[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP0710774A2 - Verin de travail - Google Patents

Verin de travail Download PDF

Info

Publication number
EP0710774A2
EP0710774A2 EP95115386A EP95115386A EP0710774A2 EP 0710774 A2 EP0710774 A2 EP 0710774A2 EP 95115386 A EP95115386 A EP 95115386A EP 95115386 A EP95115386 A EP 95115386A EP 0710774 A2 EP0710774 A2 EP 0710774A2
Authority
EP
European Patent Office
Prior art keywords
working cylinder
cylinder according
pressure medium
chamber
piston
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
EP95115386A
Other languages
German (de)
English (en)
Other versions
EP0710774B1 (fr
EP0710774A3 (fr
Inventor
Lothar Müller
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.)
Festo SE and Co KG
Original Assignee
Festo SE and Co KG
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 Festo SE and Co KG filed Critical Festo SE and Co KG
Publication of EP0710774A2 publication Critical patent/EP0710774A2/fr
Publication of EP0710774A3 publication Critical patent/EP0710774A3/fr
Application granted granted Critical
Publication of EP0710774B1 publication Critical patent/EP0710774B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • 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
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • 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
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1428—Cylinders
    • 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
    • F15B15/202—Externally-operated valves mounted in or on the actuator

Definitions

  • the invention relates to a working cylinder with a housing in which a piston chamber is formed, in which there is a piston which can be driven to move by the application of fluid.
  • Working cylinders of this type are general state of the art and are operated regularly in the context of pressure medium networks.
  • a compressor acts as a pressure medium source, which supplies a pressure medium store, from where the assigned working cylinders are supplied with the compressed air via pipes or hoses.
  • the pressure medium reservoir is used to compensate for pressure fluctuations within a network in order to ensure that the operating pressure is as high as possible for all consumers.
  • a working cylinder of the type mentioned at the outset that its housing has a pressure medium reservoir which is fed by a compressed air medium source and has at least one storage chamber which is in fluid communication with the piston chamber.
  • the working cylinder thus has its own pressure medium reservoir, which is provided on or in the housing of the working cylinder.
  • the working cylinder and the pressure medium accumulator can thus belong together Form assembly that combines the working cylinder and the pressure medium accumulator in a compact design.
  • the pressure medium reservoir provides a pressure medium volume in the immediate vicinity of the piston chamber of the working cylinder, the size of which can easily be dimensioned such that the cylinder function required from case to case can be reliably called up.
  • the proximity to the piston chamber results in short fluid paths, so that there is no significant drop in pressure and the working cylinder has a very good response.
  • the combination of the working cylinder with a pressure medium storage opens up a wide range of design and application options, which depend, among other things, on whether the storage chamber of the pressure medium storage is constantly connected to at least one working chamber of the working cylinder or whether control elements are interposed in the fluid connection that control the passage cross section enable.
  • a particularly cost-effective solution is available if the Pressure fluid reservoir is an integral part of the housing, the at least one storage chamber being arranged together with the piston chamber in one and the same housing.
  • Such a compact unit can be realized in an advantageous manner by designing a tubular section of the housing as an extruded or drawn component into which the piston chamber and the storage chamber are integrally molded.
  • the piston chamber has an oval cross section shaped like an ellipse, and the cross section of the storage chamber is rectangular.
  • the pressure medium accumulator in which the storage chamber of the pressure medium accumulator is in constant communication with the one working chamber of the piston chamber, can be used to form a fluid spring, in particular an air spring, which prestresses the piston in an initial position.
  • a fluid spring in particular an air spring, which prestresses the piston in an initial position.
