EP0579919B1 - Pneumatischer Linearantrieb mit Endlagenverriegelung - Google Patents

Pneumatischer Linearantrieb mit Endlagenverriegelung Download PDF

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Publication number
EP0579919B1
EP0579919B1 EP93107819A EP93107819A EP0579919B1 EP 0579919 B1 EP0579919 B1 EP 0579919B1 EP 93107819 A EP93107819 A EP 93107819A EP 93107819 A EP93107819 A EP 93107819A EP 0579919 B1 EP0579919 B1 EP 0579919B1
Authority
EP
European Patent Office
Prior art keywords
piston
control piston
spring
control
piston rod
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
EP93107819A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0579919A1 (de
Inventor
Franz Dipl.-Ing. Sperber
Arno Dipl.-Ing. Voit
Walter Dipl.-Ing. Stich
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 EP0579919A1 publication Critical patent/EP0579919A1/de
Application granted granted Critical
Publication of EP0579919B1 publication Critical patent/EP0579919B1/de
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, with at least one spring which counteracts the pneumatic force and loads the piston rod in the direction of an end position, and each with a positive, pneumatic lock for each of the two end positions of the piston rod according to the preamble of the claim 1.
  • DE-OS 36 09 765 is in contact with the surface of the piston rod during the extension movement (from left to right) under spring force until it engages in the corresponding recess when the end position is reached. In this way, it exerts a compressive and a frictional force on the piston rod, which are suitable for damping any slight vibrations that may occur.
  • the invention has for its object a pneumatic linear drive with a single-acting piston / cylinder unit, with at least one spring counteracting the pneumatic force and with a positive, pneumatic locking for each of the two end positions
  • a pneumatic linear drive with a single-acting piston / cylinder unit, with at least one spring counteracting the pneumatic force and with a positive, pneumatic locking for each of the two end positions
  • the locks for both end positions are summarized on one of diametrical sides in a recess of the piston rod lockable locking link with two acting on this control piston, resulting in a compact arrangement of the locking mechanism.
  • the first control piston which is smaller due to the pressurized cross section, is rigidly connected to the locking link and is used for locking in the pneumatically unpressurized, i.e. responsible for the spring-actuated, end position of the piston rod. With respect to a cryogenic control valve, this would preferably be the closed position of the valve.
  • the second, from the pressurized cross section larger control piston is limited translationally movable relative to the locking link on a rigidly connected to this support tube, with a support tube fixed and a housing-fixed stop are present, and a compression spring between the control piston and the locking link is arranged.
  • the power transmission between the control piston and the locking link is thus resilient, i.e. relatively soft.
  • the second, larger control piston is for locking in the pneumatically pressurized, i.e. active, end position of the piston rod is responsible, with respect to a cryogenic control valve, this would preferably be the open position.
  • valve piston Through appropriate flow channels in the area of the valve piston, the second Control piston, the support tube and the locking link in connection with the various stops ensures that the pressurization, ie the activation, of the piston / cylinder unit takes place only after the complete release of the unpressurized end position, resulting in a material-friendly, largely jamming-free operation.
  • valve piston releases an additional flow cross-section between itself and the second control piston, so that the piston rod movement takes place relatively quickly.
  • each of the two control pistons is responsible for locking in one end position and for unlocking in the opposite end position.
  • the control pistons are activated actively by pneumatic pressure on one side.
  • the locking link rests on one side under pneumatic or spring force on the surface of the piston rod and dampens any vibrations that may occur due to the normal and frictional force exerted.
  • the sub-claims 2 to 4 contain preferred embodiments of the linear drive according to claim 1.
  • the linear drive 1 shown in its essential elements is part of a cryogenic control valve, not shown, with which the flow of a liquid, frozen rocket fuel component is blocked or released.
  • the extended (left) position of the piston rod 8 and the piston 6 shown in FIG. 1 corresponds to the closed position of the control valve
  • the retracted (right) position of the piston rod 8 shown in FIGS. 3 and 4 corresponds to the open position.
  • the terms “retracted” and “extended” refer to the part of the piston rod 8 which extends from the piston 6 to the left and which is connected to the valve body of the cryogenic control valve, which is also not shown.
  • the linear drive 1 comprises the piston / cylinder unit 2, which essentially consists of the housing parts 3 and 4, the piston 6 with the sealing ring 7 and the piston rod 8.
  • the linear drive further comprises the spring 5, which is connected at its left, invisible end directly or indirectly to the piston rod 8 and loads it against the pneumatic force in the direction of its left end position.
  • the linear drive 1 also includes the entire locking mechanism, via which the piston rod movement is also controlled.
  • the housing part 3 takes up the displacement of the piston / cylinder unit 2 and supports the right-hand part of the piston rod 8, which improves the rod and piston guidance but is not absolutely necessary in terms of its overall function.
  • the housing part 4 receives the locking mechanism and carries the right end of the spring 5.
  • the central element of the lock is formed by the locking link 14, which can be moved linearly to a limited extent in its displacement 15 transversely to the piston rod 8 and which, in the end positions of the piston rod 8, alternately engages in its recesses 9, 10 from opposite sides.
  • the locking link 14 has a recess 16 which can be closed around the piston rod or open on one side transversely to the direction of movement of the locking.
