EP0164334B1 - Hydraulic cylinder with force multiplication - Google Patents

Hydraulic cylinder with force multiplication Download PDF

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Publication number
EP0164334B1
EP0164334B1 EP85890103A EP85890103A EP0164334B1 EP 0164334 B1 EP0164334 B1 EP 0164334B1 EP 85890103 A EP85890103 A EP 85890103A EP 85890103 A EP85890103 A EP 85890103A EP 0164334 B1 EP0164334 B1 EP 0164334B1
Authority
EP
European Patent Office
Prior art keywords
piston
force
transmitter
shut
pressure medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP85890103A
Other languages
German (de)
French (fr)
Other versions
EP0164334A1 (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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Filing date
Publication date
Application filed by ENFO Grundlagen Forschungs AG filed Critical ENFO Grundlagen Forschungs AG
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
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • 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 invention relates to a hydraulic cylinder with force multiplication, with a cylinder housing in which a working piston with a piston rod on one side and a two-stage force booster piston having two regions of different diameters are sealed and arranged to be axially movable, the cylinder housing being a stepped bore with a shoulder between two regions of different diameter and the power booster piston with its areas of different diameters is guided in one of the areas of different diameters of the stepped bore to form an intermediate annular chamber, the pressure medium supply line being parallel to the drive side of the working piston and the drive side of the larger stage of the power transmission piston and in the supply line to the larger stage the power booster piston is arranged a shut-off device, which when the supply pressure increases as soon as the working piston to a Hind ernis meets opens, and the pressure chamber of the smaller stage of the power booster piston is connected to the drive side of the working piston.
  • Hydraulic cylinders are required 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 ratios 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.
  • It hydraulic cylinder of the type mentioned is known for example from DE-A-1 903 852.
  • a two-stage working piston penetrates at least partially a partially sleeve-like power transmission piston, the smaller overdrive stage of the working piston being acted upon directly by the pressure medium supplied, whereas the larger working stage of the working piston is acted upon by pressure medium of higher pressure.
  • the increase in the supply pressure is used as soon as the working piston encounters an obstacle to act on the larger step of the power transmission piston, which then generates the higher pressure with its smaller step to act on the working step of the working piston. Due to the design of the working piston and the arrangement of both pistons acting in the same direction, this known hydraulic cylinder is also relatively large and can therefore only be used instead of the customary single-stage cylinder while accepting disadvantages in this regard.
  • the object of the present invention is to avoid the disadvantages of the known arrangements and to improve a hydraulic cylinder of the type mentioned at the outset in such a way that the simplest possible way without appreciable increase in size and weight compared to conventional single-stage cylinders.
  • the working piston is formed in a single stage and with a piston rod penetrating the force intensifying piston centrally sealed and is guided in the region of the stepped bore with a smaller diameter, the piston rod penetrating the region of the stepped bore with a larger diameter, and in that the annular chamber between the two areas of different diameters on the force intensifier piston and on the cylinder housing directly forms the pressure chamber of the smaller step of the force intensifier piston.
  • Working piston and power booster piston are thus arranged directly in the same cylinder housing, the power booster piston moving in the opposite direction to the direction of movement of the working piston when pressure is applied, which enables a simple and compact construction.
  • the area of the stepped bore with a smaller diameter lying between the working piston and the pressure booster piston has an opening for pressure medium supply and discharge, which on the one hand allows the two pistons to be easily returned to their starting position after the working stroke has been carried out and on the other hand results in a very simple way a stroke limitation, since when this opening is shut off by the working piston no further stroke is possible.
  • an opening piston can be acted upon by pressure medium, which opens the shut-off element in the pressure medium supply line to the drive side of the force transmission piston.
  • pressure medium can flow off without pressure from the drive side of the power booster piston via the associated shut-off device.
  • a further shut-off element is connected in the pressure medium supply line to the drive side of the working piston, which opens at a lower pressure than that assigned to the power transmission piston and has an associated opening piston which is parallel to the Opening piston of the other shut-off element can be acted upon with pressure medium.
  • a single-stage working piston and a two-stage power booster piston 3 are arranged in the cylinder housing 1, a piston rod 4 connected to the working piston 2 passing through the power booster piston 3.
  • the working piston 2 has a circumferential groove 5 with a sealing ring 6 provided therein.
  • the force intensifier piston 3 comprises the regions 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 are provided in the area 7 and in the area 8.
  • a circumferential groove 14 with a seal 15 provided therein is also provided in the bore 13 provided in the region 8 of the force booster piston 3 for the passage of the piston rod 4.
  • the cylinder housing 1 is closed on the side of the force booster piston 3 by a cylinder cover 16, through which the piston rod 4 is guided.
  • a circumferential groove 18 is provided in the bore 17 of the cylinder cover 16, a circumferential groove 18 is provided with a seal 19 attached therein.
  • a first shut-off element which is acted upon by a first, weak spring 21 and is designed as a shut-off piston 22, and a second shut-off element acted upon by a second, strong spring 23 and which is designed as a shut-off piston 24.
  • Both the first and the second shut-off piston are designed in two stages, a part 25 or 26 with a larger diameter and a part 27 or 28 with a smaller diameter being provided in each case.
  • a piston rod 29 or 30 is connected to each of the parts 27 and 28 with a smaller diameter, which each lead into a chamber 31 or 32 opposite the shut-off piston. 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 on the drive side of the working piston between the latter and the cylinder wall.
  • a branch line 40 leads into an annular chamber 41 between the area 7 of the force booster piston 3 and the inner wall of the cylinder housing 1.
  • This annular chamber 41 is laterally by a shoulder 42 on the outer circumference of the force booster piston 3 and by a shoulder 43 on the inner wall of the Cylinder housing 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 on the drive side of the force booster piston 3 between the boundary surface 46 of the force booster piston opposite the cylinder cover 16 and the cylinder cover.
  • the chamber 47 between the working piston 2 and the power booster piston 3 is connected via a line 48 to the chambers on the right side of the opening piston 33 and 34 according to the figure.
  • the pressure medium is conveyed from the unpressurized chamber 47 via a 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)
  • Vehicle Body Suspensions (AREA)
  • Servomotors (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

