg des Kolbens zu steuern. Erfindungsgemäß wird diese Aufgabe dadurch gelöst, daß die beiden Kolben gekoppelt sind, so daß der zweite Kolben von dem ersten Kolben mitgeschleppt wird, und daß die zweite Kammer des ersten Zylinders mit der ersten Kammer des zweiten Zylinders verbunden ist, so daß in beiden Kammern der gleiche Druck herrscht .The invention has for its object to control the force generated by a piston in a simple manner as a function of the travel path of the piston. According to the invention, this object is achieved in that the two pistons are coupled, so that the second piston is entrained by the first piston, and in that the second chamber of the first cylinder is connected to the first chamber of the second cylinder, so that in both chambers there is the same pressure.
Bei einer Ausfahrbewegung des ersten Kolbens wird das Fluid aus der zweiten Kammer des ersten Zylinders in die erste Kam- mer 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 Zy~ linders 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 Aus- fahren des ersten Kolbens wegabhängig kontinuierlich zunimmt.When the first piston extends, the fluid is displaced from the second chamber of the first cylinder into the first chamber of the second cylinder. By coupling the two pistons, they move synchronously, so that the extension of the second chamber of the first cylinder is accompanied by an enlargement of the first chamber of the second cylinder during an extension movement. If the diameter of the second cylinder is now made larger than that of the first cylinder, the total volume of the second chamber of the first cylinder and the first chamber of the second cylinder increases when the first piston extends, so that the back pressure decreases and that of force generated in the first cylinder increases continuously as the first piston moves out.
Hat der zweite Zylinder dagegen einen kleineren Durchmesser, so sinkt die von dem ersten Zylinder erzeugte Kraft bei einer Ausfahrbewegung kontinuierlich.If, on the other hand, the second cylinder has a smaller diameter, the force generated by the first cylinder decreases continuously during an extension movement.
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 a largely continuous and linear function of its extension path.
Vorzugsweise wird der Druck in der zweiten Kammer des zweiten Zylinders 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.Preferably, the pressure in the second chamber of the second cylinder is controlled so 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. 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 Druckfiuid verbindbar ist.The two cylinder / piston units can be standard cylinders with one piston and the two chambers of each cylinder have the same diameter. The coupling of the two pistons is expediently mechanical and positive. The initial value of the back pressure of the first cylinder can preferably be set, for which purpose its second chamber can be connected to the source of pressure fluid via a regulator, on which the starting value of the back pressure can be set.
Das Druckfiuid ist vorzugsweise ein Druckgas, insbesonder Druckluft, wobei die Quelle für das Druckfiuid, das Druckgas oder die Druckluft die einzige Energiequelle des Systems ist.The compressed fluid is preferably a compressed gas, in particular compressed air, the source of the compressed fluid, the compressed gas or the compressed air being the only energy source of 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 anstei- gen 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 contained in aluminum cartridges with a wavy surface. The viscous mass can be, for example, an adhesive. When the mass is dispensed, the cartridge is compressed. The more force the cartridge is pressed, the greater the force required for this. In order to output the viscous mass with a volume flow that is constant over time, it is therefore necessary to control the force exerted on the cartridge as a function of the remaining size of the cartridge, and to let it increase. For this purpose, the cartridge can be inserted into an output device in which it is acted upon by the first piston of the device according to the invention.
Ein Ausführungsbeispiel der Erfindung wird nachfolgend anhand der Zeichnung erläutert, wobeiAn embodiment of the invention is explained below with reference to the drawing, wherein
Fig. 1 ein Schaltbild der Drucksteuerung zeigt.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 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.In the exemplary embodiment shown, a first or output cylinder 10 and a second or control cylinder 20 are arranged parallel to one another. A first or output piston 12 with a piston rod 14 runs in the output cylinder 10 and divides the output cylinder 10 into a first chamber 16 and a second chamber 18, the second chamber 18 being on the side of the piston rod 14. In a corresponding manner, a second or control piston 22 with a piston rod 24 runs in the control cylinder 20 and divides the control cylinder 20 into a first chamber 26 and a second chamber 28, the second chamber 28 being on the side of the piston rod 24.