  • the fluid connection between the at least one storage chamber and the piston chamber is a connection which is controlled with regard to the passage cross section, with the two working chambers of the piston chamber advantageously communicating with the storage chamber via their own controlled fluid connection.
  • a control valve can be provided as the control element, for example in the form of a 3/2-way valve, wherein the control valves can be integrated in the housing in order to make a further contribution to the compactness of the working cylinder.
  • the working cylinder according to the example has a housing designated overall by 1, which is composed of a central tube section 2 and two end caps 3, 4 attached to the end of this tube section 2.
  • a linearly extending piston chamber 5 is formed in the tube section 2, which extends over the entire length and has a cylindrical cross-sectional contour.
  • the piston chamber 5 opens on both end faces of the pipe section 2 and is sealed there by the attached end caps 3, 4.
  • a piston 6 is arranged axially displaceably in the piston chamber 5. It works in a sealing manner with the peripheral wall of the piston chamber 5 and divides it axially into two working chambers 7, 8. In a manner still to be explained, both working chambers 7, 8 can be acted upon with a pressurized fluid, referred to below as pressure medium, around the piston 6 to drive a linear movement in one direction or the other.
  • pressure medium a pressurized fluid, referred to below as pressure medium
  • compressed air is provided as the pressure medium.
  • the movement of the piston 6 can be tapped outside the housing 1.
  • the piston 6 is connected to a piston rod 12 which passes through at least one end cover 4 to the outside and whose outer section 13 enables the connection to an object to be moved.
  • a sealing and / or guiding device 15 cooperating with the piston rod 12 is provided in the corresponding opening 14 of the end cover 3.
  • a pressure medium reservoir 16 An integral part of the housing 1 and in the present case the Pipe section 2 is a pressure medium reservoir 16.
  • the pressure medium reservoir 16 is formed by a storage chamber 17 which, like the piston chamber 5, is designed as a cavity in the pipe section 2.
  • the storage chamber 17 advantageously runs parallel to the longitudinal extent of the piston chamber 5 and the piston running surface provided therein. It is open to the two opposite axial end faces 18, 18 'of the pipe section 2 and there, like the piston chamber 5, is closed off by the associated end cover 3, 4.
  • the tube section 2 can be produced very simply in the form of an extruded or drawn profile part, the piston chamber 5 and the storage chamber 17 being introduced directly during production using the extrusion process.
  • the pipe section 2 thus practically represents a double pipe component, at least the wall of the storage chamber 17 after extrusion not requiring any further finishing, since it does not form a running surface and does not have to lead to any moving parts.
  • connection opening 22 is provided which is accessible from the outside and opens into the storage chamber 17.
  • the storage chamber 17 can be connected to a pressure medium source P via this connection opening 22.
  • the connection is made via a rigid or flexible line 23 which can be detachably screwed onto the connection opening 22.
  • the pressure medium source P is a compressor. This externally arranged pressure medium source P need not necessarily have its own pressure medium store.
  • a certain volume of air is always made available in the storage chamber 17 via the pressure medium source P, which is preferably constantly present.
  • the pressure medium pressure prevailing in the storage chamber 17 is predetermined as required via a so-called pressure reducer or a pressure control valve 24 which is switched on in the connection between the storage chamber 17 and the pressure medium source P. In this way, the maintenance of constant pressure conditions in the pressure medium reservoir 16 can be ensured.
  • the pressure control valve 24 can be arranged in the course of the line 23, but is preferably integrated in the housing 1.
  • the storage chamber 17 and the piston chamber 5 are in fluid communication via at least one channel 25, 25 '. In this way, pressure medium can be supplied to the piston chamber 5 from the storage chamber 17. Since the latter is located in the immediate vicinity of the piston chamber 5, there is no significant drop in pressure, so that the response to the piston movement is very good. This also applies to the long-stroke version of the working cylinder.
  • both working chambers 7, 8 are independently in fluid connection with the storage chamber 17. In both cases, these are connections which can be controlled with regard to the passage cross section made available to the pressure medium.