  • the displacement 15 of the locking link 14 preferably has a rectangular, possibly with rounded corners or an oval cross-section, whereas the displacements of all pistons are generally circular in cross-section.
  • the locking link 14 is rigidly connected via a piston rod 19 to a first, relatively small control piston 17, which is guided gas-tight in its career by means of a sealing ring 18.
  • the control piston can be pressurized with compressed gas, preferably helium, through the channel 20 and thereby generates a force or a movement of the locking link 14 radially towards the piston rod 8.
  • a second, larger control piston 21 is arranged, which in connection with a valve piston 28 serves not only to move the locking link but also to control the gas for the actual working piston, ie the piston 6.
  • the second control piston 21 is not rigidly connected to the locking link 14, but is mounted on a supporting tube 30 which is fixed to the locking link and is axially movably limited.
  • the end position of the control piston 21 remote from the link is defined by a rigid stop 31 on the support tube 30, which interacts with the smaller diameter of a stepped bore 23 in the control piston 21. This piston position is shown in Figure 1.
  • the movement of the control piston 21 to the locking link 14 or to the piston rod 8 is limited twice, on the one hand by striking the bottom of the valve piston 28 on the end face 32 of the support tube 30, and on the other hand by the stop 39 in the housing part 4.
  • the valve piston 28 lies usually by the force of the biased Spring fingers 27 of the spring cage 25 fixedly connected to the control piston 21 on the end face 24 of the control piston 21 in a gas-tight manner, an additional sealing element, for example an O-ring, being able to be present in this area.
  • the valve piston 28 can be lifted from the end face 24 by a corresponding pressure or force action, and at most up to the abutment against the stop lugs 26 of the spring cage 25, an open flow cross section being created between the pistons 21 and 28.
  • the spring cage 25 is not a closed, pot-like structure but a flow-permeable body with several openings.
  • the pistons 21 and 28 mostly behave like an integral body, their resilient connection only comes into effect under certain conditions.
  • the power transmission from the control piston 21 to the locking link 14 takes place elastically compliant via the spring 37.
  • a relatively hard, direct power transmission only occurs in the moments when the bottom of the valve piston 28 abuts the end face 32 of the support tube 30.
  • the compressed gas supply to the piston 6 takes place through the valve piston 28 and the control piston 21, see in particular FIGS. 2 and 3.
  • This connection begins with the openings 33 in the area of the end face 32 of the support tube 30 and continues with the flow channel 36 in the interior of the support tube and with the openings 34 and 35 in the area of the locking link 14.
  • the openings 12 and 13 in the wall element 11 belong to this flow connection.
  • the number, size and arrangement of the openings and channels can be used to influence the movements of the piston rod 8, specifically depending on the position of the locking link 14 relative to the wall element 11.
  • the flow connection mentioned is always open.
  • the flow connection is interrupted from the outside (bottom) of the valve piston 28 into the interior of the pistons 28 and 21 by contacting the bottom of the valve piston 28 on the end face 32 of the support tube 30 with the throttle channel 29 closed.
  • the valve piston 28 must also lie gas-tight on the control piston 21, the latter by means of a sealing ring 22 is performed gastight in his career.
  • the flow connection from the channel 38 in the housing part 4 to the pressure side of the piston 6 is open, as shown in FIGS. 1 to 4.
  • Figure 1 shows the extended (left) and locked end position of the piston rod 8, which is brought about by the force of the spring 5.
  • the control piston 17 is pressurized with helium (see arrow), the pistons 21, 28 and 6 are "'vented", i.e. depressurized. Due to the force of the spring 37, the control piston 21 is in its outermost (lowest) position on the support tube 30 at the stop 31.
  • the control piston 17 In order to release the lock and initiate the retracting movement of the piston rod 8, the control piston 17 is “vented” and the control piston 21 is pressurized with helium. As a result of the strong throttling action of the narrow throttle duct 29, the valve piston 28, together with the control piston 21, is pushed as far as possible against the end face 32 of the support tube 30, the throttle duct 29 being closed and the spring 37 being compressed. From then on, the pistons 21 and 28 and the support tube 30 move together with the locking link 14, the part of the locking link 14 facing the control piston 17 completely moving out of the recess 10 and thus releasing the piston rod 8.
  • FIG. 3 shows the locked, retracted position of the piston rod 8 with the spring 5 pushed together to the maximum, which corresponds to the opened state of the cryogenic control valve, not shown.
  • the locking link is engaged by the force of the spring 37 in the recess 9 of the piston rod 8, the piston 6 is under pressure.
  • the pistons 21 and 28 are “vented” and the control piston 17 is pressurized, whereby the unlocking movement of the locking link 14 begins. Due to the pressure still present in the displacement of the piston 6, which extends into the area of the pistons 21 and 28, the valve piston 28 lifts off the end face 24 of the control piston 21 and releases a relatively large flow cross section via the throttle channel 29. In this way there is a rapid reduction in pressure in the displacement of the piston 6 and, after complete unlocking, a relatively rapid extension movement of the piston rod 8.
  • Figure 4 shows the moment of transition from unlocking to extending movement.
  • the locking link 14 then rests in a damping manner on the piston rod 8 until it engages in the recess 10 in the extended end position.
  • the frictional force in the damping phase is kept at a moderate level by the small pressure cross section of the control piston 17.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
  • Actuator (AREA)
EP93107819A 1992-06-27 1993-05-13 Pneumatischer Linearantrieb mit Endlagenverriegelung Expired - Lifetime EP0579919B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4221230 1992-06-27
DE4221230A DE4221230C1 (ja) 1992-06-27 1992-06-27

