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EP0638731B1 - Entraînement linéaire pneumatique à verrouillage en position déployée - Google Patents

Entraînement linéaire pneumatique à verrouillage en position déployée Download PDF

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Publication number
EP0638731B1
EP0638731B1 EP94110397A EP94110397A EP0638731B1 EP 0638731 B1 EP0638731 B1 EP 0638731B1 EP 94110397 A EP94110397 A EP 94110397A EP 94110397 A EP94110397 A EP 94110397A EP 0638731 B1 EP0638731 B1 EP 0638731B1
Authority
EP
European Patent Office
Prior art keywords
piston
control rod
rod
valve
linear drive
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 - Lifetime
Application number
EP94110397A
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German (de)
English (en)
Other versions
EP0638731A1 (fr
Inventor
Markus Dipl.-Ing. Horstmann
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.)
Airbus Defence and Space GmbH
Original Assignee
Daimler Benz Aerospace AG
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 Daimler Benz Aerospace AG filed Critical Daimler Benz Aerospace AG
Publication of EP0638731A1 publication Critical patent/EP0638731A1/fr
Application granted granted Critical
Publication of EP0638731B1 publication Critical patent/EP0638731B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B15/261—Locking mechanisms using positive interengagement, e.g. balls and grooves, for locking in the end positions

