EP0141215A1 - Vérin à fluide sous pression avec dispositif amortisseur fin de course pour le piston - Google Patents

Vérin à fluide sous pression avec dispositif amortisseur fin de course pour le piston Download PDF

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Publication number
EP0141215A1
EP0141215A1 EP84111136A EP84111136A EP0141215A1 EP 0141215 A1 EP0141215 A1 EP 0141215A1 EP 84111136 A EP84111136 A EP 84111136A EP 84111136 A EP84111136 A EP 84111136A EP 0141215 A1 EP0141215 A1 EP 0141215A1
Authority
EP
European Patent Office
Prior art keywords
piston
working
additional
chamber
cylinder according
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
EP84111136A
Other languages
German (de)
English (en)
Other versions
EP0141215B1 (fr
Inventor
Heinrich Dr. Kedzierski
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 AT84111136T priority Critical patent/ATE25279T1/de
Publication of EP0141215A1 publication Critical patent/EP0141215A1/fr
Application granted granted Critical
Publication of EP0141215B1 publication Critical patent/EP0141215B1/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
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads
    • 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
    • F15B15/227—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having an auxiliary cushioning piston within the main piston or the cylinder end face

Definitions

  • the invention relates to a pressure-actuated working cylinder with a device for damping the end braking of the working piston according to the preamble of claim 1.
  • Such a double-acting cylinder is previously known from DE-OS 31 46 998.
  • the working piston is braked in its two end positions in such a way that the damping chamber is in one end position by a piston-like projection of one cylinder cover and a corresponding recess in the working piston and in the other end position by a piston-like one Projection of the working piston and a corresponding recess of the other cylinder cover is formed.
  • This working cylinder can thus only be braked in its two end positions and not in any intermediate position.
  • the invention is therefore based on the object of creating a pressure-actuated working cylinder of the type mentioned which, by simple means, enables precise positioning in any possible intermediate position of the working piston with adequate damping acting at the same time.
  • the invention has the advantage that only the additional piston has to be stopped for the exact positioning.
  • the position of the additional piston can be detected in a simple manner with the usual, known sensors.
  • the additional piston which has a comparatively low mass, is then braked in a control circuit or with a target control and fixed in the desired position. It is easily possible to fix the additional piston with the required parking brake forces.
  • the working piston of the working cylinder then runs with its mass and the mass of the parts moved by it against the additional piston thus fixed, which then forms a fixed wall. This final braking of the working piston is then damped in a manner known per se.
  • the position of the working piston can also be exactly predetermined.
  • the two functions "positioning” and “end deceleration” are separated to a certain extent and each is implemented in the best possible way.
  • the drawing shows a double-acting cylinder that can be used as a positioning cylinder.
  • a working piston is guided in a sealed manner.
  • This working piston sits on the stepped section 15 of a piston rod 30 and comprises two piston parts 43 and 45, between which a piston wall 14 is arranged, which in turn carries a piston seal 13.
  • the piston serving as the working piston is named with the reference number of the piston wall 14.
  • a nut 57 which can be screwed onto a corresponding thread of the piston rod 30, is provided for fastening the piston 14 on the section 15 of the piston rod 30, a sleeve 55, the piston part 45, the piston wall 14, between this nut 57 and a shoulder 22 of the piston rod 30. the piston part 43 and a further sleeve 20 are clamped.
  • an additional piston 49 is arranged, which surrounds the sleeve 55 and the piston part 45 in a ring and on the one hand by means of a seal 10 against the inner wall of the cylinder tube 48 and on the other hand by means of an intermediate the piston part 45 and the sleeve 55 arranged seal 11 is sealed against the piston 14.
  • the additional piston 49 rests under the tension of a spring 46 on a shoulder 61 of the sleeve 55, so that it can be moved axially relative to the piston 14 against the force of the spring 46.
  • the spring 46 designed as a compression spring is supported on the one hand on the piston wall 14 and on the other hand on a shoulder 47 of the additional piston 49.
  • the seal 11 is designed as a check valve so that the chamber 12 between the piston 14 and the additional piston 49, which serves as a damping chamber, via the check valve 11 with the pressure between the cover 60 and the additional piston 49 lying working pressure chamber 5 can be acted upon.
  • a further additional piston 19 is provided on the right side of the piston 14, which surrounds the sleeve 20 and the piston part 43 in an annular manner and rests against a projection 21 of the sleeve 20 under the tension of a spring 42.
  • the spring 42 designed as a compression spring is arranged between the piston wall 14 and a shoulder 16 of the additional piston 19.
  • the additional piston 19 is sealed off from the inner wall of the cylinder tube 48 by means of a seal 18.
  • the sealing against the piston part 43 and thus against the piston 14 takes place by means of a seal 17 which is arranged between the piston part 43 and the sleeve 20.
  • the seal 17 serves as a check valve, via which the pressure between the working pressure chamber 35 located between the cover 27 and the additional piston 19 can be applied to the chamber 44 located between the piston 14 and the additional piston 19 and provided as a damping chamber. It can be seen that the additional piston 19 can be moved axially relative to the piston 14 in accordance with the additional piston 49.
  • Air connection 59 is provided, which is connected to the working pressure chamber 5 via a bore 58.
  • the compressed air connection 59 is pressurized with compressed air via a compressed air line (not shown)
  • the working pressure chamber 5 and the damping chamber 12 are pressurized with compressed air so that the piston 14 can be moved to the right.
  • the force of the spring 42 is dimensioned so large that in the described operating state the additional piston 19 can also be moved to the right in the position shown relative to the piston 14.
  • a further compressed air connection 31 is provided, which is connected to the working pressure chamber 35 via a bore 32.
  • the working pressure chamber 35 and the damping chamber 44 are filled with compressed air, so that the piston 14 is then moved to the left with the additional piston 19.
  • the force of the spring 46 is dimensioned such that, in the operating state described last, the other additional piston 49 remains in the position shown relative to the piston 14.
