EP0164334A1 - Hydraulic cylinder with force multiplication - Google Patents

Hydraulic cylinder with force multiplication Download PDF

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Publication number
EP0164334A1
EP0164334A1 EP85890103A EP85890103A EP0164334A1 EP 0164334 A1 EP0164334 A1 EP 0164334A1 EP 85890103 A EP85890103 A EP 85890103A EP 85890103 A EP85890103 A EP 85890103A EP 0164334 A1 EP0164334 A1 EP 0164334A1
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EP
European Patent Office
Prior art keywords
piston
cylinder
pistons
chamber
shut
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
EP85890103A
Other languages
German (de)
French (fr)
Other versions
EP0164334B1 (en
Inventor
Dionizy Simson
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.)
Cessione hoerbiger Ventilwerke AG
Original Assignee
ENFO Grundlagen Forschungs AG
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Publication date
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Priority to AT85890103T priority Critical patent/ATE36038T1/en
Publication of EP0164334A1 publication Critical patent/EP0164334A1/en
Application granted granted Critical
Publication of EP0164334B1 publication Critical patent/EP0164334B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high 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
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/428—Flow control characterised by the type of actuation actuated by fluid 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
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the present invention relates to a hydraulic cylinder internal pressure transmission for force multiplication.
  • Hydraulic cylinders are needed in many places where a fast stroke with little force and then a short, slow stroke with great force are important. Hydraulic cylinders with hydraulic transmission are used in fixture construction, manufacturing machines and presses, in civil engineering for piling and pulling devices. Such cylinders are more compact and lighter than single-stage hydraulic cylinders with the same effective force.
  • the object of the present invention is to eliminate these disadvantages. This is achieved according to the invention by the features of the characterizing part of independent claim "I.
  • a single-stage primary piston 2 and a two-stage secondary piston 3 are arranged in the cylinder 1, a piston rod 4 connected to the primary piston 2 passing through the secondary piston 3.
  • the primary piston 2 has a circumferential groove 5 with a sealing ring 6 provided therein.
  • the secondary piston comprises the parts 7 and 8 which form the two stages and which have a different diameter from one another.
  • a circumferential groove 9 and 10 with seals 11 and 12 provided therein are provided in part 7 and in part 8.
  • a circumferential groove 14 with a seal 15 provided therein is also provided in the bore 13 provided in part 8 of the secondary piston 3 for the passage of the piston rod.
  • the cylinder 1 is closed on the side of the secondary piston 3 by a cylinder cover 16, through which the piston rod 4 is guided.
  • a circumferential groove 18 is provided with a seal 19 attached therein.
  • a first shut-off piston 22 acted upon by a first, weak spring 21 and a second shut-off piston 24 acted upon by a second strong spring 23.
  • Both the first and the second shut-off piston are designed in two stages, each with a part 25 or. 26 with a larger diameter and a part 27 respectively. 28 are provided with a smaller diameter. With parts 27 and 28 with a smaller diameter is a piston rod 29, respectively. 30 connected, each in a chamber 31 opposite the shut-off piston. 32 lead.
  • Opening pistons 33 and 34 are provided in the chambers 31 and 32.
  • a supply line 35 for the pressure medium leads into the chamber 31 in the area between the piston rod 29 and the end face of the opening piston 33, the two chambers 31 and 32 being connected by a line 36.
  • the chamber 37 surrounding the front part 27 of the first shut-off piston 22 is connected via a line 38 to a first pressure chamber 39 between the primary piston and the cylinder wall. From the line 38 leads a branch line 40 into a step chamber 41 between the part 7 of the secondary piston 3 and the inner wall of the cylinder 1. This step chamber 41 is laterally by a shoulder 42 on the outer circumference of the secondary piston 3 and by a shoulder 43 on the inner wall of the Cylinder 1 limited.
  • the chamber surrounding the front part 28 of the second shut-off piston 24 is connected via a line 44 for the pressure medium to a second pressure chamber 45 between the boundary surface 46 of the secondary piston opposite the cylinder cover and the cylinder cover.
  • the chamber 47 between the primary and secondary pistons is connected via a line 48 to the chambers on the right-hand side of the opening pistons 33 and 34 according to the FIG.
  • the pressure medium is conveyed from the unpressurized chamber 47 via the line 48 into a container (not shown).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Servomotors (AREA)
  • Vehicle Body Suspensions (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

A hydraulic cylinder device for power multiplication includes a cylinder (1) containing a single-stage piston (2) having a piston rod (4) and a two-stage secondary piston (3), the piston rod (4) extending through a bore in the secondary piston. The cylinder (1) is closed by a cylinder cover (16) through which the piston rod (4) also extends. Two stop-pistons (22, 24) with different strength springs (21, 23) are located in projection (20) integral with cylinder (1) and opposite the stop-pistons are two opening-pistons (33, 34).