Publications (2)

Publication Number Publication Date
EP0579919A1 EP0579919A1 (de) 1994-01-26
EP0579919B1 true EP0579919B1 (de) 1995-12-20

Family

ID=6462029

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93107819A Expired - Lifetime EP0579919B1 (de) 1992-06-27 1993-05-13 Pneumatischer Linearantrieb mit Endlagenverriegelung

Country Status (4)

Country Link
EP (1) EP0579919B1 (ja)
JP (1) JP2929568B2 (ja)
AT (1) ATE131910T1 (ja)
DE (1) DE4221230C1 (ja)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4323846C1 (de) * 1993-07-16 1994-11-10 Deutsche Aerospace Pneumatischer Linearantrieb mit Endlagenverriegelung
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
FR2743518B1 (fr) * 1996-01-12 1998-04-17 Robotic Sa Perfectionnement pour porte pilote mobile
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
IT1391300B1 (it) * 2008-10-17 2011-12-01 Biesse Spa Gruppo di lucidatura per una macchina per la lavorazione di bordi di lastre in vetro, marmo e simili materiali lapidei
CN101858371B (zh) * 2010-05-25 2013-08-21 中航飞机起落架有限责任公司 内置手动应急开锁装置的作动筒
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
EP2802782A2 (en) * 2012-01-13 2014-11-19 Norgren GmbH Position adjustment and position locking of a fluid operated actuator
DE102017126196A1 (de) * 2017-11-09 2019-05-09 Arianegroup Gmbh Federunterstützter, verriegelbarer Linearantrieb und ein damit ausgestattetes Ventil
CN111636979B (zh) * 2020-06-08 2021-05-25 安徽九州云箭航天技术有限公司 泵压变推力液体火箭发动机液氧主路用开关及流量调节阀
DE102021108820A1 (de) 2021-04-08 2022-10-13 Fte Automotive Gmbh Hydraulischer Parksperrenaktuator

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
CH353428A (de) * 1957-06-04 1961-04-15 Sprecher & Schuh Ag Druckmittelbetätigter Antrieb für elektrische Schaltgeräte
DE2146592A1 (de) * 1971-09-17 1973-03-22 Westinghouse Bremsen Apparate Druckmittelbetaetigbarer arbeitszylinder mit endstellungsverriegelung
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

Also Published As

Publication number Publication date
EP0579919A1 (de) 1994-01-26
DE4221230C1 (ja) 1993-07-08
JP2929568B2 (ja) 1999-08-03
ATE131910T1 (de) 1996-01-15
JPH06159140A (ja) 1994-06-07

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