  • Corresponding control devices are indicated at 26 in FIGS. 1 and 2 and in the present case are formed by control valves 27, 27 '.
  • the two working chambers 7, 8 are each connected to the storage chamber 17 via one of the channels 25, 25 'mentioned, and each of these channels 25, 25' is controlled by a control valve 27, 27 ', which is expediently interposed in the relevant channel .
  • the control valves 27, 27 ' accordinging to the example are switching valves which either enable or completely block the passage through the assigned channel 25, 25'.
  • control valves can also be readily provided, with which intermediate positions between the closed position and the maximum open position can be specified, with so-called proportional valves being particularly considered.
  • the control valves 27, 27 ' are integrated into the housing 1 of the working cylinder in order to achieve a space-saving design.
  • the two control valves 27, 27 'in the exemplary embodiment are installed in the two oppositely arranged end caps 3, 4, in which they are preferably received completely recessed.
  • Each control valve 27, 27 ' communicates with a plurality of channels which run inside the associated end cover 3, 4.
  • the first is the already mentioned connecting channel 25, 25 ', which is divided by the control valve 27, 27' into two channel sections 28, 28 ', one of which is in the storage chamber 17 and the other in the associated working chamber 7 and 8 opens.
  • Ventilation channel 32 which is also connected on the one hand to the control valve 27, 27 ', but on the other hand is open to the environment and opens out on the outer surface of the associated end cover 3, 4.
  • Lines or silencers can be attached.
  • the control valves 27, 27 ' are designed as so-called 3/2-way valves and provide two possible switching positions.
  • the first switching position the open position, the two channel sections 28, 28 'are connected to one another, so that the passage through the relevant connecting channel 25, 25' is released.
  • the second switching position the closed position, the channel section 28 leading into the storage chamber 17 is blocked, while the second channel section 28 'is connected to the ventilation channel 32, so that pressure medium can be displaced from the associated working chamber 7 or 8.
  • the pressure medium reservoir 16 serves as an internal pressure medium source, from which the working chambers 7, 8 are fed as required and, depending on the switching position of the control valves 27, 27 ', a movement of the piston 6 in a desired direction can be caused.
  • control valves 27, 27 ' are advantageously electrically operated and can be designed as solenoid valves. Electrical supply lines are indicated at 33.
  • FIG. 3 Several working cylinders of those shown in Figs. 1 and 2 Type can be combined with one another in the context of a pressure medium network, as is indicated schematically in FIG. 3.
  • several working cylinders are connected via the lines 23 mentioned to a common compressed air source P, which keeps the pressure medium accumulator 16 of all working cylinders filled in parallel. Since each working cylinder is assigned its own pressure medium reservoir 16 in the immediate vicinity, there is sufficient pressure and air volume in each piston chamber even when all working cylinders are actuated at the same time in order to ensure reliable functioning.
  • FIG. 4 Another design of the working cylinder according to the invention is shown in FIG. 4.
  • only one of the working chambers 7 is in fluid communication with the storage chamber 17, which is an uncontrolled permanent connection which is provided by a connecting channel 25 formed in the housing 1.
  • the working chamber 7 which is acted upon is expediently the working chamber on the piston rod side, so that the prevailing pressure medium pressure constantly acts on the piston-piston rod combination in the direction of entry.
  • the compressed air has the function of a fluidic return spring, which always tries to keep the piston 6 in a starting position on the end cover 3 facing away from the piston rod 12.
  • the second working chamber 8 is connected to the pressure medium source P via an intermediate control valve 34.
  • the associated working chamber 8 In a first switching position of the control valve 34, the associated working chamber 8 is vented, so that the piston 6, caused by the stored pressure medium, is held in the retracted starting position.
  • pressure medium arrives from the pressure medium source P in the working chamber 8 and moves the piston 6 against the restoring force in the direction of the opposite end cover 4. This is in the chamber system consisting of the piston rod-side working chamber 7 and the storage chamber 17 existing air is compressed, so that the piston 6 is pushed back into the starting position after the control valve 34 has been switched again.