Description

Gegenstand vorliegender Erfindung ist ein hydraulischer Zylinder interner Druckübersetzung zur Kraftmultiplikation.The present invention relates to a hydraulic cylinder internal pressure transmission for force multiplication.

Es werden vielerorts hydraulische Zylinder gebraucht, bei denen es auf einen schnellen Hub mit geringer Kraft und anschliessend einen kurzen, langsamen Hub mit grosser Kraft ankommt. Im Vorrichtungsbau, bei Fertigungsmaschinen und Pressen, im Tiefbau bei Ramm- und Ziehgeräten werden Hydraulikzylinder mit hydraulischer Uebersetzung eingesetzt. Solche Zylinder sind kompakter und leichter als einstufige Hydraulikzylinder mit gleicher Wirkkraft.Hydraulic cylinders are needed in many places where a fast stroke with little force and then a short, slow stroke with great force are important. Hydraulic cylinders with hydraulic transmission are used in fixture construction, manufacturing machines and presses, in civil engineering for piling and pulling devices. Such cylinders are more compact and lighter than single-stage hydraulic cylinders with the same effective force.

Es sind Lösungen bekannt, welche aus zwei Kolben und drei Druckkammern bestehen, und wo die Kolben nacheinander angeordnet sind (GB-PS 16 00 733; GB-PS 1 420 389; US-PS 4 011 724; DE-OS 31 19 307 Al). Diese Bauart verlangt zwischen beiden Kolben eine Trennwand. Die Kolben bewegen sich beim Arbeitsvorgang, z.B. einem Klemmvorgang, in gleicher Richtung. Dies hat zur Folge, daß die Zylinderl1änge um die Trennwandstärke größer sein muß. Sobald der Primärkolben auf seinem Weg keinen Widerstand trifft, gelangt er an den Zylinderdeckel, der übersetzungsvorgang wird eingeleitet und der Deckel wird abgerissen oder rnuß entsprechend starkSolutions are known which consist of two pistons and three pressure chambers and where the pistons are arranged one after the other (GB-PS 16 00 733; GB-PS 1 420 389; US-PS 4 011 724; DE-OS 31 19 307 Al ). This design requires a partition between the two pistons. The pistons move during the working process, e.g. a clamping process in the same direction. The consequence of this is that the cylinder length must be greater by the partition wall thickness. As soon as the primary piston encounters no resistance on its way, it comes to the cylinder cover, the translation process is initiated and the cover is torn off or the nut is strong

ausgelegt werden, was sich als Zuwachs der Abmessungen und des Gewichtes auswirkt.be interpreted, which has an impact on the increase in dimensions and weight.

Aufgabe der vorliegenden Erfindung ist es, diese Nachteile zu beseitigen. Dies wird erfindungsgemäss durch die Merkmale des kennzeichnenden Teiles des unabhängigen Anspruches" I gelöst.The object of the present invention is to eliminate these disadvantages. This is achieved according to the invention by the features of the characterizing part of independent claim "I.

Bevorzugte Ausführungsformen der Erfindung ergeben sich aus den abhängigen Ansprüchen.Preferred embodiments of the invention result from the dependent claims.

Ein Ausführungsbeispiel der Erfindung ergibt sich aus der beiliegenden Zeichnung.An embodiment of the invention results from the accompanying drawing.

