EP0000850B1 - Kraftverstärkungs-Mechanismus und damit versehenes Absperrventil - Google Patents

Kraftverstärkungs-Mechanismus und damit versehenes Absperrventil Download PDF

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Publication number
EP0000850B1
EP0000850B1 EP78400041A EP78400041A EP0000850B1 EP 0000850 B1 EP0000850 B1 EP 0000850B1 EP 78400041 A EP78400041 A EP 78400041A EP 78400041 A EP78400041 A EP 78400041A EP 0000850 B1 EP0000850 B1 EP 0000850B1
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EP
European Patent Office
Prior art keywords
axis
driving
rolling
ramp
force
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Expired
Application number
EP78400041A
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English (en)
French (fr)
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EP0000850A1 (de
Inventor
Pierre Louis Christian Barbe
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Pont a Mousson SA
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Pont a Mousson SA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/12—Actuating devices; Operating means; Releasing devices actuated by fluid
    • F16K31/16—Actuating devices; Operating means; Releasing devices actuated by fluid with a mechanism, other than pulling-or pushing-rod, between fluid motor and closure member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H25/00—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms
    • F16H25/18—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions
    • F16H25/183—Gearings comprising primarily only cams, cam-followers and screw-and-nut mechanisms for conveying or interconverting oscillating or reciprocating motions conveying only reciprocating motion, e.g. wedges

Definitions

  • the present invention relates to force multiplier mechanisms of the type comprising a driving member movable along an axis and having a driving surface making a relatively small angle with this axis, a fixed bearing surface making a relatively large angle with this axis, a movable driven member along said axis and having an attack surface perpendicular to this axis, and rolling members capable of coming into contact simultaneously with these three surfaces.
  • Such mechanisms are particularly advantageous when looking for a large thrust and a small displacement, for example to cause a blockage or a locking of a valve shutter or of a machine tool tool.
  • the rolling members each consist of a ball, a roller, a roller or a barrel.
  • Each of these members thus has three point or linear contacts, at the rate of one contact with each of these surfaces, but it is only on the surface of the leading member that there is rolling, the other two contacts being of friction. This results in a significant loss of energy by friction.
  • the object of the invention is to provide a force multiplier mechanism which overcomes this drawback by offering, under the same conditions as above, three rolling contacts instead of just one.
  • each rolling member comprises three independent rolling elements freely rotatable about the same axis, each of these elements being able to roll on one and only one of the three surfaces.
  • the mechanism can be used to transmit as is an effort over any distance and to multiply this effort only at the end of the race.
  • a second multiplier assembly comprising a second driving surface, a second bearing surface and a second attack surface as well as a second set of rolling members similar to the first, this second set being arranged so as to multiply the force in the direction of movement of the driving member opposite to the first.
  • the force multiplier mechanism according to the invention lends itself particularly well to the actuation of a tap for industrial fluids pipelines requiring a high force only for the start of opening of the shutter and for the end of closing, and a corresponding small stroke. This is why the invention also relates to a valve with sliding shutter and actuating actuator, characterized in that between the servomotor and the shutter operating rod is interposed a force multiplier mechanism such as defined above.
  • Industrial valves likely to benefit from this application are, for example, gate valves with one or two wedge-shaped lids or valves of the valve type or with a wedge-shaped obturator and a conjugate flared seat.
  • FIG. 1 which represents in a meridian section a known force multiplier mechanism
  • the principle of such a mechanism is as follows.
  • a driving or driving member 1 constituted for example by a part of revolution about an axis X-X, comprises a ramp 2 of slight inclination of angle x relative to the axis X-X.
  • This ramp 2 can be frustoconical with axis X-X or else be planar.
  • a support or reaction member is constituted by a fixed tapered ramp 3 of axis XX, of angle of inclination y substantially greater than the angle x and converging in the direction opposite to the ramp 2 so as to form with the latter a hollow corner or angle z with a movable wall 2 parallel to the axis XX.
