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EP0060412B1 - Dispositif de freinage en fin de course d'un piston de cylindre à double effet - Google Patents

Dispositif de freinage en fin de course d'un piston de cylindre à double effet Download PDF

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Publication number
EP0060412B1
EP0060412B1 EP82101329A EP82101329A EP0060412B1 EP 0060412 B1 EP0060412 B1 EP 0060412B1 EP 82101329 A EP82101329 A EP 82101329A EP 82101329 A EP82101329 A EP 82101329A EP 0060412 B1 EP0060412 B1 EP 0060412B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
medium
return valve
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
EP82101329A
Other languages
German (de)
English (en)
Other versions
EP0060412A1 (fr
Inventor
Axel Kemner
Helmut Göttling
Rolf Heise
Werner Dannenberg
Hans-Jürgen Pfeifer
Wolf-Dietrich Kamke
Walter Ortmann
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.)
Wabco Westinghouse Steuerungstechnik and Co GmbH
Original Assignee
Wabco Westinghouse Steuerungstechnik and Co GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wabco Westinghouse Steuerungstechnik and Co GmbH filed Critical Wabco Westinghouse Steuerungstechnik and Co GmbH
Priority to AT82101329T priority Critical patent/ATE13215T1/de
Publication of EP0060412A1 publication Critical patent/EP0060412A1/fr
Application granted granted Critical
Publication of EP0060412B1 publication Critical patent/EP0060412B1/fr
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
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/225—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke with valve stems operated by contact with the piston end face or with the cylinder wall
    • 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
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke

