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EP0433955B1 - Vérin hydraulique muni d'un mécanisme de blocage - Google Patents

Vérin hydraulique muni d'un mécanisme de blocage Download PDF

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Publication number
EP0433955B1
EP0433955B1 EP90124490A EP90124490A EP0433955B1 EP 0433955 B1 EP0433955 B1 EP 0433955B1 EP 90124490 A EP90124490 A EP 90124490A EP 90124490 A EP90124490 A EP 90124490A EP 0433955 B1 EP0433955 B1 EP 0433955B1
Authority
EP
European Patent Office
Prior art keywords
piston
locking
working
space
hydraulic cylinder
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
EP90124490A
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German (de)
English (en)
Other versions
EP0433955A1 (fr
Inventor
Georg Dipl.-Ing. Koch
Wolfgang Traupe
Frank Dipl.-Ing. Van De Poel
Kurt Schaible
Holger Dipl.-Ing. Seel
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.)
Hyco Pacoma GmbH
Original Assignee
Pacoma Hydraulik 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 Pacoma Hydraulik GmbH filed Critical Pacoma Hydraulik GmbH
Publication of EP0433955A1 publication Critical patent/EP0433955A1/fr
Application granted granted Critical
Publication of EP0433955B1 publication Critical patent/EP0433955B1/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 lockable hydraulic cylinder with a housing with at least one pressure connection, a displaceable working piston guided in a sealed manner in the housing with a piston rod, a locking piston supported on a locking spring and a ball lock with in a cage radially in the locking position in a locking groove or balls movable in the release position in an escape groove, the working piston following a working space on a working effective surface and the locking piston following a releasing space on a releasing effective surface can be acted upon via the pressure connection.
  • Such lockable hydraulic cylinders are used to actuate a consumer, which can consist, for example, of a cover, a lever or another part, which is ultimately articulated on the piston rod of the working piston and can be actuated in this respect by pressurizing the working piston.
  • the working piston of the hydraulic cylinder can be actuated on one or both sides. Operation in a differential circuit is also possible.
  • the present invention is not dependent on all of these possibilities. It is only important that the starting point of the working piston can be mechanically positively locked, which is effective in the unpressurized state, ie in the absence of pressurization via the pressure connection.
  • the locking position must also be safely accessible when the working piston returns to its initial position, which is either in a double-acting hydraulic cylinder by pressurizing the piston rod side and / or by the action of z.
  • a weight of the consumer on the piston rod may be the case.
  • Lockable hydraulic cylinders of the type described above are known from DE-PS 29 11 071 and DE-A 37 32 561.
  • the hydraulic cylinder according to DE-A 29 11 071 has a working piston which is guided in the housing and which, following a working space, has a working working surface which can be acted upon directly by hydraulic pressure via the pressure connection on the housing.
  • An extension of the working piston is designed as a cage for the balls of a ball ratchet and is surrounded by a sleeve-like locking piston which is supported on the rear side on a locking spring.
  • the locking piston can also be acted upon from the pressure connection on a release active surface following a release space via a branch line, so that the pressure build-up in the work space and in the release space takes place simultaneously.
  • the working piston cannot yet leave its starting position because the ball lock is still in the locking position. Only after the locking piston has moved from the locking position into the release position against the force of the locking spring can the balls of the ball lock move radially outwards out of the locking groove into the escape groove and only then can the working piston make its stroke.
  • the immediate action on the working piston on the working surface when pressurized via the pressure connection leads to the balls of the ball lock being loaded with force and to a certain extent clamped in the locking position of the ball lock, because the working piston transmits a tensile force via the balls, but still its starting position can't leave.
  • the locking piston Due to the sudden pressurization of the locking piston over its entire release active surface, the locking piston is accelerated into the release position and the balls of the ball ratchet also jump suddenly and suddenly radially outwards, so that the working piston also suddenly starts to move. In many cases this is undesirable or even for the Adversely affecting consumers.
  • Another disadvantage is that the rear space of the locking piston, in which the locking spring is located, is not vented, so that there is a risk of hydraulic locking of the ball ratchet if, for. B. passes over a leaking seal of the locking piston hydraulic medium in the back space and fills it. In this case, the ball lock can no longer be unlocked hydraulically. The entire hydraulic cylinder then fails.
  • a double-acting, lockable hydraulic cylinder is also known with the features specified in the preamble of the claim.
  • Both a locking piston and a working piston are acted upon via a pressure connection.
  • a positively controlled shut-off valve is switched on, which prevents the working piston from being acted upon in its closed position and enables an unthrottled acting upon the working piston in its open position.
  • the positive control of this check valve is designed so that it is controlled via a shoulder depending on the movement of the locking piston.
  • the shut-off valve is opened, so that subsequently a pressure build-up on the working piston takes place until the full control pressure is reached, so that the working piston sets in motion according to the pressure build-up after unlocking the ball ratchet.
  • a lockable hydraulic cylinder in which a locking piston can be acted upon via a first pressure connection and a working piston can be acted upon via a second pressure connection.
  • a check valve is switched on, which is designed in the manner of a slide valve.
  • the valve body of the check valve has an extension, via which the check valve is controlled as a function of the movement of the locking piston.