Die Erfindung betrifft einen hydraulischen Zylinder mit Kraftmultiplikation, mit einem Zylindergehäuse, in dem ein Arbeitskolben mit einseitiger Kolbenstange und ein zweistufiger, zwei Bereiche unterschiedlichen Durchmessers aufweisender Kraftübersetzerkolben abgedichtet und axial beweglich angeordnet sind, wobei das Zylindergehäuse eine Stufenbohrung mit einem Absatz zwischen zwei Bereichen unterschiedlichen Durchmessers aufweist und der Kraftübersetzerkolben mit seinen Bereichen unterschiedlichen Durchmessers jeweils in einem der Bereiche unterschiedlichen Durchmessers der Stufenbohrung unter Bildung einer dazwischenliegenden Ringkammer geführt ist, wobei die Druckmittelzuleitung zur Antriebsseite des Arbeitskolbens und zur Antriebsseite der größeren Stufe des Kraftübersetzerkolbens parallel geführt und in der Zuleitung zur größeren Stufe des Kraftübersetzerkolbens ein Absperrorgan angeordnet ist, welches bei einer Erhöhung des Zuleitungsdruckes sobald der Arbeitskolbens auf ein Hindernis trifft öffnet, und wobei der Druckraum der kleineren Stufe des Kraftübersetzerkolbens mit der Antriebsseite des Arbeitskolbens verbunden ist.The invention relates to a hydraulic cylinder with force multiplication, with a cylinder housing in which a working piston with a piston rod on one side and a two-stage force booster piston having two regions of different diameters are sealed and arranged to be axially movable, the cylinder housing being a stepped bore with a shoulder between two regions of different diameter and the power booster piston with its areas of different diameters is guided in one of the areas of different diameters of the stepped bore to form an intermediate annular chamber, the pressure medium supply line being parallel to the drive side of the working piston and the drive side of the larger stage of the power transmission piston and in the supply line to the larger stage the power booster piston is arranged a shut-off device, which when the supply pressure increases as soon as the working piston to a Hind ernis meets opens, and the pressure chamber of the smaller stage of the power booster piston is connected to the drive side of the working piston.