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 mechanically positively coupled outside the cylinders 10, 20 by an indicated connection 30, so that they can only move synchronously.
Als Druckfiuid 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 ver- bunden 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 Gegen- druck-Regler 46 durchläßt. 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.The compressed fluid is compressed air, which is fed from a compressed air source 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 into the first chamber 16 of the output cylinder 10. The extension speed of the discharge piston 12 can be adjusted by means of the throttle 38. A parallel 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 their blocking position in FIG. 1. To pass the pressure fluid, both are moved so that there is a connection between the connections 1 and 2 or 1 and 4. The second chamber 18 of the output cylinder 10 is connected to the first chamber 26 of the control cylinder 20 via a second line 42. The initial value of the back pressure prevailing in these two chambers 18, 26 and the second line 42 can be set via a second shut-off valve 44 and a back pressure regulator 46, which is connected to the connection 2 of the slide 36 by means of a third line 48 and which can be connected to the compressed air source 32 by appropriate adjustment of the slide 36. In the third line 48 there is a check valve 50 between the back pressure regulator 46 and the connection 2 of the slide 36, which only allows compressed air from the compressed air source 32 to the back pressure regulator 46. 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 the connection 1 via a check valve 54 and the shut-off valve 34 with the compressed air source 32 and the connection 3 is free, the pressure in the second chamber 28 of the control cylinder 20 is 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 brought into its pass-through position. The slide 36 is set so that there is a connection between the connections 1 and 2, so that the back pressure can build up via the back pressure regulator 46 and the second shut-off valve 44, which is in its passage position, for example to 2 bar. In this position, the first chamber 16 of the output cylinder 10 is vented via a check valve 56 lying parallel to the throttle 38 and the connection between the connections 4 and 3 of the slide 36. As a result, the two pistons 12, 22 return to their starting position, in which the volumes of the first chambers 16, 26 are minimal and those of the second chambers 18, 28 are maximum. To extend the dispensing piston 12, the slide 36 is brought into the position in which the connections 1 and 4 are connected, so that compressed air of, for example, 4 bar is passed into the first chamber 16 of the dispensing cylinder 10. The output piston 12 thereby extends (to the left in FIG. 1) and, as a result of the coupling 30, also carries the control piston 22 along. The volume of the second chamber 18 of the dispensing cylinder 10 is thereby 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 of the output cylinder 10, the total volume of these two chambers 18, 26 connected via the second line 42 increases, so that the back pressure decreases . As the extension piston 12 moves outward, it increases generated force in the example corresponding 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 Ausfahr- richtung 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 the same via the linear regulator 52, this cylinder generates almost no force. Because the second chamber 28 is located on the side of the piston rod 24, the area under pressure on this side of the control piston 22 is somewhat smaller, so that the control piston 22 generates a small force pointing in the extension direction. However, this force only serves to overcome the friction in both cylinders 10, 20 when the piston rods are extended.
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. To vent the device, the first shut-off valve 34 is brought into its blocking position, the slide 36 into the position in which the connections 1 and 2 or 3 and 4 are connected, so that the first line 40 is vented. The second line 42 is ventilated, the piston rods 14 and 24 retracted and the chambers 18, 26 and 28 with the regulated initial value of the back pressure, e.g. 2 bar filled. If the second shut-off valve 44 is brought into its venting position as required, the second line 42 is vented.