Definitions

  • the invention relates to a device for the end braking of the working piston of a double-acting working cylinder according to the preamble of claim 1.
  • Such double-acting working cylinders with end braking are used wherever it is necessary to first transmit a rapid movement in two directions and then to slow the movement relatively slowly. This is e.g. B. required for automatic door locking devices.
  • a known device of the type mentioned above (door cylinder 422 802 Europe catalog from WABCOissemsen GmbH) is constructed in such a way that each chamber of the double-acting working cylinder is continuously connected to a pressure medium connection via a throttled passage and via a stroke-controlled valve with relative Large cross section can be connected to the pressure medium connection.
  • the valve is designed and arranged such that it is automatically closed when a predetermined position of the working piston is reached, so that the chamber to be vented is then only vented via the throttled passage.
  • the stepwise ventilation described is carried out in the chamber on the piston rod side in that the piston rod is stepped and the thicker part of the piston rod facing the piston forms the desired valve for blocking the ventilation of the large cross section from the chamber on the piston rod side with an annular seal arranged in an intermediate wall of the cylinder .
  • the ring seal has a sealing lip which enables the ventilation of the chamber on the piston rod side and which bears sealingly against the thicker part of the piston rod during the ventilation.
  • a magnetically actuated valve device which, arranged on a double-acting working cylinder, serves for venting the chamber of the working cylinder acted upon by the pressure medium when the working piston approaches its end position.
  • this known valve device one cannot Avoid largely usable extension of the working cylinder.
  • a disadvantage of this valve device is that the valve switching magnet must be moved mechanically from the working piston towards the valve closure member.
  • the path that the piston is to travel at a reduced speed in order to prevent the piston from hitting the cylinder cover hard can be dimensioned only very briefly. In the case of large working cylinders whose pistons have a relatively large mass to be accelerated or decelerated, this short distance is often not sufficient to effectively reduce the piston speed.
  • the invention is therefore based on the object to provide a device of the type mentioned, in which the described, not usable for the use of the working piston and thus the piston rod extension of the cylinder is avoided with simple means and which a safe and sufficient reduction in speed of the piston before reaching its end position.
  • the device according to the invention is characterized in addition to the compact and short construction of the working cylinder in that both the compressed air to be controlled into the pressure medium chambers and the compressed air flowing out of the pressure medium chambers are used for switching the valves, which enables the use of small switching and holding magnets.
  • the piston rod 1, 36 is arranged in the end wall, which closes the first pressure medium chamber 19, and is provided with a sealing element 37 lead out of the working cylinder.
  • a sealing ring 20 arranged on the circumference of the working piston 21 seals the first pressure medium chamber 1 against the second pressure medium chamber 22.
  • the piston rod 1, 36 is divided into a non-magnetizable part 36 and a magnetizable part 1 in a ratio of approximately 1: 3.
  • the cylinder has two pressure medium connections 13 and 23 via an unshown multi-port valve with egg - can be brought ner pressure fluid source in communication.
  • the pressure medium connection 13 is part of a quick exhaust valve, which has a sealing seat 12, an outlet seat 9 and a cantilevered valve closure member 11.
  • the connection 23 is also part of a quick exhaust valve, which has a sealing seat 24, an outlet seat 26 and a cantilevered valve closure member 25.
  • Both quick exhaust valves 19, 11, 12 and 24, 25, 26 each have a pressure medium outlet 7 and 27 leading to the atmosphere.
  • the quick-exhaust valve 9, 11, 12 provided with the connection 13 is followed by a check valve integrated in the working cylinder housing, which comprises a valve seat 14, a valve closure body 15 and a valve closure body 15, which is supported on a housing shoulder 2, in the direction of the valve seat 14 compression spring 18 to be acted upon.
  • a permanent magnet 17 is firmly connected to the valve closure body 15. The stroke of the valve closure member 15 and thus also of the permanent magnet 17 is limited in the direction of the open position by a stop 3 provided in the valve housing, on which a disk 5 fixedly connected to the valve closure member 15 is placed. Passages 4 are provided in the disk 5, via which the first pressure medium chamber 19 is continuously connected to a throttle bore 8 serving as a bypass.
  • the throttle bore 8 leads to the outlet 7 of the quick exhaust valve 9, 11, 12.
  • the cross section of the throttle bore 8 can be changed by means of an adjusting screw 6.
  • the piston rod part 36 has an axially extending bore 34 which penetrates the working piston 21 and which cooperates in a plug-like manner with a mandrel 32 arranged on the end face which closes the second pressure medium chamber 22 of the working cylinder.