Es werden vielerortes 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 Übersetzung eingesetzt. Solche Zylinder sind kompakter und leichter als einstufige Hydraulikzylinder mit gleicher Wirkkraft.Hydraulic cylinders are required 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 ratios 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 (G B-A-1 600 733 ; GB-A-1 420 389 ; US-A-4011 724 ; DE-A-3 119 307 A1). 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 Zylinderlänge um die Trennwandstärke größer sein muß. Sobald der Arbeitskolben auf seinem Weg keinen Widerstand trifft, gelangt er an den Zylinderdeckel, der Übersetzungsvorgang wird eingeleitet und der Deckel wird abgerissen oder muß entsprechend stark ausgelegt werden, was sich als Zuwachs der Abmessungen und des Gewichtes auswirkt.Solutions are known which consist of two pistons and three pressure chambers and where the pistons are arranged one after the other (G BA-1 600 733; GB-A-1 420 389; US-A-4011 724; DE-A-3 119 307 A1). This design requires a partition between the two pistons. The pistons move during the working process, e.g. B. 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 working piston encounters no resistance on its way, it reaches the cylinder cover, the translation process is initiated and the cover is torn off or has to be designed accordingly, which has the effect of an increase in dimensions and weight.

Es hydraulischer Zylinder der eingangs genannten Art ist beispielsweise aus der DE-A-1 903 852 bekannt. Ein zweistufiger Arbeitskolben durchsetzt dabei einen teilweise hülsenartig ausgeführten Kraftübersetzerkolben zumindest teilweise, wobei die kleinere Schnellgangstufe des Arbeitskolbens direkt vom zugeleiteten Druckmittel beaufschlagt wird, wogegen die größere Arbeitsgangstufe des Arbeitskolbens mit Druckmittel von höherem Druck beaufschlagt wird. Dabei wird die Erhöhung des Zuleitungsdruckes sobald der Arbeitskolben auf ein Hindernis trifft zur Beaufschlagung der größeren Stufe des Kraftübersetzerkolbens verwendet, der dann mit seiner kleineren Stufe den höheren Druck zur Beaufschlagung der Arbeitsgangstufe des Arbeitskolbens erzeugt. Zufolge der Bauweise des Arbeitskolbens sowie der in die gleiche Richtung wirkenden Anordnung beider Kolben ist auch dieser bekannte hydraulische Zylinder relativ großbauend und damit nur unter Inkaufnahme diesbezüglicher Nachteile anstelle der üblichen einstufigen Zylinder einsetzbar.It hydraulic cylinder of the type mentioned is known for example from DE-A-1 903 852. A two-stage working piston penetrates at least partially a partially sleeve-like power transmission piston, the smaller overdrive stage of the working piston being acted upon directly by the pressure medium supplied, whereas the larger working stage of the working piston is acted upon by pressure medium of higher pressure. The increase in the supply pressure is used as soon as the working piston encounters an obstacle to act on the larger step of the power transmission piston, which then generates the higher pressure with its smaller step to act on the working step of the working piston. Due to the design of the working piston and the arrangement of both pistons acting in the same direction, this known hydraulic cylinder is also relatively large and can therefore only be used instead of the customary single-stage cylinder while accepting disadvantages in this regard.

Aufgabe der vorliegenden Erfindung ist es, die genannten Nachteile der bekannten Anordnungen zu vermeiden und einen hydraulischen Zylinder der eingangs genannten Art so zu verbessern, daß auf möglichst einfache Weise ohne nennenswerten Zuwachs der Abmessungen und des Gewichtes gegenüber üblichen einstufigen Zylindern ausgekommen wird.The object of the present invention is to avoid the disadvantages of the known arrangements and to improve a hydraulic cylinder of the type mentioned at the outset in such a way that the simplest possible way without appreciable increase in size and weight compared to conventional single-stage cylinders.

Dies wird gemäß der Erfindung dadurch erreicht, daß der Arbeitskolben einstufig und mit einer den Kraftübersetzerkolben zentral abgedichtet durchsetzenden Kolbenstange ausgebildet und in dem Bereich der Stufenbohrung mit kleinerem Durchmesser geführt ist, wobei die Kolbenstange den Bereich der Stufenbohrung mit größerem Durchmesser durchdringt, und daß die Ringkammer zwischen den beiden Bereichen unterschiedlichen Durchmessers am Kraftübersetzerkolben und am Zylindergehäuse unmittelbar den Druckraum der kleineren Stufe des Kraftübersetzerkolbens bildet. Arbeitskolben und Kraftübersetzerkolben sind damit unmittelbar im gleichen Zylindergehäuse angeordnet, wobei der Kraftübersetzerkolben bei Druckbeaufschlagung sich gegenläufig zur Bewegungsrichtung des Arbeitskolbens bewegt, was eine einfache und kompakte Konstruktion ermöglicht.This is achieved according to the invention in that the working piston is formed in a single stage and with a piston rod penetrating the force intensifying piston centrally sealed and is guided in the region of the stepped bore with a smaller diameter, the piston rod penetrating the region of the stepped bore with a larger diameter, and in that the annular chamber between the two areas of different diameters on the force intensifier piston and on the cylinder housing directly forms the pressure chamber of the smaller step of the force intensifier piston. Working piston and power booster piston are thus arranged directly in the same cylinder housing, the power booster piston moving in the opposite direction to the direction of movement of the working piston when pressure is applied, which enables a simple and compact construction.