  • the cover 60 has a further compressed air connection 1, which is connected via a bore 2 to a line connection 4 arranged in the working pressure chamber 5.
  • the line connection 4 is connected via a flexible, helical compressed air line 56 to a further line connection 54 which is arranged on the additional piston 49.
  • the line connection 54 is connected via a bore 53 of the additional piston 49 to a brake pressure chamber 52 of the additional piston 49.
  • the brake pressure chamber 52 is toward the inner wall of the cylinder tube 48 with an elastic membrane 51 completed, which can bulge outward in the manner of a bellows when pressure is applied to the brake pressure chamber 52.
  • a plurality of brake elements 50 are arranged distributed over the circumference of the additional piston 49, possibly forming a single part, which can be moved radially outward so that they can be brought into frictional engagement with the inner wall of the cylinder tube 48.
  • Corresponding brake elements 40 are arranged on the additional piston 19, which lie between the inner wall of the cylinder tube 48 and an elastic membrane 38.
  • the membrane 38 closes a brake pressure chamber 39, which connects a bore 25 in the cover 27 to a corresponding compressed air connection 26 via a bore 37 and a line connection 36 of the additional piston 19 and a flexible, helical compressed air line 23, a line connection 24 arranged in the working pressure chamber 35 is.
  • the brake elements 40 can be brought into frictional engagement with the inner wall of the cylinder tube 48 by means of compressed air supply to the compressed air connection 26.
  • the brake pressure chambers 39 and 52 are each connected to the associated damping chamber 44 or 12 via a check valve, the check valve opening towards the brake pressure chamber.
  • this check valve is shown only symbolically as valve 41 in the additional piston 19.
  • a corresponding check valve is arranged in the additional piston 49, where it forms a connection between the damping chamber 12 and the brake pressure chamber 52.
  • the additional piston 49 has further bores 8 and 9, between which a throttle 7 adjustable by means of a screw is arranged.
  • a throttle 7 adjustable by means of a screw Via this throttle device or throttle line 7, 8, 9, the damping chamber 12 is connected to an annular chamber 6 surrounding the sleeve 55, which in turn is connected to the working pressure chamber 5.
  • the check valve formed by the annular lip seal 11 and opening towards the damping chamber 12 is bridged by the throttle device 7, 8, 9.
  • a corresponding throttle device for bridging the check valve formed by the annular lip seal 15 and opening towards the damping chamber 44 is provided in the additional piston 19. To simplify the drawing, this throttle device for the additional piston 19 is not shown.
  • the double-acting working cylinder described so far and shown in the drawing with a greatly reduced length works as follows: It is assumed that the piston 14 is to be moved out of the position shown to the right until it has reached a predetermined position. The predetermined position is to be reached or approached in such a way that the interruption of the movement of the piston and thus the interruption of the movement of the masses driven by the piston is damped.
  • a compressed air control system (not shown) with corresponding valves first applies compressed air to the compressed air connection 59. This leads to the fact that the working pressure chamber 5 and the damping chamber 12 are also acted upon by compressed air. As soon as the actuating force generated in this way on the piston 14 in the right direction is the opposite direction Overcomes resistance forces (friction, load, etc.), the piston 14 is moved accelerated to the right. When the piston 14 moves to the right, it is checked in a manner not shown whether or when the additional piston 19 is in the predetermined position or whether or when the piston 14 is in a predetermined position or whether or when the piston 14 is in one of the predetermined positions Appropriate predetermined position upstream corresponding position or reached this.
  • the compressed air connection 26 is acted upon by compressed air via the aforementioned compressed air control system.
  • Compressed air is then applied to the Bresm pressure chamber 39 via the path of the compressed air comprising the compressed air line 23.
  • the brake elements 40 are brought into frictional engagement with the inner wall of the cylinder tube 48 and the additional piston 19 is stopped.
  • the additional piston 19 is stopped very quickly and very precisely.
  • the additional piston 19 fixed in this way then forms, as it were, a fixed wall on the side of the piston 14 not acted upon by the working pressure, which wall delimits the damping chamber 44.
  • the application of compressed air to the working pressure chamber 5 can be interrupted.
  • the piston 14 will - due to its and the masses moved by it - then continue to run to the right.
  • the volume of the damping chamber 44 is then reduced and the pressure in this damping chamber 44 is increased accordingly, since the lip seal 17 prevents venting of the damping chamber 44.
  • a pressure relief or venting of the damping chamber 44 takes place only via the throttle device (not shown) (corresponding to the throttle device 7, 8, 9 of the additional piston 49) and the check valve 41.
  • the damping chamber 44 is thus vented throttled due to the dynamic processes. This means that the movement of the piston 14 is braked in a damped manner. With a corresponding dimensioning of the throttle device adapted to the usual load and speed of movement of the piston 14, the piston 14 will finally come into contact with the additional piston 19 and thus reach the predetermined position in a damped manner.
  • pistons actuated by pressure medium can also be used. It is also possible to design the damping device for the piston 14 differently than in the manner described. So it is e.g. advantageously possible that the damping chamber is formed by a piston-like projection of the working piston or the additional piston and a recess of the additional piston or the working piston, the recess serving for the sealed reception of the piston-like projection.
  • the throttled venting of the damping chamber takes place in a manner similar to that in the exemplary embodiment described.
  • the damping chamber can also be formed instead of directly from the working piston by a pressure piece arranged on the corresponding side of the working piston and non-positively connected to the working piston.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Braking Arrangements (AREA)
  • Actuator (AREA)
EP84111136A 1983-10-26 1984-09-19 Vérin à fluide sous pression avec dispositif amortisseur fin de course pour le piston Expired EP0141215B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84111136T ATE25279T1 (de) 1983-10-26 1984-09-19 Druckmittelbetaetigbarer arbeitszylinder mit einer einrichtung zum daempfen der endabbremsung des arbeitskolbens.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19833338781 DE3338781A1 (de) 1983-10-26 1983-10-26 Druckmittelbetaetigbarer arbeitszylinder mit einer einrichtung zum daempfen der endabbremsung des arbeitskolbens
DE3338781 1983-10-26