Definitions

  • the invention relates to a linear drive with a single-acting, pneumatic piston / cylinder unit and with at least one spring which counteracts the pneumatic force and loads the piston rod in the direction of an end position.
  • a linear drive with all the generic features of the present invention is known from DE-PS 42 21 230.
  • the locking in both end positions of the drive is carried out by a pneumatically operated locking link that is movable transversely to the piston rod and can be snapped into a recess in the piston rod from diametrical sides.
  • a first, smaller control piston which is responsible for locking in the pneumatically inactive end position of the drive, is rigidly connected to the locking link.
  • a second, larger control piston is located on the opposite side of the piston rod and transmits its actuating force to the locking link in a spring-elastic manner. This is responsible for locking in the pneumatically active end position of the drive.
  • the piston / cylinder unit is also pneumatically actuated via a mostly open flow connection.
  • a valve device (valve piston, spring finger, throttle channel, etc.) is coupled to the second, larger control piston, which temporarily releases an additional flow cross section when the piston / cylinder unit is vented and thus increases the overall flow cross section. This allows the movement of the piston rod to be accelerated in one direction (from the pneumatically active to the inactive end position), or throttling effects can be compensated for by the cryogenic pressure medium (gap reduction, higher viscosity of the flow, etc.).
  • this linear drive is relatively compact, light, uncomplicated, reliable and suitable for the operating conditions in the vicinity of rocket engines.
  • the object of the invention is to provide a generic linear drive which is still more compact, simple, reliable and easy to maintain with at least largely the same functionality.
  • the locking link is actuated only by an actuating rod and by a double piston separating the two pressure chambers.
  • the force transmission from the double piston to the actuating rod is resilient in both directions, the forces also being at least largely the same in size.
  • the pneumatic system is on one side of the piston rod and is therefore more compact, easier, more reliable and easier to maintain.
  • the design and arrangement of the one-way flow control valve in the area between the locking link and the double piston also contributes to this.
  • the sub-claims 2 to 5 contain preferred embodiments of the linear drive according to claim 1.
  • the linear drive 1 is an essential component of a rocket fuel valve, not shown with regard to its other components, through which liquid hydrogen or liquid oxygen flows, for example.
  • the pressure medium to be used for the actuation must neither condense nor freeze at the extremely low fuel temperatures and should be inert in the event of possible contact with the fuel. These conditions are also met by the particularly low-weight gas helium.
  • the housing 2 encloses or carries both the elements required for the valve actuation, ie the piston / cylinder unit 3 and the spring 11, and the locking mechanism, ie in particular the Locking link 12, the actuating rod 13 and the double piston 20.
  • the locking and unlocking movement takes place vertically, the valve movement horizontally.
  • the valve cone and seat would be in the area of the left end of the piston rod.
  • the piston / cylinder unit 3 comprises in particular the cylinder 4, the piston 5, which is movably sealed in the cylinder 4 by means of a sealing ring 6, the piston rod 7 provided with two axially offset, diametrical recesses 8, 9, and the sliding bushing 10 which guides and seals the piston rod 7 .
  • the right end of the piston-piston / cylinder unit 3 with cylinder cover, piston rod bushing, ventilation, etc. is not shown for the sake of simplicity. It goes without saying that the entire housing 2 actually consists - for manufacturing and assembly reasons - of a large number of individual parts, seals, screw connections, centerings, etc. In the figures, the housing 2 is shown as an integral block for the sake of clarity. The same also applies to other components, such as the actuating rod 13 and the double piston 20.
  • the essence of the invention is, of course, in the design and type of locking, including the pressure gas guide.
  • the locking link 12 which engages around the piston rod 7 or, for example as a perforated plate, surrounds on all sides, serves as a locking element, which snaps into the recesses 8, 9 of the piston rod 7.
  • the power transmission to the locking link 12 takes place via the actuating rod 13 which is firmly connected thereto and extends into the region of the double piston 20.
  • the double piston 20 converts the pneumatic pressure into a mechanical axial force and for this purpose extends into two pressure chambers 31 and 32 which can be ventilated and vented separately and which have openings 33, 34 leading to external connections (not shown).
  • the double piston 20 is provided with a cylindrical cavity 26, in which two bushings 28, 29 are axially displaceable to a limited extent, and which has an opening 27 for the actuating rod 13.
  • the bushings 28, 29 are held at a distance by a compression spring 30 and interact with a stop surface 14, 15 on the actuating rod 13.
  • the flow of force runs from the double piston via the first bushing, the compression spring and the second bushing to the stop surface on the actuating rod, the compression spring 30 forming the elastic link. This applies to downward and upward piston forces.
  • the double piston 20 is slidably sealed in the housing 2 by means of the seal 25, furthermore the seals 23, 24 are effective in its stop surfaces 21, 22 in their two end positions, which rest on elevations of the inner housing surface.
  • the lower pressure chamber 32 is permanently fluid-mechanically connected to the space on the left of the piston 5 inside the cylinder 4, but the available flow cross sections vary with time.
  • the opening 17 is molded into an exchangeable calibration insert 19 and can be varied in a targeted manner by exchanging the same.
  • Both the guidance of the locking link 12 in the housing 2 and the housing opening for the piston rod 7 are on the right of the locking link 12 designed to be gas permeable.
  • the opening 17 plunges into the guide bore of the valve piston 36 of the throttle check valve 35 in certain operating states.
  • there is a clearance fit here which is also not gas-tight. In the figures, this is indicated by a radial gap.
  • the guide bore of the valve piston 36 can also be designed in a targeted manner with grooves, grooves, etc. in the longitudinal direction.
  • the sliding bush 43 also does not enclose and guide the actuating rod 13 in a gastight manner.
  • the throttle check valve 35 has the task of temporarily increasing the flow cross section when venting the piston / cylinder unit 3. This state is shown in Fig. 2.
  • the valve piston 36 lifts against the force of the compression spring 38 from the seal 41 in the stop surface 40 until it abuts the stop surface 39 in the housing 2.
  • the pressure medium can thus flow rapidly through the flow gap 42 and through the passage openings 37 to the pressure chamber 32. If desired, this accelerates the closing of the fuel valve.
  • the effect is compensated that in the pneumatically active state of the piston / cylinder unit 3, the heat and capacity of the cryogenic pressure medium reduce the clearances and gaps and thus also the flow cross sections between the components, which would result in increased flow resistance, i.e. a slowed piston rod movement.
  • Fig. 1 shows the pneumatically active, locked end position.
  • the locking link 12 is located in the recess 9 of the piston rod 7 and would inadvertently close the pneumatic pressure in the event of failure Prevent fuel valves.
  • the pressurization of the lower pressure chamber 32 and thus of the piston 5 is indicated by a white arrow at the opening 34.
  • Fig. 2 shows an intermediate position in the transition movement from the active to the passive end position.
  • the piston movement is indicated by a black arrow.
  • the upper pressure chamber 31 is pressurized, the lower pressure chamber 32 and thus the piston / cylinder unit 3 are vented.
  • the pressure medium flowing back has opened the throttle check valve 35 and thus has additional flow cross sections (passage openings 37 etc.).
  • the locking link is under spring force (compression spring 30) from above on the piston rod 7 and dampens any vibrations that may occur. It can be seen that the lower bush 29 is displaced upwards in the double piston 20, but is not in contact with the upper bush 28, as a result of which the power transmission is still elastically flexible.
  • Fig. 3 shows the pneumatically passive, locked end position.
  • the locking link 12 is located in the recess 8 of the piston rod 7 and prevents unwanted opening of the fuel valve. Only the upper pressure chamber 31 is pressurized (see white arrow).