Nach einer weiteren Ausgestaltung der Erfindung weist der zwischen Arbeitskolben und Druckübersetzerkolben liegende Bereich der Stufenbohrung mit kleinerem Durchmesser eine Öffnung zur Druckmittelzu- bzw. -ableitung auf, was einerseits auf einfache Weise eine Rückstellung der beiden Kolben in ihre Ausgangsposition nach der Durchführung des Arbeitshubes erlaubt und andererseits auf sehr einfache Weise eine Hubbegrenzung ergibt, da beim Absperren dieser Öffnung durch den Arbeitskolben kein weiterer Hub mehr möglich ist.According to a further embodiment of the invention, the area of the stepped bore with a smaller diameter lying between the working piston and the pressure booster piston has an opening for pressure medium supply and discharge, which on the one hand allows the two pistons to be easily returned to their starting position after the working stroke has been carried out and on the other hand results in a very simple way a stroke limitation, since when this opening is shut off by the working piston no further stroke is possible.

Parallel zu dieser Öffnung zwischen den beiden Kolben kann ein Öffnungskolben mit Druckmittel beaufschlagbar sein, der das Absperrorgan in der Druckmittelzuleitung zur Antriebsseite des Kraftübersetzerkolbens öffnet. Damit kann bei Druckbeaufschlagung des Bereiches zwischen den beiden Kolben zum Öffnen des Zylinders das Druckmedium von der Antriebsseite des Kraftübersetzerkolbens her einfach über das zugehörige Absperrorgan drucklos abfließen.Parallel to this opening between the two pistons, an opening piston can be acted upon by pressure medium, which opens the shut-off element in the pressure medium supply line to the drive side of the force transmission piston. Thus, when pressure is applied to the area between the two pistons to open the cylinder, the pressure medium can flow off without pressure from the drive side of the power booster piston via the associated shut-off device.

In weiterer Ausgestaltung der Erfindung kann vorgesehen sein, daß parallel zu dem in der Druckmittelzuleitung zur Antriebsseite des Kraftübersetzerkolbens angeordneten Absperrorgan ein weiteres Absperrorgan in der Druckmittelzuleitung zur Antriebsseite des Arbeitskolbens geschaltet ist, welches bei einem geringerem Druck als das dem Kraftübersetzerkolben zugeordnete öffnet und einen zugehörigen Öffnungskolben aufweist, der parallel mit dem Öffnungskolben des anderen Absperrorgans mit Druckmedium beaufschlagbar ist. Die diesbezüglichen Funktionsmerkmale und Vorteile ergegen sich ebenso wie eine nähere Erläuterung der Erfindung aus der Beschreibung des in der beiliegenden Zeichnung dargestellten Ausführungsbeispiels.In a further embodiment of the invention it should be provided that a further shut-off element is connected in the pressure medium supply line to the drive side of the working piston, which opens at a lower pressure than that assigned to the power transmission piston and has an associated opening piston which is parallel to the Opening piston of the other shut-off element can be acted upon with pressure medium. The relevant functional features and advantages, as well as a more detailed explanation of the invention, can be found in the description of the exemplary embodiment shown in the accompanying drawing.