  • a driven member 4 has an end portion constituted by a sleeve of axis X-X having a leading surface or abutment 5 perpendicular to the axis X-X; this member 4 is movable parallel to the axis X ⁇ X.
  • the surface 5 forms in meridian section the third side of a triangle, the other two sides of which are the ramps 2 and 3.
  • Force transmission members arranged in the space between the ramps 2 and 3 and the surface 5, are constituted for example by balls 6 distributed around the axis X-X.
  • the balls 6 have tangential and punctual contacts A, B, C respectively with the ramp 2, the ramp 3 and the attack surface 5.
  • each ball 6 forms during the active phase of the mechanism, a circle inscribed in the triangle 2-3-5.
  • a driving force f parallel to the axis X-X is applied to the driving member 1.
  • the member 1 then moves in the same direction, and its ramp 2 tends to push each ball 6 out of the point of angle z of the triangle 2-3-5.
  • This movement causes a discharge of each ball 6, forcing it to roll on the ramp 2 and to move along the fixed reaction or support ramp 3 which in turn gives it a certain displacement parallel to the axis XX.
  • Due to the difference between the angles x and y; the displacement of the balls 6 is substantially less than the original displacement of the driving member and, correspondingly, the balls transmit to the surface 5 a force F significantly greater than f. It is the slope of ramp 2 which gives the effort multiplication ratio F / f.
  • each ball 6 is replaced by a set of three rolling elements 7-8-9 coaxial with axis YY perpendicular to XX, of different diameters, mounted idly and independent around this YY axis.
  • rolling elements 7-8-9 coaxial with axis YY perpendicular to XX, of different diameters, mounted idly and independent around this YY axis.
  • rollers or rollers These are rollers or rollers.
  • the rollers 7 and 8 Due to the size of the rollers 7 and 8, two of the rolling surfaces are indented to allow them to rotate freely without contact: these are the ramp 2, indented in a groove 10, and the attack surface 5, indented in a groove 11.
  • the ramps 2 and 3 are flat.
  • the operation is the same as before: the set of rollers 7, 8 and 9 of transmission transmits the work fX L of the member leading to ramp 2 to the driven member of attack surface 5 by transforming this work into FX / increasing the thrust and decreasing the stroke.
  • the three rollers rotate in the directions indicated by the arrows in Fig. 2A.
  • a descent of the force multiplication ramp 2 in the direction of the arrow f narrows the angular interval between the ramps 2 and 3 and forces to descend the rolling members.
  • a rise in the ramp 2 widens the abovementioned angular interval and allows a rise in the rolling members when a thrust force is exerted upwards on the driven member 4.
  • a force multiplier mechanism according to the principle of FIG. 2 lends itself particularly well to actuating the operating rod of the shutter of an industrial valve, for example of the valve or valve type, taking into account the fact that the opening and closing operations require significant efforts with small displacements, and that the displacement of the shutter between the two extreme positions requires only a much weaker effort.
  • the single acting force multiplier mechanism of FIG. 5 comprises a tubular body of axis XX in two parts 12 and 13 screwed one on the other by female and male threads 14 a -14 b .
  • the cap portion 12, shown unscrewed in FIG. 5 comprises a central cylindrical opening 15 to deliver passage to the motor or driving member, and a support or reaction ramp 3 frustoconical. The details of this mechanism are visible in Figs. 6 and 7, which show a globe valve fitted with a similar mechanism.
  • Part 13 is used to house the driving, driven and transmission components. It has for this purpose a blind cylindrical cavity 16 open upwards in which slides, by its external cylindrical surface, a tubular sleeve 4 constituting the driven member. This sleeve is hollowed out on its upper edge by a number of notches 11 a -11 b in steps equal to the number of sets of transmission elements 7-8-9, here equal to three.