  • the mandrel 32 has a bore 33 running in the longitudinal direction, via which the second pressure medium chamber 22 can be connected to a channel 28 and further to the pressure medium outlet 27 of the quick exhaust valve 24, 25, 26 leading to the atmosphere.
  • a throttle bore 29 establishes a permanent connection between the second pressure medium chamber 22 and the pressure medium outlet 27.
  • the cross section of the throttle bore 29 can be changed by means of an adjusting screw 30.
  • the working cylinder has a fastening eyelet 31 on its right end.
  • first pressure medium chamber 19 of the working cylinder is vented and the second pressure medium chamber 22 of the working cylinder is vented, so that the working piston 21 is in its right end position.
  • the mandrel 32 is received in this end position of the working piston 21 by the bore 34 arranged in the non-magnetizable part 36 of the piston rod.
  • Pressure medium is present at the connection 13 of the quick exhaust valve 9, 11, 12 belonging to the first pressure medium chamber 19 and in the first pressure medium chamber 19.
  • the valve closure member 11 of the quick exhaust valve 9, 11, 12 is held by the pressure medium at the connection 13 on the outlet seat 9, so that the pressure medium cannot escape from the first pressure medium chamber 19 via the pressure medium outlet 7.
  • valve closure member 15 of the check valve 14, 15, 18 is displaced in the direction of the stop 3 when the first pressure medium chamber 19 is ventilated by the force of the pressure medium against the force of the compression spring 18, and the check valve 14, 15, 18 has thus been brought into the open position .
  • the valve closure member 15 connected to the permanent magnet 17 is held in this position by the force of the pressure medium.
  • An additional holding force is generated by the magnetic field, which has built up around the magnetizable part 1 of the piston rod and the permanent magnet 17.
  • the valve also not shown, which is arranged between the pressure medium source (not shown) and the connections 13, 23 is switched over.
  • the second pressure medium chamber 22 is vented.
  • the pressure medium line leading to connection 13 is vented.
  • the pressure medium located in the first pressure medium chamber 19 is pressed out of the first pressure medium chamber 19 via the open check valve 14, 15, 18, the throttle bore 8, the passage 10 and the pressure medium outlet 7 .
  • the pressure medium flowing through the passage 10 causes the valve closure body 11 to rest on the sealing seat 12 of the quick exhaust valve.
  • the pressure medium connection 13 is now closed and the pressure medium outlet 7 is open. Through the opened check valve 14, 15, 18 and the passage 10, the pressure medium escapes quickly from the first pressure medium chamber 19 to the atmosphere.
  • the check valve 14, 15, 18 is held in the open position as long as the magnetizable part 1 of the piston rod 1, 36 is in the region of the permanent magnet 17 connected to the valve closure body 15.
  • connection 13 of the quick exhaust valve 9, 11, 12 is connected to the pressure medium source and the pressure medium supply to the connection 23 of the quick exhaust valve 24, 25, 26 belonging to the second pressure medium chamber 22 is blocked.
  • valve closure member 11 of the quick exhaust valve 9, 11, 12 Due to the force of the pressure medium, the valve closure member 11 of the quick exhaust valve 9, 11, 12 is lifted off the sealing seat 12 and pressed against the outlet seat 9.
  • the pressure medium flowing through the quick exhaust valve 9, 11, 12 into the passage 10 acts on the surface of the valve closure member 15 of the check valve 14, 15, 18 facing the quick exhaust valve 9, 11, 12 and displaces the valve closure member 15 and thus the permanent magnet 17 against the force of the Compression spring 18 in the direction of the stop 3.
  • pressure medium enters the first pressure medium chamber 19, as a result of which the working piston 21 is displaced in the direction of the second pressure medium chamber 22.
  • the pressure in the second pressure medium chamber 22 is first quickly reduced via the bore 33 provided in the mandrel 32 and the throttle bore 29 and the pressure medium outlet 27. As soon as the mandrel 32 is received by the bore 34 provided in the sealing element 35 and arranged in the working piston 21 and in the piston rod part 36, the pressure medium can only escape from the second pressure medium chamber 22 via the throttle bore 29. Consequently, the working piston 21 now slows down to its right end position.
  • the check valve 14, 15, 18 assigned to the first pressure medium chamber 19 remains open since the magnetizable part 1 of the piston rod 1, 36 is located in the area of the permanent magnet 17.
  • the piston rod 38 is led out of the working cylinder through a piston rod bushing provided with an annular seal 39.
  • the working piston 66 has a circumferential seal 68, by means of which the two pressure medium chambers 71, 65 are separated from one another in a pressure-tight manner.
  • a check valve is attached, which he has a valve seat 47 and a p by a compression spring 43 toward the valve seat 47 to applied Ventilver- schlußkör 46th
  • An iron core 42 firmly connected to the valve closure body 46 is slidably mounted in an annular first permanent magnet 41, which is arranged in the valve housing.