Publications (2)

Publication Number Publication Date
EP0141215A1 true EP0141215A1 (fr) 1985-05-15
EP0141215B1 EP0141215B1 (fr) 1987-01-28

Family

ID=6212725

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84111136A Expired EP0141215B1 (fr) 1983-10-26 1984-09-19 Vérin à fluide sous pression avec dispositif amortisseur fin de course pour le piston

Country Status (4)

Country Link
US (1) US4633758A (fr)
EP (1) EP0141215B1 (fr)
AT (1) ATE25279T1 (fr)
DE (2) DE3338781A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4841846A (en) * 1986-02-24 1989-06-27 Grambling William D Pneumatic actuators with liquid seals for oil and gas well swabs
US5058385A (en) * 1989-12-22 1991-10-22 The United States Of America As Represented By The Secretary Of The Navy Pneumatic actuator with hydraulic control
US5730410A (en) * 1996-06-10 1998-03-24 Archambault; Marc-Antoine Ceiling mounted displaceable support arm for suspending a device
US5735122A (en) * 1996-11-29 1998-04-07 United Technologies Corporation Actuator with failfixed zero drift
US6135029A (en) * 1998-10-27 2000-10-24 Nexen Group, Inc. Linear motion brake
US6460678B1 (en) * 2000-10-24 2002-10-08 Nexen Group, Inc. Linear motion brake
US7124861B2 (en) 2004-02-20 2006-10-24 Nexen Group, Inc. Motion control apparatus
DE102005032297B4 (de) 2005-07-11 2018-02-01 Laeis Gmbh Hydraulische Presse mit Kolben-Zylinder-Anordnung
KR102185279B1 (ko) * 2014-03-05 2020-12-01 삼성전자 주식회사 단동형 공압 실린더
US9470285B2 (en) * 2014-04-08 2016-10-18 The Boeing Company Aircraft door dampening system
US10941790B2 (en) * 2017-03-15 2021-03-09 Seiko Instruments Inc. Cylinder device, press machine, workpiece clamping apparatus, cylinder device actuating method, method for clamping workpiece, and method for pressing workpiece