Im Zylindergehäuse 1 sind ein einstufiger Arbeitskolbens sowie ein zweistufiger Kraftübersetzerkolben 3 angeordnet, wobei eine mit dem Arbeitskolben 2 verbundene Kolbenstange 4 den Kraftübersetzerkolben 3 durchsetzt. Der Arbeitskolben 2 weist eine umlaufende Nut 5 mit einem darin vorgesehenen Dichtungsring 6 auf. Der Kraftübersetzerkolben 3 umfaßt die die beiden Stufen bildenden Bereiche 7 und 8, welche einen voneinander verschiedenen Durchmesser aufweisen. Am äußeren Umfang des Kraftübersetzerkolbens 3 sind im Bereich 7 und im Bereich 8 je eine umlaufende Nut 9 und 10 mit darin angebrachten Dichtungen 11 und 12 vorgesehen. In der im Bereich 8 des Kraftübersetzerkolbens 3 vorgesehenen Bohrung 13 zur Durchführung der Kolbenstange 4 ist ebenfalls eine umlaufende Nut 14 mit einer darin angebrachten Dichtung 15 vorgesehen.A single-stage working piston and a two-stage power booster piston 3 are arranged in the cylinder housing 1, a piston rod 4 connected to the working piston 2 passing through the power booster piston 3. The working piston 2 has a circumferential groove 5 with a sealing ring 6 provided therein. The force intensifier piston 3 comprises the regions 7 and 8 which form the two stages and which have a different diameter from one another. On the outer circumference of the force booster piston 3, a circumferential groove 9 and 10 with seals 11 and 12 are provided in the area 7 and in the area 8. A circumferential groove 14 with a seal 15 provided therein is also provided in the bore 13 provided in the region 8 of the force booster piston 3 for the passage of the piston rod 4.

Das Zylindergehäuse 1 wird auf der Seite des Kraftübersetzerkolbens 3 durch einen Zylinderdeckel 16 abgeschlossen, durch welchen die Kolbenstange 4 geführt wird. In der Bohrung 17 des Zylinderdeckels 16 ist eine umlaufende Nut 18 mit einer darin angebrachten Dichtung 19 vorgesehen.The cylinder housing 1 is closed on the side of the force booster piston 3 by a cylinder cover 16, through which the piston rod 4 is guided. In the bore 17 of the cylinder cover 16, a circumferential groove 18 is provided with a seal 19 attached therein.

Integriert in einem Ansatz 20 am Zylindergehäuse 1 sind ein durch eine erste, schwache Feder 21 beaufschlagtes, als Absperrkolben 22 ausgebildetes erstes Absperrorgan, sowie ein durch eine zweite, starke Feder 23 beaufschlagtes, als Absperrkolben 24 ausgebildetes zweites Absperrorgan vorgesehen. Sowohl der erste als auch der zweite Absperrkolben ist zweistufig ausgebildet, wobei jeweils ein Teil 25 bzw. 26 mit größerem Durchmesser und ein Teil 27 bzw. 28 mit kleinerem Durchmesser vorgesehen sind. Mit den Teilen 27 und 28 mit kleinerem Durchmesser ist je eine Kolbenstange 29 bzw. 30 verbunden, welche je in eine den Absperrkolben gegenüberliegende Kammer 31 bzw. 32 führen. In den Kammern 31 und 32 sind Öffnungskolben 33 und 34 vorgesehen.Integrated in an extension 20 on the cylinder housing 1 are a first shut-off element, which is acted upon by a first, weak spring 21 and is designed as a shut-off piston 22, and a second shut-off element acted upon by a second, strong spring 23 and which is designed as a shut-off piston 24. Both the first and the second shut-off piston are designed in two stages, a part 25 or 26 with a larger diameter and a part 27 or 28 with a smaller diameter being provided in each case. A piston rod 29 or 30 is connected to each of the parts 27 and 28 with a smaller diameter, which each lead into a chamber 31 or 32 opposite the shut-off piston. Opening pistons 33 and 34 are provided in the chambers 31 and 32.

Eine Zuleitung 35 für das Druckmedium führt in die Kammer 31 in den Bereich zwischen Kolbenstange 29 und Stirnfläche des Öffnungskolbens 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 an der Antriebsseite des Arbeitskolbens zwischen diesem und der Zylinderwand verbunden.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 on the drive side of the working piston between the latter and the cylinder wall.

Von der Leitung 38 führt eine Zweigleitung 40 in eine Ringkammer 41 zwischen dem Bereich 7 des Kraftübersetzerkolbens 3 und der Innenwandung des Zylindergehäuses 1. Diese Ringkammer 41 wird seitlich durch einen Absatz 42 am äußeren Umfang des Kraftübersetzerkolbens 3 und durch einen Absatz 43 an der Innenwandung des Zylindergehäuses 1 begrenzt.From the line 38, a branch line 40 leads into an annular chamber 41 between the area 7 of the force booster piston 3 and the inner wall of the cylinder housing 1. This annular chamber 41 is laterally by a shoulder 42 on the outer circumference of the force booster piston 3 and by a shoulder 43 on the inner wall of the Cylinder housing 1 limited.