  • the check valve 47, 46, 43 is connected on the one hand via a pressure medium line 40 to the first pressure medium chamber 71 of the working cylinder and on the other hand via a channel 48 to a first quick exhaust valve which has a pressure medium connection 52, a sealing seat 51, an outlet seat 49 and a pressure medium outlet leading to the atmosphere 53 and a cantilevered valve closure body 50.
  • a throttle bore 45 is arranged in the valve housing between the pressure medium line 40 leading from the first pressure medium chamber 71 of the working cylinder to the check valve 46, 47, 43 and the channel 48 leading from the check valve 47, 46, 43 to the quick exhaust valve 49, 50, 51.
  • the cross section of the throttle bore 45 can be changed by means of an adjusting screw 44.
  • the pressure medium connection 52 of the quick exhaust valve 49, 50, 51 can be connected to a pressure medium source via a switch valve (not shown).
  • a second quick exhaust valve which is firmly connected to the working cylinder, can also be connected to the pressure medium source via a pressure medium connection 54 and the changeover valve.
  • the second quick exhaust valve has a sealing seat 55, an outlet seat 57, a cantilevered valve closure member 56 and a pressure medium outlet 58 leading to the atmosphere.
  • the quick exhaust valve 55, 56, 57 is connected to the second pressure medium chamber 65 of the working cylinder via a channel 59 and a bore 63 provided in a mandrel 64.
  • the mandrel 64 is on the end face of the work delimiting the second pressure medium chamber 65 firmly arranged cylinder and forms a valve together with a bore 70 penetrating the working piston 66 in the axial direction and extending a bit into the piston rod 38.
  • the bore 70 is enclosed in the area of the end face of the working piston 66 by a sealing ring 67.
  • a throttle bore 61 arranged in the end wall of the working cylinder delimiting the second pressure medium chamber 65 connects the second pressure medium chamber 65 to the channel 59 leading to the quick exhaust valve 55, 56, 57.
  • the cross section of the throttle bore 61 can be changed by means of an adjusting screw 62.
  • a second annular permanent magnet 69 is arranged on the piston rod 38 in the vicinity of the working piston 66.
  • a holder 60 is provided on the right end face of the working cylinder.
  • the second pressure medium chamber 65 is vented and the first pressure medium chamber 71 is vented.
  • the valve closure body 46 of the check valve 46, 47, 43 together with the iron core 42 has been displaced from the pressure medium in the direction of the working cylinder housing and the check valve 46, 47, 43 has thus been opened.
  • the permanent magnet 41 is arranged and designed so that it holds the iron core 42 with the valve closure body 46 against the force of the compression spring 43 in the position lifted from the valve seat 47.
  • the pressure medium supply to the pressure medium connection 52 of the quick exhaust valve 49, 50, 51 assigned to the first pressure medium chamber 71 is interrupted and via the quick exhaust valve 55 assigned to the second pressure medium chamber 65 , 56, 57, the channel 59 and the bore 61 or 63 pressure medium introduced into the second pressure medium chamber 65.
  • the pressure medium emerging from the first pressure medium chamber 71 shifts the valve closure body 50 in the direction of the sealing seat 51.
  • the pressure in the first pressure medium chamber 71 is initially quickly reduced.
  • the second permanent magnet 69 arranged on the piston rod 38 has reached the effective range of the first permanent magnet 41 arranged in the valve housing by the displacement of the working piston 66, the second permanent magnet 69 cancels the force of the first permanent magnet 41 (the first and second permanent magnets are arranged with opposite polarity to one another ).
  • valve closure member 46 By the force of the compression spring 43, the valve closure member 46 is pressed against the valve seat 47, so that the check valve 46, 47, 43 is closed again.
  • the pressure medium can now only reach the pressure medium outlet 53 via the throttle bore 45.
  • the pressure medium connection 52 of the first quick exhaust valve 49, 50, 51 is connected to the pressure medium source and the pressure medium supply to the pressure medium connection 54 of the quick ventilation valve 55, 56, 57 assigned to the second pressure medium chamber 65 is blocked.
  • Pressure medium flows through the first quick exhaust valve 49, 50, 51, the check valve 46, 47, 43 and the pressure medium line 40 into the first pressure medium chamber 71 of the working cylinder and displaces the working piston 66 in the direction of the second pressure medium chamber 65.
  • the pressure in the second pressure medium chamber 65 is first rapidly reduced via the bore 63 provided in the mandrel 64, the throttle bore 61, the channel 59 and the pressure medium outlet 58.
  • the mandrel 64 is received by the bore 70 provided with the sealing element 67 and arranged in the working piston 66 and in the piston rod 38, the pressure medium can only escape from the second pressure medium chamber 65 via the throttle bore 61.
  • the working piston 66 now slows down to its right end position.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Braking Arrangements (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Claims (10)