  • the deep indentations 11 8 receive with play the rolling and force and stroke transmission elements 7 and 8 which do not roll on the lateral bearings 11 b , which constitute both the attack or abutment surface 5 and means for lateral positioning of the elements 9 of smaller diameter.
  • the blind cylindrical cavity 17 of the sleeve 4 serves as a guide for a cylindrical driving member 1 truncated into as many flat ramps 2 as there are sets of rolling members, here three in number.
  • Each ramp 2 is indented by a straight groove 10 and parallel to the ramp 2.
  • each set of rolling elements 7-8-9 is housed between the driving member 1, the driven sleeve 4 and the cap 12 of the body.
  • each set of rolling elements 7-8-9 is mounted according to a system provided with symmetry (FIG. 7), with a cylindrical roller 8 of large diameter flanked by two rollers 7 of smaller diameter.
  • the rollers 7 and 8 rotate freely, independently of each others, on a roller 9 of axis YY, of much smaller diameter than the rollers 7 and whose length is substantially greater than the sum of the lengths of the generators of the rollers 7 and 8, so as to have its active rolling ends projection relative to the rollers 7.
  • the roller 8 is intended to roll on the fixed support ramp 3 of the part 12 forming a cover.
  • the notch 10 of the ramps 2 has a length greater than that of the roller 8 and a depth greater than the difference of the radii between the roller 8 and the rollers 7 in order to allow passage to the roller 8 with play, without contact.
  • the two rollers 7 of average diameter roll on the ramp 2.
  • the roller 9 rolls by its free and active ends on the notches 11 of the tubular sleeve 4, which offer an active surface of width greater than the active length of each end of the roller 9.
  • the notches 1 1 a of the sleeve 4 provide passage with clearance , without contact, to the rollers 7 and 8 and therefore have a width greater than the sum of the lengths of the generators of a roller 8 and two rollers 7 and a depth, relative to the notches 1 1 b , greater than the difference of radius between roller 8 and roller 9.
  • the rolling contacts of the rollers 7 and the rollers 9 are not punctual but linear along generators, the traces of which, in the diagram of FIG. 2, are points A and C; similarly, due to the short axial length of the rollers 8, there is also a linear contact at B.
  • the frustoconical ramp 3 can be replaced by three flat ramps, or else the central roller 8 rolling on this ramp 3 can be curved in a barrel, while the three ramps 2 with flattening could be replaced by a single frustoconical ramp and the rollers 7 could remain cylindrical or else be curved in barrels.
  • the valve itself in FIG. 6 comprises a body 20 of axis X-X, fluid flow conduits in the direction of the arrows, 21 for the inlet and 22 for the outlet, perpendicular to the axis X-X; at the ends of these conduits are provided connection means with pipes by thread 23 and by flange 24
  • the body 20 also comprises a plane seat 25 of axis XX and a cylindrical upper pot 26 with internal thread 27.
  • a lower tubular extension 30 of the part 13 of the multiplier mechanism In this extension 30, forming the cap of the valve, slides with a sealed seal the operating rod 28 of the valve 29 of the valve.
  • the part 12 of the multiplier body forming a cap of axis XX, is surmounted by a boss 12 ° of connection by threading with the body 31 of a diaphragm cylinder constituting a servomotor.
  • the membrane 32 of axis XX ' is integral with a push rod 33 of axis XX guided through a bore of the boss 12 8 and capable of exerting a thrust on the upper end edge of the driving member 1 of the effort multiplier mechanism.
  • the latter is in fact in the form of a hollow capsule with cavity 34 oriented downwards.
  • the body 31 has at its upper part an opening 35 capable of being connected to a supply of pressurized working fluid, for example compressed air.
  • the membrane 32 is subjected on its upper face to the pressure of the working fluid and, on its lower face, to the antagonistic action of a return spring 36 bearing on the lower bottom of the body 31.
  • the driven sleeve 4 slides in the cavity 16 against a helical spring 37 bearing on the lower bottom of this cavity and on an external shoulder 4 8 of the sleeve 4.