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)

Claims (5)

  1. Dispositif d'entraînement linéaire (1), en particulier pour des valves de commande cryogènes dans des conduites de propergol liquide de moteurs-fusées, comprenant un ensemble piston/cylindre ou vérin pneumatique (3) à simple effet, au moins un ressort (11) agissant à l'encontre de la force pneumatique et sollicitant la tige de piston (7) en direction d'une position de fin de course, une coulisse de verrouillage (12) mobile transversalement à la tige de piston (7), susceptible d'être encliquetée depuis des côtés diamétraux dans une parmi deux échancrures (8, 9) de la tige de piston, et actionnée pneumatiquement en passant par au moins un piston de commande (20), deux chambres de pression (31, 32) séparées, susceptibles d'être mises sous pression et déchargées, pour l'actionnement de la coulisse de verrouillage (12), une communication de fluide ouverte au moins dans la plupart des conditions de fonctionnement, entre l'une (32) de ces deux chambres de pression et le côté, sollicité par le fluide sous pression, du piston (5) du vérin (3), et une valve (35) dans cette communication de fluide, laquelle valve accroît temporairement la section d'écoulement lors de la décharge de cette chambre de pression (32) et donc du vérin (3), caractérisé par :
    a) une tige de réglage (13) reliée rigidement à la coulisse de verrouillage (12) et actionnant cette dernière,
    b) un piston double (20) qui actionne l'extrémité de la tige de réglage (13), éloignée de la coulisse, qui pénètre dans les deux chambres de pression (31, 32) et qui sépare ces dernières de façon étanche l'une de l'autre,
    c) la prévision, entre l'extrémité de la tige de réglage (13) éloignée de la coulisse et le piston double (20), d'une liaison à mobilité axiale limitée (cavité 26, douilles 28, 29, surfaces de butée 14, 15) dans la direction longitudinale de la tige de réglage (13), dans le sens d'éloignement de et de rapprochement de la coulisse de verrouillage (12), cette liaison étant élastique (ressort de compression (30)) jusqu'à l'appui contre des butées,
    d) une communication de fluide permanente entre la chambre de pression (32) et le vérin (3), et
    e) la réalisation de la valve accroissant temporairement la section d'écoulement de cette communication de fluide, en tant que clapet anti-retour à étranglement (35) et la disposition de ce clapet dans la zone de la tige de réglage (13) entre le piston double (20) et la coulisse de verrouillage (12).
  2. Dispositif d'entraînement linéaire suivant la revendication 1, caractérisé par le fait que :
    - le piston double (20) présente intérieurement une cavité (26) cylindrique, fermée sur un côté frontal et munie d'une ouverture centrale (27) sur l'autre côté frontal,
    - deux douilles (28, 29) sont disposées dans ladite cavité (26) l'une derrière l'autre, avec mobilité limitée en translation axiale,
    - au moins un ressort de compression (30) disposé entre lesdites douilles (28, 29), et
    - la prévision sur la tige de réglage (13) pénétrant dans ladite cavité (26), de deux surfaces de butée (14, 15) coopérant avec les douilles (28, 29).
  3. Dispositif d'entraînement linéaire suivant la revendication 1 ou 2, caractérisé par :
    - un clapet anti-retour à étranglement (35) comprenant un piston de clapet (36) entourant concentriquement la tige de réglage (13) et déplaçable en translation axiale sur cette dernière,
    - une fente d'écoulement (42) annulaire entre le piston de clapet (36) et le carter (2),
    - plusieurs ouvertures de passage (37) dans le piston de clapet (36),
    - deux surfaces de butée (39, 40) disposées dans le carter (2), limitant le mouvement du piston de clapet (36) et munies le cas échéant d'un joint supplémentaire (41),
    - au moins un ressort de compression (38) sollicitant le piston de clapet (36) en direction de la coulisse de verrouillage (12), et
    - un canal d'écoulement axial (16) à l'intérieur de la tige de réglage (13) et deux ouvertures (17, 18) menant vers le côté extérieur de la tige de réglage (13) dans la zone du clapet anti-retour à étranglement (35), ouvertures dont au moins une est calibrée (insert de calibrage (19)).
  4. Dispositif d'entraînement linéaire suivant une ou plusieurs des revendications 1 à 4, caractérisé par le fait que le piston double (20) présente deux surfaces de butée (21) coopérant avec le carter (2) et munies chacune d'un joint supplémentaire (23, 24).
  5. Dispositif d'entraînement linéaire suivant une ou plusieurs des revendications 1 à 4, caractérisé par le fait que la coulisse de verrouillage comporte un prolongement dépassant dans la direction longitudinale de la tige de piston et pénétrant, lorsque le vérin est verrouillé dans la position de fin de course pneumatiquement active et lors d'une défaillance de pression dans le système pneumatique, dans un creux correspondant dans l'échancrure de la tige de piston.
EP94110397A 1993-07-16 1994-07-04 Entraînement linéaire pneumatique à verrouillage en position déployée Expired - Lifetime EP0638731B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4323846 1993-07-16
DE4323846A DE4323846C1 (de) 1993-07-16 1993-07-16 Pneumatischer Linearantrieb mit Endlagenverriegelung