1. Dispositif de freinage en fin de course du piston (21), muni d'une tige (1, 36) d'un vérin à double effet, présentant les particularités suivantes:
a) une des chambres (19) de fluide de pression du vérin est reliée au raccord de fluide de pression (13) correspondant par un clapet de non-retour (15, 14), qui est monté de façon à être amené dans la position d'ouverture, en direction de la chambre (19);
b) la chambre de fluide de pression (19) est reliée directement au raccord (13) par un alésage (8) muni d'un étrangleur (6);
c) le clapet de non-retour (15, 14) est réalisé et disposé de façon à s'ouvrir d'abord quand du fluide de pression s'échappe de la chambre (19) puis à se fermer quand le piston (21) atteint une position prédéterminée, avant l'extrémité de la course, de sorte que le fluide de pression refoulé par le piston (21) peut d'abord s'échapper pratiquement sans entrave par le clapet de non-retour (15, 14) ouvert, et doit passer dans l'étrangleur (6) quand le clapet de non-retour est fermé,

et caractérisé en ce que:
d) l'obturateur (15) du clapet de non-retour (15, 14) est chargé par un ressort (18) dans le sens de fermeture; et
e) un aimant permanent (17) est affecté à l'obturateur (15) et interagit avec une unité constructive (1, 36) affectée au piston (21) et présentant dans le sens axial des propriétés magnétiques différentes, de sorte que l'obturateur (15) chargé par ressort est d'abord maintenu pendant la course dans la position d'ouverture, par la force magnétique, et cette dernière est supprimée dès que le piston (21) atteint la position prédéterminée avant l'extrémité de la course.
2. Dispositif selon revendication 1, caractérisé en ce que:
a) l'obturateur (15) de clapet de non-retour (14, 15, 18) est solidaire d'un aimant permanent (17); et
b) pour le déplacement de l'aimant permanent (17), l'unité constructive (1, 36) est divisée axialement en une zone (1) constituée dans un matériau magnétisable et une zone (2) constituée par un matériau non magnétisable, la zone (36) étant située en regard de l'aiment permanent (17), radialement à l'intérieur et au voisinage de la position limite du piston (21).
3. Dispositif selon revendication 2, caractérisé en ce que l'unité constructive est constituée par la tige (1, 36) du piston.
4. Dispositif selon revendication 1, caractérisé en ce que:
a) un noyau de fer (42) est disposé sur l'obturateur(46) du clapet de non-retour (46,47,43);
b) un premier aimant permanent (41) est affecté au noyau de fer (42) et peut maintenir l'obturateur (46) solidaire dudit noyau (42) dans la position soulevée par rapport au siège (47), contre la force de fermeture exercée par le ressort (43); et
c) un second aimant permanent (69) est affecté au piston (66) et disposé de façon à supprimer la force de maintien du premier aimant permanent (41) quand le piston (66) se rapproche de sa position limite.
5. Dispositif selon revendication 4, caractérisé en ce que le second aimant permanent (69) est monté sur la tige (38) du piston (66).
6. Dispositif selon une quelconque des revendications 1 à 5, caractérisé en ce qu'un dispositif de freinage du piston en fin de course est affecté à chacune des deux chambres (19, 22) de fluide de pression du vérin.
. 7. Dispositif selon une quelconque des revendications 1 à 6, caractérisé en ce que le clapet de non-retour (14, 15, 18) peut être amené dans la position d'ouverture contre la force exercée par un ressort de compression (18).
8. Dispositif selon une quelconque des revendications 1 à 6, caractérisé en ce que:
a) une soupape de purge rapide (9, 11, 12) est disposée entre le clapet de non-retour (14, 15, 18) et le raccord (13) de fluide de pression; et
b) la soupape de purge rapide (9, 11, 12) est réalisée et disposée de façon à fermer, quand du fluide de pression est introduit dans la chambre (19) du vérin qui lui est affectée, un orifice de sortie (7) relié au clapet de non-retour (14, 15, 18) et débouchant à l'air libre et à établir la liaison entre le raccord (13) de fluide de pression et le clapet de non-retour (14,15,18), et quand du fluide de pression est refoulé de la chambre du vérin, à éloigner la chambre (19) de l'orifice de sortie (7) et interrompre la liaison entre le raccord (13) de fluide de pression et le clapet de non-retour (14, 15,18).
9. Dispositif selon revendication 8, caractérisé en ce que le clapet de non-retour (14, 15, 18) et la soupape de purge rapide (9, 11, 12) sont disposés au voisinage du passage de la tige de piston dans le corps du vérin.
10. Dispositif selon une quelconque des revendications 1 à 9, caractérisé en ce que:
a) le clapet de non-retour (46, 47, 43) est réalisé sous forme d'une unité constructive, indépendante du vérin et monté de façon amovible sur ce dernier; et
b) la chambre du clapet de non-retour (46, 47, 43), reliée à la chambre (71) du vérin, est reliée par une canalisation (40) de fluide de pression au vérin.
EP82101329A 1981-03-16 1982-02-22 Dispositif de freinage en fin de course d'un piston de cylindre à double effet Expired EP0060412B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82101329T ATE13215T1 (de) 1981-03-16 1982-02-22 Einrichtung zur endabbremsung des arbeitskolbens eines doppeltwirkenden arbeitszylinders.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19813110132 DE3110132A1 (de) 1981-03-16 1981-03-16 Einrichtung zur endabbremsung des arbeitskolbens eines doppeltwirkenden arbeitszylinders
DE3110132 1981-03-16