  • the bottom 38 of this sleeve 4 is fixed to the operating rod 28 which passes through it, for example by a screw 39.
  • the sleeve 4 is integral in translation with the operating rod 28 of the valve.
  • the driving member 1 can slide in the cavity 17 under the opposing actions of the push rod 33, therefore of the diaphragm cylinder 32, and of a helical return spring 40 compressed between the bottom upper of the cavity 34 and a fixed intermediate ring 41 fixed to the cap 30 of the tap by at least one pin 42 which crosses with play the bottom of the bowl 38 of the sleeve 4.
  • the valve 29 When the diaphragm cylinder 32 is inactive, that is to say not supplied by the conduit 35 with pressurized fluid, the valve 29 is applied to its seat 25 in the closed position, under the action of the return spring 40 In fact, the spring 40 causes the member 1 to rise, so that the angular interval between the ramps 2 and 3 tends to narrow, which causes the downward movement of the rolling members 7-8-9, of which the descent of the sleeve 4 and of the valve assembly 28-29 which is integral therewith.
  • FIG. 6 This operation is illustrated in Figs. 6 and 6A: in Fig. 6, when the distance d 'between the capsule 1 and the upper bottom of the cap 12 is the smallest (cylinder at rest), the distance D' between the axis YY of the bearing members 7-8-9 and this bottom is the largest. Consequently, the sleeve 4 and consequently the valve 29 are in the low position (closing). In Fig. 6, when the distance d 'between the capsule 1 and the upper bottom of the cap 12 is the smallest (cylinder at rest), the distance D' between the axis YY of the bearing members 7-8-9 and this bottom is the largest. Consequently, the sleeve 4 and consequently the valve 29 are in the low position (closing). In Fig. 6, when the distance d 'between the capsule 1 and the upper bottom of the cap 12 is the smallest (cylinder at rest), the distance D' between the axis YY of the bearing members 7-8-9 and this bottom is the largest. Consequently, the slee
  • the ramp or ramps 2 are. converging towards the shutter and its seat.
  • This variant uses, like that of FIG. 6, a mechanism known as a simple multiplication effect because it offers a certain ratio or factor of multiplication of the motor force only during the locking stroke, and is satisfied with a direct transmission of the motor force, without multiplication, during the return race, that is to say unlocking and opening.
  • This mechanism is implemented in the following manner.
  • This member consists of a cone with an inclined ramp 2 which slides on an axial guide pin 43 with a head 44 passing through a stepped bore 45 of this cone.
  • This pin is integral with the valve operating rod 29 by means of a portion of threaded rod 46 screwed into the upper end of the operating rod 28 so that the pin 43 and this rod 28 are secured to the sleeve 4.
  • the latter has an attack surface 5 in which three notches 11 are formed.
  • the cone 1 is actuated by a push rod 33 slightly modified compared to that of FIG. 6 since it comprises a flange 33a for fixing to the cone 1, or any other equivalent fixing means.
  • the ramp 2 the slope of which defines the effort multiplication ratio or factor F / f, has a special feature which does not exist in FIG. 6: it comprises a clearance portion 2 8 which is strongly inclined relative to the axis XX, followed downwards by a level portion 2 b roughly parallel to the axis XX.
  • the portion 2a abruptly widens the angular interval between the cone 1 and a cylindrical rolling cavity 47 extending upward the support ramp 3 of the cover 12 of the force multiplier mechanism.
  • the clearance 2a facilitates the penetration of the rolling members into the cavity 47 during the recoil stroke of the driving member 1 and limits the force of the roller 8 on this cylindrical cavity at the point of contact B because this force, without the portion 2 28 , would be unnecessarily large and would cause excessive wear of the cavity 47.
  • the cap 12 of the mechanism body and the part 13 of this body forming the valve cap has internally a bearing guide cavity for the transmission members 7-8-9, which decomposes, from top to bottom, into a cylindrical part 47, mentioned above, a flared part with flat straight ramp or frustoconical 3, and a cylindrical part 48 of diameter greater than the part 47.