Claims

Patentansprüche claims
1. Verfahren zur wegabhängigen Steuerung der von einem ersten Kolben (12) erzeugten Kraft, wobei der erste Kolben (12) in einem ersten Zylinder (10) läuft, der durch den ersten Kolben (12) in eine erste und eine zweite Kammer (16, 18) unterteilt wird, und ein Druckfiuid (32) in die erste Kammer (16) geleitet wird, wobei ein zweiter Zylinder (20) vorgesehen ist, in dem ein zweiter Kolben (22) läuft und der durch den zweiten Kolben (22) ebenfalls in eine erste und eine zweite Kammer (26, 28) unterteilt wird, dadurch gekennzeichnet , daß die beiden Kolben (12, 22) gekoppelt (30) sind, so daß der zweite Kolben (22) von dem ersten Kolben (12) mitgeschleppt wird, und daß die zweite Kammer (18) des ersten Zylinders (10) mit der ersten Kammer (26) des zweiten Zylinders (20) verbunden ist, so daß in beiden Kammern (18 und 26) der gleiche Druck herrscht.1. A method for path-dependent control of the force generated by a first piston (12), the first piston (12) running in a first cylinder (10) which flows through the first piston (12) into a first and a second chamber (16 , 18) and a pressure fluid (32) is fed into the first chamber (16), a second cylinder (20) being provided, in which a second piston (22) runs and which passes through the second piston (22) is also divided into a first and a second chamber (26, 28), characterized in that the two pistons (12, 22) are coupled (30) so that the second piston (22) is entrained by the first piston (12) and that the second chamber (18) of the first cylinder (10) is connected to the first chamber (26) of the second cylinder (20) so that the same pressure prevails in both chambers (18 and 26).
2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß der Druck in der zweiten Kammer (28) des zweiten Zylinders2. The method according to claim 1, characterized in that the pressure in the second chamber (28) of the second cylinder
(20) so geregelt wird, daß er stets gleich dem Gegendruck in der ersten Kammer (26) des zweiten Zylinders (20) und der zweiten Kammer (18) des ersten Zylinders (10) ist.(20) is regulated so 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).
3. Verfahren nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Anfangswert des Gegendrucks in der zweiten Kammer (18) des ersten Zylinders (10) einstellbar ist.3. The method according to claim 1 or 2, characterized in that the initial value of the back pressure in the second chamber (18) of the first cylinder (10) is adjustable.
4. Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Durchmesser des zweiten Zylinders (20) größer ist als der des ersten Zylinders (10) , so daß der Gegendruck bei einer Ausfahrbewegung des ersten Kolbens (12) absinkt und dadurch die von dem ersten Kolben (12) erzeugte Kraft wegabhängig linear ansteigt. 4. The method according to any one of claims 1 to 3, characterized in that the diameter of the second cylinder (20) is larger than that of the first cylinder (10), so that the back pressure drops during an extension movement of the first piston (12) and thereby the force generated by the first piston (12) increases linearly depending on the path.
. Vorrichtung zur Ausführung des Verfahrens nach einem der Ansprüche 1 bis 4, mit einer Quelle (32) für ein Druckfiuid, mit einem ersten Zylinder (10) , in dem ein erster Kolben (12) läuft und der durch den ersten Kolben (12) in eine erste und eine zweite Kammer (16, 18) unterteilt wird, wobei das Druckfiuid (32) in die erste Kammer (16) geleitet wird, und mit einem zweiten Zylinder (20) , in dem ein zweiter Kolben (22) läuft und der durch den zweiten Kolben (22) ebenfalls in eine erste und eine zweite Kammer (26, 28) unterteilt wird, und mit einer Leitung (42), die die zweite Kammer (18) des ersten Zylinders (10) mit der ersten Kammer (26) des zweiten Zylinders (20) verbindet, gekennzeichnet durch eine Kopplung (30) der beiden Kolben (12, 22), so daß der zweite Kolben (22) von dem ersten Kolben. Device for carrying out the method according to one of Claims 1 to 4, with a source (32) for a pressure fluid, with a first cylinder (10) in which a first piston (12) runs and which passes through the first piston (12) dividing a first and a second chamber (16, 18), the pressure fluid (32) being fed into the first chamber (16), and with a second cylinder (20) in which a second piston (22) runs and the is also divided into a first and a second chamber (26, 28) by the second piston (22), and with a line (42) which connects the second chamber (18) of the first cylinder (10) with the first chamber (26 ) of the second cylinder (20), characterized by a coupling (30) of the two pistons (12, 22) so that the second piston (22) from the first piston
(12) mitgeschleppt wird und durch eine Leitung (42) , die die zweite Kammer (18) des ersten Zylinders (10) mit der ersten Kammer (26) des zweiten Zylinders (20) verbindet.(12) is entrained and through a line (42) which connects the second chamber (18) of the first cylinder (10) with the first chamber (26) of the second cylinder (20).
6. Vorrichtung nach Anspruch 5, gekennzeichnet durch einen Linear-Regler (52) , der den Druck in der zweiten Kammer6. The device according to claim 5, characterized by a linear regulator (52), the pressure in the second chamber
(28) des zweiten Zylinders (20) so regelt, daß er stets gleich dem Gegendruck in der ersten Kammer (26) des zweiten Zylinders (20) und der zweiten Kammer (18) des ersten Zylinders (10) ist.(28) of the second cylinder (20) regulates so 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).
7. Vorrichtung nach Anspruch 5 oder 6 , gekennzeichnet durch einen Gegendruck-Regler (46), mit dem der Anfangswert des Gegendrucks in der zweiten Kammer (18) des ersten Zylinders (10) einstellbar ist.7. The device according to claim 5 or 6, characterized by a back pressure regulator (46) with which the initial value of the back pressure in the second chamber (18) of the first cylinder (10) is adjustable.
8. Vorrichtung nach einem der Ansprüche 5 bis 7, dadurch gekennzeichnet, daß der Durchmesser des zweiten Zylinders (20) größer ist als der des ersten Zylinders (10) , so daß der Gegendruck bei einer Ausfahrbewegung des ersten Kol- bens (12) absinkt und dadurch die von dem ersten Kolben (12) erzeugte Kraft wegabhängig linear ansteigt. 8. Device according to one of claims 5 to 7, characterized in that the diameter of the second cylinder (20) is larger than that of the first cylinder (10), so that the back pressure upon an extension movement of the first piston bens (12) decreases and thereby the force generated by the first piston (12) increases linearly depending on the path.
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)

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

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

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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
CN105179356B (en) * 2015-08-27 2017-05-24 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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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

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DE59904374D1 (en) 2003-04-03
US6397726B1 (en) 2002-06-04
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WO1999057443A1 (en) 1999-11-11
DE29808049U1 (en) 1998-07-30
AU4258499A (en) 1999-11-23

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