Publications (2)

Publication Number Publication Date
EP0638731A1 EP0638731A1 (fr) 1995-02-15
EP0638731B1 true EP0638731B1 (fr) 1996-09-25

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EP94110397A Expired - Lifetime EP0638731B1 (fr) 1993-07-16 1994-07-04 Entraînement linéaire pneumatique à verrouillage en position déployée

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EP (1) EP0638731B1 (fr)
DE (2) DE4323846C1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022107278A1 (de) 2022-03-28 2023-09-28 Zf Cv Systems Europe Bv Aktuator eines automatisierten Schaltgetriebes

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FR2735539B1 (fr) * 1995-06-16 1997-08-22 Henri Berthier Verin a fluide sous pression a double effet comportant un verrouillage de la tige de son piston
DE19828199C2 (de) * 1998-06-25 2000-04-20 Daimler Chrysler Ag Absperrventil
DE19841631C2 (de) 1998-09-11 2002-02-28 Daimler Chrysler Ag Pneumatischer Linearantrieb für kryogene Steuerventile
DE102008022509A1 (de) * 2008-05-07 2009-11-12 Robert Bosch Gmbh Wegeventil mit einer Rastvorrichtung
CN102400973B (zh) * 2011-11-18 2015-07-08 北京市三一重机有限公司 一种液压油缸
WO2013104707A2 (fr) * 2012-01-13 2013-07-18 Norgren Gmbh Réglage de position et verrouillage de position d'un actionneur commandé par fluide
BR112014017678B1 (pt) * 2012-01-20 2021-10-26 Naf Ab Atuador de válvula acionável pneumaticamente e método de bloquear um elemento de fechamento de válvula em relação a um corpo de válvula
DE102013214188B4 (de) * 2013-07-19 2025-06-26 Zf Friedrichshafen Ag Vorrichtung zum Betätigen eines Verriegelungsmechanismus, insbesondere zum Betätigen einer Parksperreneinrichtung
CN103750658A (zh) * 2014-02-08 2014-04-30 北京北方车辆集团有限公司 一种电动斜抽拉式抽屉
DE102017126196A1 (de) * 2017-11-09 2019-05-09 Arianegroup Gmbh Federunterstützter, verriegelbarer Linearantrieb und ein damit ausgestattetes Ventil
CN112610562B (zh) * 2020-12-30 2023-02-24 三一海洋重工有限公司 油缸锁止装置和油缸

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US2130618A (en) * 1936-09-03 1938-09-20 Westinghouse Air Brake Co Fluid pressure motor and locking means therefor
US2908251A (en) * 1955-05-13 1959-10-13 Gratzmuller Jean Louis Single acting hydraulic motor
DE3609765A1 (de) * 1986-03-22 1987-09-24 Colt Int Holdings Druckmittelbetaetigbarer hubzylinder fuer vorzugsweise entlueftungseinrichtungen
DE3913009C2 (de) * 1989-04-20 1994-08-11 Wolfgang Dipl Ing Niemann Pneumatik-Zylinder mit Endstellungs-Verriegelung
DE4221230C1 (fr) * 1992-06-27 1993-07-08 Messerschmitt-Boelkow-Blohm Ag, 8012 Ottobrunn, De

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102022107278A1 (de) 2022-03-28 2023-09-28 Zf Cv Systems Europe Bv Aktuator eines automatisierten Schaltgetriebes

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Publication number Publication date
DE4323846C1 (de) 1994-11-10
DE59400735D1 (de) 1996-10-31
EP0638731A1 (fr) 1995-02-15

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