  • the check valve has a closed position and an open position, so that pressure medium can only pass into the working space of the working piston in the open position.
  • the locking piston is supported on a locking spring and has an active surface which is provided in connection with a release space. The release space can be acted upon unthrottled via the separate pressure connection, so that the shut-off valve also switches suddenly from its closed position to the open position, which results in a corresponding starting process for the working piston.
  • the present invention aims to avoid the problem of abrupt starting of the working piston when pressure is applied and to achieve a smooth starting of the working piston from the starting position.
  • this is achieved in that a throttle with a time-delayed throttle function is provided between the pressure connection and the working space of the working piston, while the release space of the locking piston can be acted upon unthrottled via the pressure connection, so that when the pressure connection is acted upon, the locking piston first leaves the locking position and Only then does the pressure build up in the work area.
  • a throttle with a time-delayed throttle function is provided between the pressure connection and the working space of the working piston, while the release space of the locking piston can be acted upon unthrottled via the pressure connection, so that when the pressure connection is acted upon, the locking piston first leaves the locking position and Only then does the pressure build up in the work area.
  • the point in time at which the throttling function is switched off can be determined by the axial length of the throttle, depending on a corresponding stroke of the locking piston. This ensures in any case that the throttling function only then is switched off when the locking piston has actually left its locking position. The throttling function is switched off before the locking piston has reached its complete release position.
  • the adjustment is also made to the movement geometry and the movement speed of the parts of the ball ratchet. This ensures that the balls of the ball ratchet can leave the locking position without the action of a significant tensile force by the working piston and the pressure build-up in the working area is initially throttled, but then unthrottled, so that the working piston moves gently but then with the required actuation force. as it is necessary for the actuation of the consumer, starts or carries out his stroke.
  • the locking piston can be designed as a stepped piston and, on the one piston side, in addition to the release active surface, can also have a second active surface which can be acted upon by the pressure in the working space.
  • the release active surface must in any case be designed so large that the force of the locking spring is overcome in the unthrottled action via the pressure connection and the locking piston is safely transferred from the locked position to the release position solely by this action.
  • the locking piston can have a second active surface, via which it is then also acted upon from the working space, so that the locking piston is held securely in the release position during the forward stroke of the working piston.
  • the step on the step piston can also be used to form functional components of the ball lock.
  • a check valve can be provided between the working space and the pressure connection, which opens in the direction of the pressure connection and in a valve that bridges the throttle Line is arranged. This line connects the pressure connection or the release space with the work space and bridges the throttle.
  • the check valve opens in the direction of the pressure connection and serves to allow the volume of the hydraulic medium in the working space to flow back into the starting position into the pressure connection during the backward movement of the working piston.
  • the working piston moves into its locked starting position and the previously deactivated throttle function of the throttle comes back into action, so that the hydraulic medium can be accelerated out of the working space via the opening check valve into the pressure connection and the control line connected there.
  • the check valve is only required if this function is desired.
  • the check valve and its associated bypass line can also be dispensed with if throttled displacement of the hydraulic medium out of the working space is desired in order to achieve the starting position of the working piston in which it is locked. In such special cases, the reinserting throttle function of the throttle can be used meaningfully for this second function.
  • the check valve can be arranged in the locking piston. Sufficient space is generally available here, in particular if the locking piston is a piston with a circular cross section - in contrast to a sleeve-shaped locking piston with a circular cross section.
  • a bypass line on the housing side, which connects the pressure connection to the work space, bridges the throttle and contains the check valve.
  • the throttle with a throttle function that can be switched off with a time delay can be formed by a throttle gap between a cylinder section on the locking piston and a bore in the housing or a part arranged in a stationary manner in the housing. This means that no separate component is required to form the throttle with a throttle function that can be switched off with a time delay.
  • the length of the overlap between the cylinder section and the bore is only determined in accordance with the desired time delay, i.e. the point in time at which the cylinder section has completely moved out of the bore with a corresponding stroke of the locking piston, so that the throttling effect is eliminated and the work space subsequently is acted upon unthrottled.
  • the throttle gap itself, the throttled pressure build-up in the work area can be influenced.
  • the locking spring of the locking piston can be arranged in a space connected to the atmosphere. This means that this space is vented and leaks through the seal of the locking piston can no longer lead to hydraulic locking of the ball lock. This increases operational safety. On the other hand, it is ensured that the ball lock can also leave its locked position and that there is a guarantee that the working piston can also perform its proper stroke.