  • rollers 7 and 8 and the roller 9 are shown here in a single copy, but appear in several sets distributed around the axis X ⁇ X of symmetry of the mechanism. They are intended to roll inside the space limited by the ramps 2 ⁇ 2 a ⁇ 2 b , the attack surface 5 and the rolling cavity 47-3-48.
  • the rod 33 exerts an upward traction on the cone 1 (direction of the arrow g 2 ), thus widening the angular interval between the ramps 2 and 3 and exerting no force on the rolling members.
  • the cone 1 quickly returns to contact with the head 44 by sliding on the spindle 43 without the rolling members 7-8-9 moving.
  • the cone 1 directly drives the head 44 and the operating rod 28 which is integral therewith.
  • the rolling members 8 and 9 are content to roll on their respective rolling surfaces 47 and 5 without playing any active role. There is simple transmission of effort without multiplication.
  • the rollers 7 are released from the ramp 2 and, when the roller 8 arrives in B ', the rollers 7 are housed in the clearance portion 2a. We find the configuration of FIG. 9, then that of FIG. 8.
  • Figs. 11 to 13 show a variant of a multiplier mechanism according to the invention which is said to have a double multiplication effect because it offers a certain ratio or multiplication factor both during the locking stroke and during the unlocking stroke.
  • This mechanism is partly analogous to the previous mechanism of Figs. 8 to 10, but it has a greater length measured parallel to the axis X-X, because it comprises in duplicate a certain number of similar parts.
  • This mechanism is implemented in the following manner.
  • this member is slidably mounted on the rod 43 with a head 44 of axis XX, but the hollow cone 1 is doubled by one. Similar cone 1 a with ramp 2 1 of slope opposite to that of ramp 2 and with grooves 10 a .
  • the cones 1 and 1 a which are joined by a cylindrical part 49, are of the same axis XX and form only one unit which is integrally sliding on the rod 43 and actuated by the push rod 33, of which it is integral. They can also be integral with a screwed piston 33- sliding in the cylindrical cavity 47, which then forms the cylinder of the actuating cylinder (FIG. 11a).
  • Part 12 is longer than previously and internally, successively from top to bottom, the following parts; a cylindrical cavity 47; a flared part with a straight or frustoconical ramp 3; again a cylindrical cavity 48 of diameter greater than the part 47; a tightening part 50 with a straight or frustoconical ramp with a slope opposite to that of part 3; and a cylindrical cavity 51.
  • the elements 7-8-9 are intended to roll inside the space limited by the ramps 2 ⁇ 2 a ⁇ 2 b , the attack surface 5 of the driving member 4 and the rolling cavity 47- 3-48.
  • the elements 107-108-109 are intended to roll inside the space limited by the ramps 49-2 c , another attack surface 5a of the driven member 4 and the cavity 47-3-48- 50.
  • a pusher which differs from the sleeve 4 of FIG. 8 by a greater length.
  • stepped openings 53 (Fig. 11 B) distributed uniformly around the axis XX in number equal to the end recesses 11 and each serving as a housing for a set of elements 107-108-109.
  • the active bearing surface of the roller 109 is the upper face 5a of the ends of the open ture 53, and the rollers 107 and 108 can roll freely inside this opening.
  • the elements 107 and 108 instead of being constituted by rollers, are constituted by rings threaded one on the other and on the roller 109.
  • the dimensioning is chosen so that even if the elements 107-108-109 leave the openings 53, they remain positioned in relation to them and return there by themselves.
  • the approach stroke of the shutter towards the closed position can be as large as possible and depends only on the length of the cylindrical cavity 47 .
  • the double-acting mechanism ensures one.