Publications (2)

Publication Number Publication Date
EP0060412A1 EP0060412A1 (fr) 1982-09-22
EP0060412B1 true EP0060412B1 (fr) 1985-05-08

Family

ID=6127433

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82101329A Expired EP0060412B1 (fr) 1981-03-16 1982-02-22 Dispositif de freinage en fin de course d'un piston de cylindre à double effet

Country Status (4)

Country Link
EP (1) EP0060412B1 (fr)
AT (1) ATE13215T1 (fr)
DE (2) DE3110132A1 (fr)
ES (1) ES510432A0 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4400483C2 (de) * 1994-01-11 1996-12-19 Invest Tech Ag Linearantriebszylinder
GB9501117D0 (en) * 1995-01-20 1995-03-08 Norgren Martonair Gmbh Fluid-powered cylinder
TW451031B (en) * 1999-10-01 2001-08-21 Smc Corp Linear actuator with air buffer mechanism
US6633015B2 (en) * 2000-12-08 2003-10-14 Doben Limited Soft-touch pneumatic drive unit
US8065930B2 (en) * 2008-03-26 2011-11-29 GM Global Technology Operations LLC Hydraulic actuator for transmissions having reduced noise
GB0810391D0 (en) * 2008-06-06 2008-07-09 Isentropic Ltd Fluid servo and applications

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Publication number Priority date Publication date Assignee Title
DE7122330U (de) * 1971-09-09 Gebr Felss Arbeitszylinder mit hydraulisch oder pneumatischer Betätigung
US2464962A (en) * 1945-09-27 1949-03-22 Westinghouse Air Brake Co Fluid pressure motor
DE1239948B (de) * 1959-06-30 1967-05-03 Stothert & Pitt Ltd Durch Druckmedium betaetigter, doppeltwirkender Druckzylinder
US3157095A (en) * 1962-04-12 1964-11-17 Elmer F Heiser Piston and cylinder device
DE1961838U (de) * 1966-10-14 1967-06-08 Realpa A G Rueckschlagventil.
DE1601770A1 (de) * 1967-02-14 1970-03-19 Westinghouse Air Brake Co Doppeltwirkender,druckmittelgesteuerter Zylinder
DE1601749A1 (de) * 1968-01-15 1970-05-21 Hermann Post Hydraulischer oder pneumatischer Arbeitszylinder
GB1278762A (en) * 1970-01-15 1972-06-21 Martonair Ltd Magnetically-operable device
DE2334413A1 (de) * 1973-07-06 1975-01-30 Wabco Westinghouse Gmbh Pneumatischer stellantrieb
FR2410756A1 (fr) * 1977-11-30 1979-06-29 Outillage Air Comprime Dispositif de demarrage d'un verin a piston amorti
DE2908583A1 (de) * 1979-03-05 1980-09-18 Wabco Fahrzeugbremsen Gmbh Einrichtung zur endabbremsung des arbeitskolbens eines doppeltwirkenden arbeitszylinders
DE2949250A1 (de) * 1979-12-07 1981-06-11 Wabco Steuerungstechnik GmbH & Co, 3000 Hannover Betaetigungseinrichtung fuer ein wegeventil

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
WABCO EUROPA-KATALOG, TÜRZYLINDER 422802, Ausgabe 10.79 *

Also Published As

Publication number Publication date
EP0060412A1 (fr) 1982-09-22
ES8303626A1 (es) 1983-02-01
DE3263635D1 (en) 1985-06-13
DE3110132A1 (de) 1982-09-23
ATE13215T1 (de) 1985-05-15
ES510432A0 (es) 1983-02-01

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