  • the locking piston can have an extension on the side facing away from the working piston, on which the locking piston can be displaced from the locking position into the release position by a mechanical force application.
  • a mechanical force application for some applications, it is necessary or desirable that the locking position of the hydraulic cylinder can be released by a manual application of force in the event of hydraulic pressure failure further manual actuation, e.g. B. the consumer to be able to bring about the intended actuation despite the absence of hydraulic pressure.
  • the ball lock must first be unlocked.
  • the extension on the locking piston permits a mechanical application of force, by means of which the locking piston is transferred from its locking position into the release position, the ball ratchet being released and the working piston thus becoming movable.
  • the locking piston can be arranged to be movable in the opposite direction to the working piston, connect with its second active surface to the working space and the locking spring can be arranged in the vented space on the other side of the locking piston.
  • the space in which the locking spring is arranged is connected to the atmosphere in a very simple manner. Any seal on the extension is missing here.
  • the locking piston if the locking piston can be transferred in the same direction as the working piston from the locking position into the release position, venting is generally somewhat more difficult. The vent can also be routed through the working piston.
  • a connection of the rear space to the rear space of the working piston is also possible; it must be ensured that the hydraulic cylinder is not operated in a differential circuit, because otherwise the ball lock cannot be released. If, on the other hand, the hydraulic cylinder is also operated in a differential circuit, ventilation of the rear space of the locking piston should be achieved in another way, e.g. B. through a longitudinal bore in the piston rod.
  • the extension of the locking piston can have an externally accessible groove for mechanical force application, so that it is possible to move the locking piston from the locking position into the release position.
  • the working piston can have an extension sleeve for receiving the balls of the ball ratchet, a locking bushing which carries the locking groove being arranged in a stationary manner in the housing. By dimensioning the locking bush in the radial direction, care can be taken that the balls of the ball ratchet do not rub against the cylindrical bore of the housing when the working piston executes its stroke.
  • the hydraulic cylinder according to FIGS. 1 and 2 has a housing 1, in the bore 2 of which a working piston 3 is slidably and sealingly guided by means of seal 4 and guide ring 5.
  • a working piston 3 On the working piston 3 is one Piston rod 6 attached, for example screwed, which is led out of the housing 1 at its other end, not shown, and is operatively connected there to a consumer, which is actuated in this way.
  • a pressure connection 7 is provided on the housing, to which a control line for a pressure medium can be connected, as is required, among other things, for actuating the working piston 3. Only a pressure connection 7 is shown here and a single-acting working piston 3 is described. It is not disadvantageous for the invention if a double-acting design and correspondingly several connections for the pressure medium are provided.
  • a locking bushing 8 is mounted in a fixed manner in a shoulder of the bore 2 and sealed to the outside with the aid of a seal 9. The locking bush 8 is held by a cover part 10 inserted into the housing 1, wherein the cover part 10 can also be designed in a different way or can also be welded or otherwise connected to the housing 1.
  • a locking piston 11 is mounted to be displaceable to a limited extent and is sealingly guided by a seal 12. The displaceability of the locking piston 11 is limited by stops. Between the locking piston 11 and the locking bush 8, a release space 13 is formed, which is in permanent connection with the pressure connection 7. Adjacent to the release space 13, the locking piston has a release active surface 14 which, as can be seen, is designed as an annular surface.
  • the locking piston 11 also has a cylinder section 15 to which a bore 16 on the locking bush 8 is assigned.
  • a throttle 17 in the form of a correspondingly dimensioned throttle gap is formed by the cylinder section 15 and the bore 16, the radial gap width and the axial gap length determining the throttle function.
  • the throttle 17 represents a connection between the release space 13 and a working space 18, which is otherwise formed between the locking piston 11 and the working piston 3. Pressure medium from the release space 13 and thus from the pressure connection 7 can only reach the working space 18 via the throttle 17.
  • the working piston 3 has a working working surface 19 following the working space 18, the application of which to hydraulic medium is essentially responsible for the stroke of the working piston 3.
  • the locking piston 11 not only has the release active surface 14, but on the same side on the end face following the working space 18 and beyond the throttle 17, a second active surface 20, which is designed as a circular active surface and extends radially approximately up to the throttle 17.
  • the locking piston has a blocking cylinder 21 and an escape groove 22, which effectively belong to a ball ratchet 23, with the aid of which the working piston 3 is mechanically blocked in the starting position shown in FIG. 1 (pressure connection 7 without pressure).
  • the ball ratchet 23 includes a cage-like extension sleeve 24, which serves to receive and guide balls 25, which are mounted in several radially guided conical individual recesses distributed over the circumference of the extension sleeve 24.
  • the storage is such that the balls 25 are only radially movable with respect to the extension sleeve 24.
  • a locking groove 26 is incorporated, which is intended for receiving the balls 25 in the locking position. In this locking position, which is shown in FIG. 1, the balls 25 have entered the locking groove 26 and are prevented by the relative position of the locking piston 11 shown via the locking cylinder 21 from radially deflecting inwards.
  • a check valve 27 is provided, which, as shown, has a spring-supported locking ball which is set against a seat 28 which is screwed into the locking piston 11 in the closed position.