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3008454A (en) * 1959-04-03 1961-11-14 Ralph M Wilkins Locking actuator
US3072104A (en) * 1960-03-30 1963-01-08 Westinghouse Brake & Signal Cylinder with piston cushioning feature
GB922157A (en) * 1958-02-17 1963-03-27 Parsons Chain Company Ltd Improvements in and relating to telescopic struts
US3626807A (en) * 1969-10-21 1971-12-14 Kenneth B Shartzer Adjustable stroke cylinders
EP0106947A1 (fr) * 1982-10-22 1984-05-02 Mannesmann Rexroth Pneumatik Gmbh Vérin à double effet

Family Cites Families (20)

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US2394785A (en) * 1944-05-04 1946-02-12 American Locomotive Co Brake for power reverse gears
DE1754792U (de) * 1956-01-07 1957-10-24 Weserhuette Ag Eisenwerk Mit fluessigkeit betriebener druckzylinder.
GB940166A (en) * 1961-04-11 1963-10-23 Faiveley Sa Improvements in or relating to pneumatic motors
DE1576097B2 (de) * 1965-04-24 1970-07-09 Hänchen, Siegfried, 7304 Ruit Mechanische Verriegelung für einen Hydrozylinder
US3353455A (en) * 1965-09-20 1967-11-21 Westinghouse Air Brake Co Fluid pressure motor
DE1627852C3 (de) * 1967-06-08 1974-09-19 Josef 6200 Wiesbaden-Bierstadt Nemetz Hydropneumatischer Spannzylinder
DE6607298U (de) * 1967-10-07 1971-02-18 Dingler Werke Ag Sperrvorrichtung in form einer spreizringbremse fuer hydraulisch oder pneumatisch betaetigte verstellaggregate
US3665812A (en) * 1969-07-01 1972-05-30 Chukyo Electric Co Apparatus for controlling rectilinear motion
DE2041597A1 (de) * 1970-02-09 1971-08-19 Orsta Hydraulik Betr Hydraulik Bremseinrichtung fuer hydraulische oder pneumatische Arbeitszylinder mit ein- oder beidseitiger Endlagenbremsung
DE2027395A1 (de) * 1970-06-04 1971-12-09 Hennecke E Doppelt wirkender druckmittelbeaufschlagter Arbeitszylinder mit Endlagendämpfung
DE2128156A1 (de) * 1971-06-07 1972-12-28 Fortmeier J Strömungsmittelbetriebene Vorrichtung zum Verstellen eines Gliedes aus ejner in eine andere Lage
FR2220700B1 (fr) * 1973-03-08 1976-09-10 Poclain Sa
DE2334413A1 (de) * 1973-07-06 1975-01-30 Wabco Westinghouse Gmbh Pneumatischer stellantrieb
DE2336066A1 (de) * 1973-07-16 1975-02-06 Wabco Westinghouse Gmbh Pneumatischer stellantrieb
FR2321060A1 (fr) * 1975-08-12 1977-03-11 Bretagne Atel Chantiers Dispositif d'immobilisation d'un piston dans son cylindre
SU832143A1 (ru) * 1978-05-03 1981-05-23 Краснодарский политехнический институт Многопозиционный пневмо/гидро/цилиндр
FR2444827A1 (fr) * 1979-06-21 1980-07-18 Poclain Sa Verin a fluide muni d'un amortisseur de fin de course
SE452281B (sv) * 1980-02-05 1987-11-23 Aga Ab Sett och anordning for att sonderdela plast eller gummimaterial
FR2513340A1 (fr) * 1981-09-23 1983-03-25 Peugeot Piston a clapets pour amortisseur
DE3146998A1 (de) * 1981-11-27 1983-06-01 Wabco Steuerungstechnik GmbH & Co, 3000 Hannover Einrichtung zur endabbremsung des arbeitskolbens eines doppeltwirkenden arbeitszylinders

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB922157A (en) * 1958-02-17 1963-03-27 Parsons Chain Company Ltd Improvements in and relating to telescopic struts
US3008454A (en) * 1959-04-03 1961-11-14 Ralph M Wilkins Locking actuator
US3072104A (en) * 1960-03-30 1963-01-08 Westinghouse Brake & Signal Cylinder with piston cushioning feature
US3626807A (en) * 1969-10-21 1971-12-14 Kenneth B Shartzer Adjustable stroke cylinders
EP0106947A1 (fr) * 1982-10-22 1984-05-02 Mannesmann Rexroth Pneumatik Gmbh Vérin à double effet

Also Published As

Publication number Publication date
EP0141215B1 (fr) 1987-01-28
DE3462280D1 (en) 1987-03-05
ATE25279T1 (de) 1987-02-15
DE3338781A1 (de) 1985-05-09
US4633758A (en) 1987-01-06

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