Im Zylinder 1 sind ein einstufiger Primärkolben 2 sowie ein zweistufiger Sekundärkolben 3 angeordnet, wobei eine mit dem Primärkolben 2 verbundene Kolbenstange 4 den Sekundärkolben 3 durchsetzt. Der Primärkolben 2 weist eine umlaufende Nut 5 mit einem darin vorgesehenen Dichtungsring 6 auf. Der Sekundärkolben umfasst die die beiden Stufen bildenden Teile 7 und 8, welche einen voneinander verschiedenen Durchmesser aufweisen. Am äusseren Umfang des Sekundärkolbens 3 sind im Teil 7 und im Teil 8 je eine umlaufende Nut 9 und 10 mit darin angebrachten Dichtungen 11 und 12 vorgesehen. In der im Teil 8 des Sekundärkolbens 3 vorgesehenen Bohrung 13 zur Durchführung der Kolbenstange ist ebenfalls eine umlaufende Nut 14 mit einer darin angebrachten Dichtung 15 vorgesehen. Der Zylinder 1 wird auf der Seite des Sekundärkolbens 3 durch einen Zylinderdeckel 16 abgeschlossen, durch welchen die Kolbenstange 4 geführt wird. In der Bohrung 17 des Zylinderdeckels ist eine umlaufende Nut 18 mit einer darin angebrachten Dichtung 19 vorgesehen. Integriert in einem Ansatz 20 am Zylinder sind ein durch eine erste, schwache Feder 21 beaufschlagter erster Absperrkolben 22 sowie ein durch eine zweite, starke Feder 23 beaufschlagter zweiter Absperrkolben 24 vorgesehen. Sowohl der erste als auch der zweite Absperrkolben ist zweistufig ausgebildet, wobei jeweis ein Teil 25 resp. 26 mit grösserem Durchmesser und ein Teil 27 resp. 28 mit kleinerem Durchmesser vorgesehen sind. Mit den Teilen 27 und 28 mit kleinerem Durchmesser ist je eine Kolbenstange 29 resp. 30 verbunden, welche je in eine den Absperrkolben gegenüberliegende Kammer 31 resp. 32 führen. In den Kammern 31 und 32 sind Oeffnungskolben 33 und 34 vorgesehen. Eine Zuleitung 35 für das Druckmedium führt in die Kammer 31 in den Bereich zwischen Kolbenstange 29 und Stirnfläche des Oeffnungskolbens 33, wobei die beiden Kammern 31 und 32 durch eine Leitung 36 verbunden sind. Die den vorderen Teil 27 des ersten Absperrkolbens 22 umgebende Kammer 37 ist über eine Leitung 38 mit einer ersten Druckkammer 39 zwischen Primärkolben und Zylinderwand verbunden. Von der Leitung 38 führt eine Zweigleitung 40 in eine Stufenkammer 41 zwischen dem Teil 7 des Sekundärkolbens 3 und der Innenwandung des Zylinders 1. Diese Stufenkammer 41 wird seitlich durch einen Absatz 42 am äussern Umfang des Sekundärkolbens 3 und durch einen Absatz 43 an der Innenwandung des Zylinders 1 begrenzt. Die den vorderen Teil 28 des zweiten Absperrkolbens 24 umgebende Kammer ist über eine Leitung 44 für das Druckmedium mit einer zweiten Druckkammer 45 zwischen der dem Zylinderdeckel gegenüberliegenden Begrenzungsfläche 46 des Sekundärkolbens und des Zylinderdeckels verbunden. Die Kammer 47 zwischen Primär-und Sekundärkolben ist über eine Leitung 48 mit den Kammern auf der gemäss der Fig. rechten Seite der Oeffnungskolben 33 und 34 verbunden.A single-stage primary piston 2 and a two-stage secondary piston 3 are arranged in the cylinder 1, a piston rod 4 connected to the primary piston 2 passing through the secondary piston 3. The primary piston 2 has a circumferential groove 5 with a sealing ring 6 provided therein. The secondary piston comprises the parts 7 and 8 which form the two stages and which have a different diameter from one another. On the outer circumference of the secondary piston 3, a circumferential groove 9 and 10 with seals 11 and 12 provided therein are provided in part 7 and in part 8. In the bore 13 provided in part 8 of the secondary piston 3 for the passage of the piston rod, a circumferential groove 14 with a seal 15 provided therein is also provided. The cylinder 1 is closed on the side of the secondary piston 3 by a cylinder cover 16, through which the piston rod 4 is guided. In the bore 17 of the cylinder cover, a circumferential groove 18 is provided with a seal 19 attached therein. Integrated in an extension 20 on the cylinder are a first shut-off piston 22 acted upon by a first, weak spring 21 and a second shut-off piston 24 acted upon by a second strong spring 23. Both the first and the second shut-off piston are designed in two stages, each with a part 25 or. 26 with a larger diameter and a part 27 respectively. 28 are provided with a smaller diameter. With parts 27 and 28 with a smaller diameter is a piston rod 29, respectively. 30 connected, each in a chamber 31 opposite the shut-off piston. 32 lead. Opening pistons 33 and 34 are provided in the chambers 31 and 32. A supply line 35 for the pressure medium leads into the chamber 31 in the area between the piston rod 29 and the end face of the opening piston 33, the two chambers 31 and 32 being connected by a line 36. The chamber 37 surrounding the front part 27 of the first shut-off piston 22 is connected via a line 38 to a first pressure chamber 39 between the primary piston and the cylinder wall. From the line 38 leads a branch line 40 into a step chamber 41 between the part 7 of the secondary piston 3 and the inner wall of the cylinder 1. This step chamber 41 is laterally by a shoulder 42 on the outer circumference of the secondary piston 3 and by a shoulder 43 on the inner wall of the Cylinder 1 limited. The chamber surrounding the front part 28 of the second shut-off piston 24 is connected via a line 44 for the pressure medium to a second pressure chamber 45 between the boundary surface 46 of the secondary piston opposite the cylinder cover and the cylinder cover. The chamber 47 between the primary and secondary pistons is connected via a line 48 to the chambers on the right-hand side of the opening pistons 33 and 34 according to the FIG.