  • a radially guided bore 29 and an axial channel 30 together form a line 29, 30, in which the check valve 27 is arranged.
  • the line 29, 30 connects the working space 18 with the release space 13 and thereby bridges the other connection between these two spaces via the throttle 17.
  • the installation direction of the check valve 27 ensures that only pressure medium from the working space 18 via the line 29, 30 in the release space 13 and thus the pressure port 7 returned, but can never be introduced in the opposite direction.
  • the locking piston 11 has on the other side of the seal 12 an extension 31 which is passed through the cover part 10 without a further seal and ends in the region of a recess 32 through which a groove 33 provided on the extension 31 is accessible from the outside.
  • This can be a mechanical force attack on the extension 31 of the locking piston 11 from the outside, whereby the locking piston 11 can be moved according to the intended axial mobility even when z. B. the print medium has failed via the pressure connection 7 or is not available.
  • a space 34 is formed on the housing side, which is in permanent communication with the atmosphere via the unsealed extension 31, ie is vented.
  • a locking spring 35 is supported on the housing side, which loads the locking piston 11 so that the ball lock 23 is in the locked position, the locking cylinder 21 preventing the balls 25 from the locking groove 26 radially to dodge inside.
  • FIG. 1 The normal starting position or rest position of the working piston 3 with the locked ball lock 23 is shown in FIG. 1. If hydraulic medium is now brought under pressure via a control line (not shown) and the pressure connection 7, a corresponding pressure builds up in the release space 13, while the action on the working space 18 is restricted by the throttle 17. Due to the force acting on the release active surface 14 of the locking piston 11, the locking piston 11 is transferred from the locking position to the release position (FIG. 2), overcoming the force of the locking spring 35, and it lies against the cover part 10, which acts here as a stop. Since the pressure of the hydraulic medium via the throttle 17 with the corresponding throttling action can build up comparatively little, no noteworthy force acts on the working piston 3 or its working working surface 19 at this point in time.
  • the balls 25 of the ball ratchet 23 can thus easily emerge from the locking groove 26 in the course of the movement of the locking piston 11, as soon as the escape groove 22 faces the balls 25, so that the ball ratchet 23 and in this respect release the mechanical locking of the working piston 3 and radially inwards dodge according to the escape groove 22.
  • the cylinder section 15 of the locking piston 11 has moved out of the bore 16 of the locking bush 8, so that the throttle function of the throttle 17 is thus switched off.
  • the narrow cross section has been eliminated and the full control pressure of the hydraulic medium can now build up and have an effect in the working space 18.
  • the ball ratchet 23 is first released and only then does the full control pressure build up on the working effective surface 19 of the working piston 3, so that the working piston 3 starts to move smoothly after the ball ratchet 23 is released.
  • the full control pressure acts on the working piston 3, so that it is able to actuate the connected consumer according to its design.
  • Figure 2 shows this position after the working piston 3 has covered a partial stroke.
  • the locking piston 11 is held in its release position (FIG. 2) by compressing the locking spring 35.
  • the balls 25 cannot fall radially inward into the working space 18 due to the special cage-like design. Special precautions can also be taken, as is clear from the second exemplary embodiment, which prevent the balls 25 from falling radially inwards or outwards.
  • the check valve 27 now opens, so that the pressure reduction and the overflow of hydraulic medium from the work space 18 into the release space 13 and thus into the pressure connection 7 can take place via this line 29, 30 and the open check valve 27. If the backward movement of the working piston 3 is also to take place very gently and gradually, the check valve 27 and the line 29, 30 can of course be missing.
  • the ball lock 23 can be released by mechanical force application on the groove 33 of the extension 31.
  • the locking piston 11 is pulled back against the force of the locking spring 35 into the release position, so that the working piston 3 is unlocked and, for example, an additional stroke of the working piston 3 can be carried out by further force application to the consumer or to the piston rod 6.
  • the working piston 3 can also be returned to its starting position, the mechanical locking also taking place in this case via the ball ratchet 23.
  • FIGS. 3 and 4 The exemplary embodiment in FIGS. 3 and 4 is fundamentally similar, at least in functional terms, which is why identical or functionally comparable parts are provided with the same reference symbols. While in the exemplary embodiment in FIGS. 1 and 2 the working piston 3 and the locking piston 11 could be actuated hydraulically in opposite directions, in the exemplary embodiment in FIGS. 3 and 4 these two parts can be actuated in the same direction. Accordingly, the space 34, in which the locking spring 35 is arranged, is provided here on the other side, that is to say toward the working piston 3, with ventilation being possible in the case of a single-acting piston via a channel 36 to the space on the piston rod side. If, on the other hand, the hydraulic piston is operated in a double-acting manner, venting of the space 34 must take place in a different way, e.g. B. via the piston rod 6.
  • a pin 37 is sealingly mounted in the cover part 10 with the aid of a seal 38, which can be pressed in manually and then rests on the locking piston 11 and transfers it from the locking position into the release position.
  • the balls 25 need not be radially movably supported in the extension sleeve 24. They can be freely movable in openings in the extension sleeve 24. If they fall out in the release position, they are held on the one hand by the locking piston 11 and its cylinder section 15.
  • a protective sleeve 40 is provided, which is supported on a spring 39 and which prevents the balls 25 from radially outwards from the openings in the extension sleeve 24 during the forward and backward stroke of the working piston 3.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)