Die den vorderen Teil 28 des zweiten Absperrkolbens 24 umgebende Kammer ist über eine Leitung 44 für das Druckmedium mit einer zweiten Druckkammer 45 an der Antriebsseite des Kraftübersetzerkolbens 3 zwischen der dem Zylinderdeckel 16 gegenüberliegenden Begrenzungsfläche 46 des Kraftübersetzerkolbens und des Zylinderdeckels verbunden. Die Kammer 47 zwischen Arbeitskolben 2 und Kraftübersetzerkolben 3 ist über eine Leitung 48 mit den Kammern auf der gemäß der Figur rechten Seite der Öffnungskolben 33 und 34 verbunden.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 on the drive side of the force booster piston 3 between the boundary surface 46 of the force booster piston opposite the cylinder cover 16 and the cylinder cover. The chamber 47 between the working piston 2 and the power booster piston 3 is connected via a line 48 to the chambers on the right side of the opening piston 33 and 34 according to the figure.

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 an der Antriebsseite des Arbeitskolbens 2 und bewegt diesen nach vorn. Dies geschieht solange, bis der Arbeitskolben 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 an der Antriebsseite des Kraftübersetzerkolbens bzw. am Zylinderdeckel 16, und die Querschnittsfläche 46 mit größerem Durchmesser des zweistufigen Kraftübersetzerkolbens 3 wird mit Druck beaufschlagt. Der Kraftübersetzerkolben 3 setzt sich in Bewegung, und dabei wird das sich zwischen den Stufen 42 und 43 des Kraftübersetzerkolbens und des Zylindergehäuses befindliche Druckmedium aus der Ringkammer 41 in die erste Druckkammer 39 an der Antriebsseite des Arbeitskolbens 2 gedrückt. Der Arbeitskolben 2 bewegt sich weiter nach vorn mit einer dem Verhältnis seiner Querschnittsfläche zur Fläche des Ansatzes 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 on the drive side of the working piston 2 and moves it forward. This continues until the working 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 drive side of the power booster piston or on the cylinder cover 16, and the cross-sectional area 46 with a larger diameter of the two-stage power booster piston 3 is pressurized. The power booster piston 3 starts to move, and the pressure medium located between the stages 42 and 43 of the power booster piston and the cylinder housing is pressed out of the annular chamber 41 into the first pressure chamber 39 on the drive side of the working piston 2. The working piston 2 moves forward with a reduced speed and increased force corresponding to the ratio of its cross-sectional area to the area of the extension 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 Arbeitskolbens und des Kraftübersetzerkolbens wird das Druckmedium aus der drucklosen Kammer 47 über eine Leitung 48 in einen nicht dargestellten Behälter befördert.During the described movements of the working piston and the force booster piston, the pressure medium is conveyed from the unpressurized chamber 47 via a line 48 into a container (not shown).