Im folgenden wird die Funktion des hydraulischen Zylinders beschrieben:

  • Sobald in der Zuleitung 35 der Druck sich so erhöht, dass der erste Absperrkolben 22, welcher mit der schwächeren Feder 21 beaufschlagt ist, abhebt, fliesst das Druckmedium in die erste Druckkammer 39 hinter dem Primärkolben 2 und bewegt diesen nach vorn. Das geschieht so lange, bis der Primärkolben 2 auf einen Widerstand stösst. In diesem Moment öffnet der zweite Absperrkolben 24, und der erste schliesst. Das Druckmedium fliesst jetzt in die zweite Druckkammer 45 am Zylinderdeckel 16, und die Querschnittfläche 46 mit grösserem Durchmesser des zweistufigen Sekundärkolbens 3 wird mit Druck beaufschlagt. Der Sekundärkolben 3 setzt sich in Bewegung, und dabei wird das sich zwischen den Stufen 42 und 43 des Sekundärkolbens und des Zylinders befindliche Druckmedium aus der Stufenkammer 41 in die erste Druckkammer 39 hinter dem Primärkolben 2 gedrückt. Der Primärkolben 2 mit der Querschnittfläche 43 bewegt sich nach vorn mit einer dem Flächenverhältnis (Fläche 49/Fläche 42) entsprechend reduzierten Geschwindigkeit und erhöhter Kraft. Sobald der gewünschte Druck in der Zuleitung 35 erreicht wird, ist der durch die Kolbenstange 4 ausgeübte Arbeitsvorgang, beispielsweise ein Klemmvorgang, beendet, der zweite Absperrkolben 24 schliesst gleichfalls, und von jetzt an wirken beide Absperrkolben als Sicherheitsventile.
The function of the hydraulic cylinder is described below:
  • As soon as the pressure in the supply line 35 increases so that the first shut-off piston 22, which is acted upon by the weaker spring 21, lifts, the pressure medium flows into the first pressure chamber 39 behind the primary piston 2 and moves it forward. This continues until the primary piston 2 encounters resistance. At this moment, the second shut-off piston 24 opens and the first closes. The pressure medium now flows into the second pressure chamber 45 on the cylinder cover 16, and the cross-sectional area 46 with a larger diameter of the two-stage second intestinal piston 3 is pressurized. The secondary piston 3 starts to move and the pressure medium located between the stages 42 and 43 of the secondary piston and the cylinder is pressed out of the stage chamber 41 into the first pressure chamber 39 behind the primary piston 2. The primary piston 2 with the cross-sectional area 43 moves forward with a reduced speed and increased force corresponding to the area ratio (area 49 / area 42). As soon as the desired pressure in the supply line 35 is reached, the work process carried out by the piston rod 4, for example a clamping process, has ended, the second shut-off piston 24 also closes, and from now on both shut-off pistons act as safety valves.