  • a pressure relief valve 35 is expediently connected to the storage chamber 17, which opens when the pressure increases, in order to limit the pressure prevailing in the chamber system mentioned and to ensure that the piston 6 can perform the maximum possible stroke.
  • the pressure medium reservoir 16 is supplied via a line 23 of the type already described above, which connects a connection opening 22 of the pressure medium reservoir 16 to the pressure medium source P.
  • a pressure control valve 24 is expediently switched on.
  • a check valve 36 is located in this connection, which blocks in the direction of the pressure medium source P in order to prevent fluid from being pushed back.
  • Both the pressure relief valve 35 and the pressure control valve 24 and the check valve 36 can be integrated in the housing 1.
  • the working chamber 8 facing away from the piston rod 12 can also be fed via the storage chamber 17 instead of a direct connection to the pressure medium source P by arranging and switching the relevant control valve 34 in the manner described in relation to FIGS. 1 to 3.
  • Aluminum material is expediently used as the material for the housing 1. It is very suitable for the production by extrusion. At this point, however, it should be mentioned that the pressure medium accumulator 16, in particular for retrofitting existing conventional working cylinders, can also be designed as a separate device which is attached to the housing of the working cylinder. However, the integration into the cylinder housing permits particularly compact designs, since it is possible to give the storage chamber 17 practically any cross-sectional shape and to accommodate it optimally in the housing cross-section.
  • the working cylinder has a housing that is relatively flat despite the integration of several cavities.
  • the arrangement is such that the longitudinal axes of the cross sections of the piston chamber 5 and the storage chamber 17 arranged above are aligned parallel to one another, so that a minimal overall height is established.
  • FIG. 5 Also possible would be the design schematically indicated in FIG. 5, in which a plurality of storage chambers 17, here: two, are designed independently of one another and have a different internal pressure. This can be achieved, for example, by the fact that all storage chambers 17 communicate with the same pressure medium source P, but that each storage chamber 17 is assigned its own pressure control valve 24, with which the storage pressure can be specified as required.
  • This arrangement makes it possible to apply different fluid pressures to the two working chambers 7, 8, it being readily possible for each working chamber 7, 8 to be connected in a controlled manner to all the storage chambers 17 in order to actuate the respective control valve in order to switch a respective working chamber to any storage chamber 17 to connect.
  • the two existing storage chambers 17 are shown one behind the other in the longitudinal direction of the housing 1. It goes without saying however, that the plurality of storage chambers 17 preferably lie next to one another and each pass over the entire length of the pipe section 2 in the manner of the storage chambers shown in FIGS. 1 to 4, in order to enable simple production by extrusion.
  • the storage chamber 17 is designed as a hollow cylinder overall and has an annular cross section, wherein it is arranged coaxially with the piston chamber 5 and surrounds it concentrically or coaxially. In this way, a particularly compact arrangement with a high storage volume can be realized.
  • FIG. 6 can also be operated, for example, in the same way as the working cylinder according to FIGS. 1 to 4.
  • An operating mode corresponding to FIG. 4 is shown, with a connection opening 22 being visible through which the storage chamber 17 of the hollow cylindrical pressure medium accumulator 16 can be seen pressure medium under a certain pressure can be filled. This pressure could be in the range of 1.5 bar, for example.
  • This pressure is present in one working chamber 7 via a connecting channel 25.
  • the other, Working chamber 8 not connected to the pressure medium reservoir is fed with pressure medium under higher pressure, this pressure being, for example, in the order of 6 bar.
  • the corresponding feed opening communicating with the working chamber 8 is shown at 37.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Pressure Circuits (AREA)
EP95115386A 1994-11-07 1995-09-29 Verin de travail Expired - Lifetime EP0710774B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4439667 1994-11-07
DE4439667A DE4439667C2 (de) 1994-11-07 1994-11-07 Arbeitszylinder