Claims (10)

  1. Vérin hydraulique pouvant être actionné au moins d'un côté et pouvant être verrouillé, avec un boîtier (1) avec un raccord de pression (7), un piston de travail (3) guidé de manière étanche et coulissante dans le boîtier, avec une tige de piston (6), un piston de verrouillage (11) appuyé sur un ressort de verrouillage (35) et un verrou à billes (23) avec des billes (25) mobiles radialement dans une cage entre une position de verrouillage dans une gorge de verrouillage (26) et une position de dégagement dans une gorge d'évitement (22), le piston de travail (3) pouvant être soumis à la pression venant du raccord (7), en étant relié à une chambre de travail (18) par une surface active de travail (19) et le piston de verrouillage (11) pouvant être soumis à la pression venant du raccord (7) en étant relié à une chambre de déblocage (13) par une surface active de déblocage (14),
    caractérisé en ce qu'il est prévu entre le raccord de pression (7) et la chambre de travail (18) du piston de travail (3) un étranglement (17) avec une fonction d'étranglement interruptible avec un délai, la chambre de déblocage (13) du piston de verrouillage (11) pouvant être soumise sans étranglement à la pression venant du raccord de pression (7), de telle sorte que lors de l'arrivée de la pression par le raccord (7), c'est d'abord le piston de verrouillage (11) qui quitte la position de verrouillage, et ce n'est qu'ensuite qu'a lieu la montée en pression dans la chambre de travail (18), d'abord avec étranglement, et ensuite sans étranglement.
  2. Vérin hydraulique selon la revendication 1, caractérisé en ce que le piston de verrouillage (11) est sous la forme d'un piston à gradins et présente, sur un même côté de piston, en plus de la surface de déblocage (14), encore une deuxième surface active (20) pouvant être soumise à la pression présente dans la chambre de travail (18).
  3. Vérin hydraulique selon la revendication 1, caractérisé en ce qu'il est prévu entre la chambre de travail (18) et le raccord de pression (7) une soupape de retenue (27) s'ouvrant en direction du raccord (7) et disposée dans une conduite contournant l'étranglement (17).
  4. Vérin hydraulique selon la revendication 3, caractérisé en ce que la soupape de retenue (27) est disposée dans le piston de verrouillage (11).
  5. Vérin hydraulique selon la revendication 1, caractérisé en ce que l'étranglement (17) à fonction d'étranglement interruptible avec un délai est constitué par une fente d'étranglement entre un tronçon cylindrique (15) sur le piston de verrouillage (11) et un alésage (16) dans le boîtier ou dans une pièce disposée à poste fixe dans le boîtier.
  6. Vérin hydraulique selon la revendication 1, caractérisé en ce que le ressort de verrouillage (35) du piston de verrouillage (11) est disposé dans une chambre (34) communiquant avec l'atmosphère.
  7. Vérin hydraulique selon la revendication 1, caractérisé en ce que le piston de verrouillage (11) présente sur son côté opposé au piston de travail (3) un appendice (31) au moyen duquel le piston de verrouillage (11) peut être entraîné par une attaque de force mécanique pour coulisser de sa position de verrouillage vers sa position de déblocage.
  8. Vérin hydraulique selon la revendication 7, caractérisé en ce que le piston de verrouillage (11) est disposé de manière à se mouvoir en sens contraire au piston de travail (3), et est relié par sa deuxième surface d'action (20) à la chambre de travail (18), et en ce que le ressort de verrouillage (35) avec la chambre (34) ouverte à l'atmosphère est disposé sur l'autre côté du piston de verrouillage (11).
  9. Vérin hydraulique selon les revendications 7 et 8, caractérisé en ce que l'appendice (31) du piston de verrouillage (11) présente une gorge (33) accessible de l'extérieur pour l'attaque de force mécanique.
  10. Vérin hydraulique selon la revendication 1, caractérisé en ce que le piston de travail (3) présente une douille prolongatrice (24) pour loger les billes (25) du verrou à billes (23) et en ce que dans le boitier (1) est disposée à poste fixe une douille de verrouillage (8) qui porte la gorge de verrouillage (26).
EP90124490A 1989-12-21 1990-12-18 Vérin hydraulique muni d'un mécanisme de blocage Expired - Lifetime EP0433955B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3942348 1989-12-21
DE3942348A DE3942348A1 (de) 1989-12-21 1989-12-21 Verriegelbarer hydraulikzylinder