Bei den beschriebenen Bewegungen des Primär- und Sekundärkolbens wird das Druckmedium aus der drucklosen Kammer 47 über die Leitung 48 in einen nicht dargestellten Behälter befördert.During the described movements of the primary and secondary pistons, the pressure medium is conveyed from the unpressurized chamber 47 via the line 48 into a container (not shown).

Beim Oeffnen wird die Leitung 48 mit Druck beaufschlagt. Beide Oeffnungskolben 33 und 34 entsperren die Absperrkolben 22 und 24, der Primär- und der Sekundärkolben 2 und 3 werden auseinander geschoben und erlangen die Ausgangsstellung. Aus den drucklosen Kammern 39, 41 und 45 gelangt das Druckmedium über die geöffneten Absperrkolben 22 und 24 und die Leitung 35 in den nicht dargestellten Behälter.When opening, line 48 is pressurized. Both Oeffnungskolben 33 and 34 to unlock the A bsperrkolben 22 and 24, the primary and secondary pistons 2 and 3 are pushed apart and acquire the initial position. From the unpressurized chambers 39, 41 and 45, the pressure medium reaches the container (not shown) via the opened shut-off pistons 22 and 24 and the line 35.

Falls der Primärkolben 2 auf seinem Weg nach vorne auf keinen Widerstand trifft, bewegt er sich so lange, bis er die Oeffnung der Leitung 48 in der Kammer 47 zudeckt. Der Sekundärkolben 2 kann sich auch nicht bewegen, da der Abfluss gesperrt ist. Wenn der Schnellhub lang wird, und der Umschaltvorgang kurz vor der Oeffnung der Leitung 48 einsetzt, treffen beide Kolben 2 und 3 aufeinander. In beiden Fällen ergeben sich keine Zylinderschäden, und es müssen keine grossen Kräfte aufgefangen werden.If the primary piston 2 encounters no resistance on its way forward, it moves until it covers the opening of the line 48 in the chamber 47. The secondary piston 2 can also not move because the drain is blocked. When the rapid stroke becomes long and the switching process begins shortly before the opening of line 48, both pistons 2 and 3 meet. In both cases, there is no cylinder damage and no large forces have to be absorbed.

Claims (4)

1. Hydraulischer Zylinder mit Kraftmultiplikation, gekennzeichnet durch einen einstufigen Primärkolben (2) und einen zweistufigen Sekundärkolben (3), wobei die Kolbenstange (4) des Primärkolbens (2) den Sekundärkolben (3) durchsetzt.1. Hydraulic cylinder with force multiplication, characterized by a single-stage primary piston (2) and a two-stage secondary piston (3), the piston rod (4) of the primary piston (2) passing through the secondary piston (3). 2. Zylinder nach Anspruch 1, dadurch gekennzeichnet, daß an der Zylinderinnenwand eine Stufe (42,43) ausgebildet ist, wodurch zwischen Zylinderinnenwand und Zylinderaußenwand des zweistufigen Sekundärkolbens (3) eine Stufenkammer (41) gebildet ist.2. Cylinder according to claim 1, characterized in that a step (42, 43) is formed on the cylinder inner wall, whereby a step chamber (41) is formed between the cylinder inner wall and the cylinder outer wall of the two-stage secondary piston (3). 3. Zylinder nach Anspruch 2, dadurch gekennzeichnet, daß die Stufenkammer (41) mit einem zwischen Primärkolben (2) und Zylinder (1) gebildeten ersten Druckkammer (39) über eine Leitung (38) für ein Druckmedium kommuniziert.3. Cylinder according to claim 2, characterized in that the step chamber (41) communicates with a first pressure chamber (39) formed between primary piston (2) and cylinder (1) via a line (38) for a pressure medium. 4. Zylinder nach Anspruch 3, dadurch gekennzeichnet, daß die Zuführleitung (35) für das Druckmedium über ein erstes Absperrventil (22) mit der ersten Druckkammer (39) und über ein zweites Absperrventil (24) mit einer zwischen Sekundärkolben (3) und Zylinder (1) gebildeten zweiten Druckkammer (45) verbunden ist.4. Cylinder according to claim 3, characterized in that the supply line (35) for the pressure medium via a first shut-off valve (22) with the first pressure chamber (39) and via a second shut-off valve (24) with one between the secondary piston (3) and cylinder (1) formed second pressure chamber (45) is connected.
EP85890103A 1984-05-11 1985-05-03 Hydraulic cylinder with force multiplication Expired EP0164334B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85890103T ATE36038T1 (en) 1984-05-11 1985-05-03 HYDRAULIC CYLINDER WITH MULTIPLE POWER.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2357/84 1984-05-11
CH2357/84A CH665007A5 (en) 1984-05-11 1984-05-11 HYDRAULIC CYLINDER WITH POWER MULTIPLICATION.