  • the single-acting mechanism of Figs. 8 to 10 is therefore applicable to conventional globe valves with well-defined fluid flow direction and of small diameter, while the double-acting mechanism of FIGS. 11 to 13 is useful for single-valve or two-valve valves that may get stuck, as well as for warhead and flared conjugate seat valves and for globe valves where the direction of flow of the fluid does not is not defined and the valve of which can therefore be subjected to a significant closing pressure, thus requiring a significant lifting effort.
  • the sleeve 1 of FIG. 6 has ramps of reverse inclination of that of the cone 1 of FIGS. 8 to 13.
  • the movements of the driving members to cause the opening and closing of the valve are opposite: this is the rise of the sleeve 1 of FIG. 6 but the descent of the cone 1 of FIGS. 8 to 13 which causes the closure.
  • the direction of the inclination of the ramps 2 will be chosen according to the needs of the construction; it should be noted that this choice is not possible with the ball mechanisms or the like of the prior art and is made possible by the ability of the rollers 7 and 8 to rotate in opposite directions.
  • FIG. 14 A variant of the tap of FIG. 6 is shown in FIG. 14.
  • the engine cone 1 with ramps 2 has its conicity converging towards the valve (not shown) and diverging towards the actuator. This conicity is therefore opposite to that of the sleeve 1 of FIG. 6.
  • a 40 ° return resort in the closed position is compressed between the cone 1 and the upper arch of the cover 12.
  • the spring 40 or 40 8 which ensures the recall to the closed position, this is for safety reasons, the valve being assumed to remain normally closed as long as the actuator does not receive a pressurized fluid.
  • the spring 40 or 40 8 which ensures the recall to the closed position
  • the force multiplication ramp 2 may successively comprise two slopes, one for approaching with a certain multiplication, the other for locking with an even greater multiplication.
  • the first slope could for example give a multiplication factor of 5 and the second a multiplication factor of 10 to 12. The latter would be on the side of the end furthest from the axis of movement of the ramp.
  • the ramp 2 can also have a continuously variable slope, like a cam.
  • the multiplier of the invention can be used not only for actuating valves, but also for blocking or clamping workpieces on machine tools, the valve 29 becoming the blocking or clamping tool.
  • the invention is also applicable to the actuation of marking or cutting punches, the valve 29 becoming a cutting tool.
  • the invention is also applicable to clutches, the operating rod 28 then being secured to a disc or a clutch cone.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Transmission Devices (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Rolling Contact Bearings (AREA)

Claims (8)

1. Kraftvervielfachervorrichtung, mit einem führenden Element, welches längs einer Achse beweglich ist und eine führende Fläche aufweist, die mit der Achse einen vergleichsweise kleinen Winkel einschließt, einer mit dieser Achse einen vergleichsweise großen Winkel einschließenden feststehenden Anlagefläche, einem geführten Element, welches längs der Achse beweglich ist und eine zur Achse senkrechte Angriffsfläche auffweist, und mit Rollkörpern, welche an allen drei Flächen gleichzeitig zur Anlage kommen können, dadurch gekennzeichnet, daß jeder Rollkörper drei Rollelemente (7-8-9, 107-108-109) aufweist, die unabhängig voneinander um die gleiche Achse (Y-Y) frei drehbar sind, und daß jedes der Elemente auf einer und nur einer der drei Flächen (2-3-5, 2°-50-5a) abrollen kann.
2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die führende Fläche (2) und die Anlagefläche (3) beide in Richtung auf die Angriffsfläche (5) divergieren.
3. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die führende Fläche (2) und die Anlagefläche (3) in Richtung auf die Angriffsfläche (5,58) divergieren bzw. konvergieren.
4. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Anlagefläche (3), bei Betrachtung in aktiver Richtung (g') der Versetzung des führenden Elements, eine zur Achse (X-X) parallele Fläche (47) vorangeht, und daß die führende Fläche (2) eine Stufe (2a―2b) aufweist, die mit dieser Achse einen nennenswerten Winkel einschließt.