Publications (2)

Publication Number Publication Date
EP0433955A1 EP0433955A1 (fr) 1991-06-26
EP0433955B1 true EP0433955B1 (fr) 1993-11-10

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP90124490A Expired - Lifetime EP0433955B1 (fr) 1989-12-21 1990-12-18 Vérin hydraulique muni d'un mécanisme de blocage

Country Status (5)

Country Link
US (1) US5097748A (fr)
EP (1) EP0433955B1 (fr)
JP (1) JPH04113006A (fr)
DE (2) DE3942348A1 (fr)
ES (1) ES2046660T3 (fr)

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* Cited by examiner, † Cited by third party
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DE4107980A1 (de) * 1991-03-13 1992-09-17 Bosch Gmbh Robert Hydraulisch betaetigte rasteinrichtung
US5379969A (en) * 1992-01-30 1995-01-10 The Boeing Company Hydraulic actuator with mechanical lock and installation
DE9303050U1 (de) * 1993-03-03 1993-04-22 Festo AG & Co, 73734 Esslingen Fluidisch betätigbarer Arbeitszylinder
FR2706536B1 (fr) * 1993-06-16 1995-07-21 Snecma Vérin d'inverseur de poussée comportant un dispositif de verrouillage interne et un dispositif de détection de la panne du dispositif de verrouillage interne.
US5349894A (en) * 1993-10-01 1994-09-27 Loud Engineering & Manufacturing Locking hydraulic actuator
US5400694A (en) * 1994-03-04 1995-03-28 Mcneilus Truck And Manufacturing, Inc. Hydraulic cylinder with internal safety valve
EP0692640A3 (fr) * 1994-06-14 1997-07-30 Rasmussen Kann Ind As Dispositif actionné par un fluide sous, pression pour l'ouverture et la fermature d'une lucarne ou d'une trappe
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Also Published As

Publication number Publication date
JPH04113006A (ja) 1992-04-14
ES2046660T3 (es) 1994-02-01
DE3942348A1 (de) 1991-06-27
US5097748A (en) 1992-03-24
DE59003465D1 (de) 1993-12-16
DE3942348C2 (fr) 1992-10-15
EP0433955A1 (fr) 1991-06-26

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