Beim Öffnen wird die Leitung 48 mit Druck beaufschlagt. Beide Öffnungskolben 33 und 34 entsperren die Absperrkolben 22 und 24, womit der Arbeitskolben 2 und der Kraftübersetzerkolben 3 auseinandergeschoben werden und die Ausgangsstellung wieder erlangen. 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 the line 48 is pressurized. Both opening pistons 33 and 34 unlock the shut-off pistons 22 and 24, so that the working piston 2 and the power booster piston ben 3 are pushed apart and regain the starting 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 Arbeitskolben 2 auf seinem Weg nach vorne auf keinen Widerstand trifft, bewegt er sich solange, bis er die Öffnung der Leitung 48 in der Kammer 47 überdeckt. Der Kraftübersetzerkolben 3 kann sich auch nicht bewegen, da der Abfluß gesperrt ist. Wenn der Schnellhub lang wird und der Umschaltvorgang kurz vor der Öffnung der Leitung 48 einsetzt, treffen beiden Kolben 2 und 3 aufeinander. In beiden Fällen ergeben sich keine Zylinderschäden und es müssen keine großen Kräfte aufgefangen werden.If the working 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 power booster piston 3 can 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. An hydraulic cylinder with force multiplication, having a cylinder housing (1, 16), in which are sealingly and axially displaceably disposed an operating piston (2) with a piston rod (4) to one side and a two-stage force-transmitter piston (3) comprising two areas (7, 8) of different diameter, wherein the cylinder housing (1, 16) comprises a stepped bore with an offset (43) between two areas of different diameter and the force-transmitter piston (3) is guided with each of its areas (7, 8) of different diameter in one of the areas of different diameter of the stepped bore so as to form an annular space (41) lying therebetween, the pressure medium supply line (35) being guided parallel to the working side (39) of the operating piston (2) and to the working side (45) of the larger stage (8) of the force-transmitter piston (3), and a shut-off device (28), which opens upon an increase in the supply pressure as soon as the operating piston (2) strikes an obstacle, being disposed in the supply line (44) to the larger stage (8) of the force-transmitter piston, and the pressure chamber (41) of the smaller stage (7) of the force-transmitter piston (3) being connected to the working side (39) of the operating piston (2), characterized in that the operating piston (2) is constructed in one stage and with a piston rod (4) passing centrally through the force-transmitter piston (3) in a sealed manner and is guided in the area of the stepped bore with the smaller diameter, the piston rod (4) passing through the area of the stepped bore with. the greater diameter, and the annular space between the two areas (7, 8) of different diameter on the force-transmitter piston (3) and on the cylinder housing (1, 16) directly forms the pressure chamber (41) of the smaller stage of the force-transmitter piston (3).
2. An hydraulic cylinder according to Claim 1, characterized in that the area of the stepped bore with a smaller diameter lying between the operating piston (2) and the force-transmitter piston (3) has an opening to the pressure medium supply or discharge line (48).
3. An hydraulic cylinder according to Claim 2, characterized in that parallel to the opening between the two pistons (2, 3) an opening piston (34) can be acted upon with pressure medium, and opens the shut-off device (28) in the pressure medium supply line to the working side (45) of the force-transmitter piston (3).
4. An hydraulic cylinder according to Claim 3, characterized in that parallel to the shut-off device (28) arranged in the pressure medium supply line to the working side (45) of the force-transmitter piston (3) a further shut-off device (27) is connected in the pressure medium supply line to the working side (39) of the operating piston (2), the further shut-off device (27) opening at a lower pressure than that associated with the force-transmitter piston (3) and comprising an associated opening piston (33) which can be acted upon with pressure medium in parallel with the opening piston (34) of the other shut-off device (28).
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
CH2357/84A CH665007A5 (en) 1984-05-11 1984-05-11 HYDRAULIC CYLINDER WITH POWER MULTIPLICATION.
CH2357/84 1984-05-11

Publications (2)

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

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ID=4231904

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EP85890103A Expired EP0164334B1 (en) 1984-05-11 1985-05-03 Hydraulic cylinder with force multiplication

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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)

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DE102012007681A1 (en) * 2012-04-17 2013-10-17 Festo Ag & Co. Kg Fluid-actuated linear drive has position dependent control valve that is actuated by primary piston and output rod for control of drive and coupling function of secondary drive fluid

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US4841846A (en) * 1986-02-24 1989-06-27 Grambling William D Pneumatic actuators with liquid seals for oil and gas well swabs
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US5062268A (en) * 1990-02-02 1991-11-05 The University Of British Columbia Fluid actuator
US5188014A (en) * 1990-02-14 1993-02-23 Dionizy Simson Hydraulic cylinder with pressure transmission
EP0442842B1 (en) * 1990-02-14 1994-04-06 Dionizy Simson Hydraulic actuator with pressure intensifier
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
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
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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DE102012007681A1 (en) * 2012-04-17 2013-10-17 Festo Ag & Co. Kg Fluid-actuated linear drive has position dependent control valve that is actuated by primary piston and output rod for control of drive and coupling function of secondary drive fluid
DE102012007681B4 (en) * 2012-04-17 2016-01-21 Festo Ag & Co. Kg Fluid operated linear actuator

Also Published As

Publication number Publication date
DE3564010D1 (en) 1988-09-01
CH665007A5 (en) 1988-04-15
ZA853539B (en) 1986-01-29
JPS6136505A (en) 1986-02-21
ATE36038T1 (en) 1988-08-15
US4620419A (en) 1986-11-04
EP0164334A1 (en) 1985-12-11

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