Publications (3)

Publication Number Publication Date
EP0710774A2 true EP0710774A2 (fr) 1996-05-08
EP0710774A3 EP0710774A3 (fr) 1998-07-29
EP0710774B1 EP0710774B1 (fr) 2002-01-09

Family

ID=6532639

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95115386A Expired - Lifetime EP0710774B1 (fr) 1994-11-07 1995-09-29 Verin de travail

Country Status (4)

Country Link
US (1) US5638676A (fr)
EP (1) EP0710774B1 (fr)
KR (1) KR0158761B1 (fr)
DE (2) DE4439667C2 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1522331A1 (fr) * 2003-10-10 2005-04-13 Festo AG & Co Extenseur pneumatique
EP1522330A1 (fr) * 2003-10-10 2005-04-13 Festo AG & Co Extenseur pneumatique

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29614205U1 (de) * 1996-08-16 1996-10-02 Kuhnke GmbH, 23714 Malente Fluidisch betätigbares Arbeitsglied
DE29714681U1 (de) * 1997-08-16 1997-10-16 Festo AG & Co, 73734 Esslingen Fluidbetätigter Arbeitszylinder
DE19823347A1 (de) * 1998-05-13 1999-11-18 Claas Ohg Einrichtung zur Steuerung und Einstellung von Arbeitszylindern
DE19826488A1 (de) * 1998-06-13 1999-12-23 Dautel Gmbh Kolben-Zylinder-Aggregat
DE19853942C1 (de) 1998-11-24 2000-07-13 Festo Ag & Co Elektrischer Linearantrieb
DE19854142C1 (de) 1998-11-24 2000-03-23 Festo Ag & Co Mehrzahl von Linearantrieben
DE19855286B4 (de) * 1998-11-24 2004-03-25 Rexroth Mecman Gmbh Pneumatischer Druckmittelzylinder
DE10161562B4 (de) * 2001-12-14 2005-07-21 Eurocopter Deutschland Gmbh Notöffnungszylinder einer Passagiertür
US7108324B2 (en) * 2002-06-28 2006-09-19 Lear Corporation Vehicle seat adjuster
EP1387090B1 (fr) * 2002-08-02 2014-04-30 Bosch Rexroth AG Dispositif à actionnement hydraulique
DE10309304B4 (de) * 2003-03-04 2005-03-31 Festo Ag & Co. Pneumatisch betätigbarer Schlitzzylinder
DE102004014293B4 (de) * 2004-03-22 2024-04-18 Alpha Fluid Hydrauliksysteme Müller GmbH Verstelleinheit
DE102005041211A1 (de) * 2005-08-31 2007-03-01 Robert Bosch Gmbh Integrierte Druckwandler-Unterdruck-Stelleinheit
DE102005049654B4 (de) * 2005-10-18 2009-03-19 Bosch Rexroth Pneumatics Gmbh Anreihbare Ventil-Zylinder-Einheit mit einstückig hergestelltem Druckmittelverteiler sowie Ventil-Zylinder-Einheiten-Anordnung
EP2361800B1 (fr) * 2010-02-17 2013-04-24 L & P Swiss Holding AG Dispositif d'ajustement pour siège et procédé de fonctionnement d'un dispositif d'ajustement
AU2014203400A1 (en) * 2014-06-23 2016-01-21 SMC Pneumatics (Australia) Pty Ltd Factory compressed air supplies
CN106838415B (zh) * 2015-02-16 2022-08-12 艾欧史密斯(中国)热水器有限公司 比例阀阀体以及比例阀
AT16161U1 (de) * 2016-07-21 2019-03-15 Pimatic Oy Oszillationsaktuator
DE102019208885B4 (de) * 2019-06-19 2022-10-20 Festo Se & Co. Kg Verfahren zur Herstellung einer Dichtungseinheit
US12038027B2 (en) * 2020-02-14 2024-07-16 Metismotion Gmbh Actuator device and method for operating an actuator device of this type
US12031556B2 (en) * 2021-09-30 2024-07-09 Deere & Company Dual gas pressure accumulator system

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2932951A (en) * 1957-03-08 1960-04-19 Gen Dynamics Corp Forming apparatus
US3023740A (en) * 1960-05-25 1962-03-06 Fairchild Stratos Corp Delayed pneumatic actuator
US3136220A (en) * 1961-04-12 1964-06-09 Gen Dynamics Corp Controlled high energy actuator
DE2001387A1 (de) * 1970-01-14 1971-08-26 Volkswagenwerk Ag Zylinderanordnung zur Krafterzeugung mit einem Arbeits- und einem UEbersetzungszylinder
GB1347264A (en) * 1971-02-26 1974-02-27 Ellingsen K F Valve actuator operated by pressurised fluid
DE2113788C3 (de) * 1971-03-22 1979-06-21 Karl Fredrik Oslo Ellingsen Ventilumstellvorrichtung
DE2301607A1 (de) * 1973-01-13 1974-07-18 Bosch Gmbh Robert Hydraulische steuereinrichtung
US4188858A (en) * 1978-05-11 1980-02-19 Signode Corporation Bumper deterioration warning system for fastener driving tools
DE3044675A1 (de) * 1980-11-27 1982-07-08 Leybold-Heraeus GmbH, 5000 Köln Verfahren zur steuerung eines hydraulischen antriebs und fuer die durchfuehrung dieses steuerungsverfahrens geeigneter hydraulischer antrieb
JPS5932685B2 (ja) * 1981-03-26 1984-08-10 日本国有鉄道 シリンダ装置
AT392674B (de) * 1981-10-01 1991-05-27 Hoerbiger Ventilwerke Ag Einrichtung zum selbsttaetigen rueckstellen eines stellzylinders
DE3228109A1 (de) * 1982-07-28 1984-02-02 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Linearantrieb zum erzeugen impulsartiger schneller stossbewegungen
US4597322A (en) * 1984-01-09 1986-07-01 Moog Inc. Seal assemblies
DE3807889A1 (de) * 1988-03-10 1989-09-21 Festo Kg Druckmittelbetaetigbare schlittenartige vorschubeinrichtung
DE9016135U1 (de) * 1989-11-27 1991-03-28 Papst, Hans Dieter, Dipl.-Ing., 7742 St Georgen Quadratprofil für Verbindungsstreben
DE4029721C3 (de) * 1990-09-17 1997-04-03 Mannesmann Ag Kolbenstangenloser Zylinder
JP3378029B2 (ja) * 1991-08-08 2003-02-17 丸善工業株式会社 油圧ブレーカ
US5241896A (en) * 1992-05-27 1993-09-07 Phd, Inc. Pneumatic cylinder apparatus