Publications (2)

Publication Number Publication Date
EP0164334A1 true EP0164334A1 (en) 1985-12-11
EP0164334B1 EP0164334B1 (en) 1988-07-27

Family

ID=4231904

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85890103A Expired EP0164334B1 (en) 1984-05-11 1985-05-03 Hydraulic cylinder with force multiplication

Country Status (7)

Country Link
US (1) US4620419A (en)
EP (1) EP0164334B1 (en)
JP (1) JPS6136505A (en)
AT (1) ATE36038T1 (en)
CH (1) CH665007A5 (en)
DE (1) DE3564010D1 (en)
ZA (1) ZA853539B (en)

Cited By (5)

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DE3620876A1 (en) * 1986-06-21 1987-12-23 Hehl Karl HYDRAULIC ELEMENT AND DRAWING TOOL ASSEMBLED WITH IT
EP0367143A2 (en) * 1988-10-31 1990-05-09 Toshiba Kikai Kabushiki Kaisha Clamping cylinder system
EP0442842A1 (en) * 1990-02-14 1991-08-21 Dionizy Simson Hydraulic actuator with pressure intensifier
US5188014A (en) * 1990-02-14 1993-02-23 Dionizy Simson Hydraulic cylinder with pressure transmission
DE4128389A1 (en) * 1991-08-27 1993-03-04 Grau Gmbh Double acting cylinder with ring piston and central piston - with dimensioning of effective surfaces to ensure pistons can move to mid-point

Families Citing this family (6)

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Publication number Priority date Publication date Assignee Title
US4841846A (en) * 1986-02-24 1989-06-27 Grambling William D Pneumatic actuators with liquid seals for oil and gas well swabs
US5062268A (en) * 1990-02-02 1991-11-05 The University Of British Columbia Fluid actuator
JP2623075B2 (en) * 1995-02-03 1997-06-25 悦男 安藤 Fluid cylinder
DE10306128A1 (en) * 2003-02-14 2004-08-26 Richard Voß Grubenausbau GmbH Method for increasing pressure in working cylinder has a smaller inner piston to further compress the fluid and achieve a working pressure greater than the pump pressure
DE102012007681B4 (en) * 2012-04-17 2016-01-21 Festo Ag & Co. Kg Fluid operated linear actuator
JP5939950B2 (en) * 2012-10-01 2016-06-22 株式会社コスメック Cylinder device with booster mechanism

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DE1964076A1 (en) * 1969-12-22 1971-06-24 Rexroth Gmbh G L Working cylinder with rapid traverse piston

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3620876A1 (en) * 1986-06-21 1987-12-23 Hehl Karl HYDRAULIC ELEMENT AND DRAWING TOOL ASSEMBLED WITH IT
EP0367143A2 (en) * 1988-10-31 1990-05-09 Toshiba Kikai Kabushiki Kaisha Clamping cylinder system
EP0367143A3 (en) * 1988-10-31 1991-05-02 Toshiba Kikai Kabushiki Kaisha Clamping cylinder system
EP0442842A1 (en) * 1990-02-14 1991-08-21 Dionizy Simson Hydraulic actuator with pressure intensifier
US5188014A (en) * 1990-02-14 1993-02-23 Dionizy Simson Hydraulic cylinder with pressure transmission
DE4128389A1 (en) * 1991-08-27 1993-03-04 Grau Gmbh Double acting cylinder with ring piston and central piston - with dimensioning of effective surfaces to ensure pistons can move to mid-point

Also Published As

Publication number Publication date
US4620419A (en) 1986-11-04
ATE36038T1 (en) 1988-08-15
ZA853539B (en) 1986-01-29
CH665007A5 (en) 1988-04-15
EP0164334B1 (en) 1988-07-27
DE3564010D1 (en) 1988-09-01
JPS6136505A (en) 1986-02-21

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