5. Vorrichtung nach einem der Asprüche 1 bis 4, dadurch gekennzeichnet, daß das führende Element (1) längs eines mit einem Kopfteil (44) versehenen Schafts (43), welcher mit dem geführten Element (4) fest verbunden ist, gleitend angebracht ist und sich während seines Rücklaufs (g2) formschlüssig gegen das Kopfteil legt.
6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß sie eine zweite Vervielfachereinrichtung umfaßt, welche eine zweite führende Fläche (21), eine zweite Anlagefläche (50) und eine zweite Angriffsfläche (58) sowie einen zweiten Satz von Rollkörpern (107-108-109) entsprechend den ersten (7-8-9) aufweist, wobei die zweite Einrichtung so eingerichtet ist, daß sie die Kraft bei einer zur ersten Versetzung (g') des führenden Elements entgegengesetzten Versetzung (g2) vervielfacht.
7. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß die drei Elemente (7-8-9, 107-108-109) verschiedenen Durchmesser haben, daß die führende Fläche (2) und die Angriffsfläche (5) Aufnehmungen (10-118-11b, 108-53) aufweisen, die mit Spiel die Elemente (7-8, 107-108) aufnehmen, die größeren Durchmesser haben als diejenigen Elemente (7-9, 107-109), mit denen die Flächen jeweils zusammenwirken.
8. Hahn mit gleitend geführtem Verschlußteil und Servoantrieb, dadurch gekennzeichnet, daß zwischen dem Servoantrieb (31-32) und dem Betätigungsschaft (28) des Verschlußteils (29) eine Vorrichtung gemäß einem der Ansprüche 1 bis 7 vorgesehen ist.
EP78400041A 1977-07-11 1978-06-28 Kraftverstärkungs-Mechanismus und damit versehenes Absperrventil Expired EP0000850B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR7721261 1977-07-11
FR7721261A FR2397569A1 (fr) 1977-07-11 1977-07-11 Mecanisme multiplicateur d'effort

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EP0000850A1 EP0000850A1 (de) 1979-02-21
EP0000850B1 true EP0000850B1 (de) 1980-08-06

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EP (1) EP0000850B1 (de)
BE (1) BE868889A (de)
CH (1) CH625322A5 (de)
DE (1) DE2860116D1 (de)
ES (1) ES471613A1 (de)
FR (1) FR2397569A1 (de)
IT (1) IT7868629A0 (de)
LU (1) LU79943A1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2485767A1 (fr) * 1980-06-27 1981-12-31 Renault Dispositif de blocage d'organes mecaniques au moyen d'un amplificateur de force
US5018406A (en) * 1989-11-14 1991-05-28 Schuler Incorporated Mechanical locking device

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR425233A (fr) * 1910-02-18 1911-06-06 Axel Gram Hanssen Mécanisme pour transformer un mouvement rectiligne dirigé dans un sens en un autre mouvement rectiligne dirigé en sens opposé
FR1007151A (fr) * 1948-03-01 1952-05-02 Dispositif multiplicateur d'effort
FR1391990A (fr) * 1964-01-31 1965-03-12 Dispositif pour la commande automatique de l'organe d'obturation de vannes ou analogue
GB1477627A (en) * 1973-05-29 1977-06-22 Grey J Rotary torque transmission device
CH574063A5 (en) * 1974-04-30 1976-03-31 Bolex Int Sa Axial movement inverting mechanism - has balls acting between conical surfaces on push rods with separating spring

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FR2397569B1 (de) 1980-02-29
CH625322A5 (de) 1981-09-15
BE868889A (fr) 1979-01-10
ES471613A1 (es) 1979-02-01
LU79943A1 (fr) 1980-02-14
EP0000850A1 (de) 1979-02-21
IT7868629A0 (it) 1978-07-10
DE2860116D1 (en) 1980-11-27
FR2397569A1 (fr) 1979-02-09

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