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1522331A1 (fr) * 2003-10-10 2005-04-13 Festo AG & Co Extenseur pneumatique
EP1522330A1 (fr) * 2003-10-10 2005-04-13 Festo AG & Co Extenseur pneumatique

Also Published As

Publication number Publication date
KR960018487A (ko) 1996-06-17
EP0710774B1 (fr) 2002-01-09
DE4439667C2 (de) 1998-07-02
DE59509989D1 (de) 2002-02-14
US5638676A (en) 1997-06-17
DE4439667A1 (de) 1996-05-09
EP0710774A3 (fr) 1998-07-29
KR0158761B1 (ko) 1998-12-01

Similar Documents

Publication Publication Date Title
EP0710774A2 (fr) Verin de travail
EP1744062B1 (fr) Vérin avec amortissement de fin de course
DE3713997A1 (de) Fluidzylinder
DE3408607A1 (de) Kolben-zylinder-aggregat
EP0886036B1 (fr) Moteur à pistons à air comprimé
EP0066274A1 (fr) Arrangement de vannes pour augmenter la vitesse de sortie d'un vérin
DE3017403A1 (de) Hydropneumatischer vorschubzylinder
DE4011908C3 (de) Mehrwegeventil
DE4419213A1 (de) Hydraulischer Arbeitszylinder
EP1453720B1 (fr) Dispositif d'orientation par cables a deux circuits a coulisseaux communs
DE3000260C2 (fr)
EP2347887A1 (fr) Dispositif d'aération
DE602005002586T2 (de) Hydraulische Betätigungseinrichtung
DE69413593T2 (de) Hebeeinheit für die Gabeln von Hubwagen
DE102016224525B4 (de) Mehrwegeventil und Verfahren zu seinem Betreiben
DE4438621A1 (de) Wasserhydraulikschweißsystem sowie ein Ventil und ein Druckübersetzer für ein solches
EP1225343A1 (fr) Dispositif d'entrainement par vérin à pression fluidique
DE102008007892A1 (de) Fluidbetätigter Mehrstellungszylinder
DE102021214056B4 (de) Wegeventil
DE29712709U1 (de) Mehrwegeventil
WO2003004881A1 (fr) Cylindre de travail
DE102021203434B4 (de) Linearbewegungsvorrichtung
DE102009016198B4 (de) Fluidbetätigter Linearantrieb mit Endlagendämpfung
DE202004005410U1 (de) Pneumatisch-hydraulischer Arbeitszylinder
EP2047115B1 (fr) Entraînement linéaire à commande fluidique

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): CH DE FR IT LI

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: FESTO AG & CO

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): CH DE FR IT LI

17P Request for examination filed

Effective date: 19980716

17Q First examination report despatched

Effective date: 20000218

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR IT LI

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: TROESCH SCHEIDEGGER WERNER AG

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 59509989

Country of ref document: DE

Date of ref document: 20020214

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20021203

Year of fee payment: 8

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20030814

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030930

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20030930

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20040930

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20050531

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050929

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060401