EP0331854B1 - Fluid actuator for driving a rotary shaft - Google Patents

Fluid actuator for driving a rotary shaft Download PDF

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Publication number
EP0331854B1
EP0331854B1 EP88400548A EP88400548A EP0331854B1 EP 0331854 B1 EP0331854 B1 EP 0331854B1 EP 88400548 A EP88400548 A EP 88400548A EP 88400548 A EP88400548 A EP 88400548A EP 0331854 B1 EP0331854 B1 EP 0331854B1
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EP
European Patent Office
Prior art keywords
bore
piston
actuator according
control shaft
actuator
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
EP88400548A
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German (de)
French (fr)
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EP0331854A1 (en
Inventor
Jean-Claude Garrigues
René Laulhe
Pierre Rieuvernet
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.)
Applications Mecaniques et Robinetterie Industrielle AMRI
Original Assignee
Applications Mecaniques et Robinetterie Industrielle AMRI
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Application filed by Applications Mecaniques et Robinetterie Industrielle AMRI filed Critical Applications Mecaniques et Robinetterie Industrielle AMRI
Priority to DE8888400548T priority Critical patent/DE3864814D1/en
Priority to EP88400548A priority patent/EP0331854B1/en
Priority to DE198888400548T priority patent/DE331854T1/en
Priority to ES88400548T priority patent/ES2010174B3/en
Priority to US07/321,195 priority patent/US4995305A/en
Priority to JP1057665A priority patent/JPH01312206A/en
Publication of EP0331854A1 publication Critical patent/EP0331854A1/en
Application granted granted Critical
Publication of EP0331854B1 publication Critical patent/EP0331854B1/en
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    • 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
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/066—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the scotch yoke type

Definitions

  • the present invention relates to an actuator using a pressurized fluid for the rotary drive of a rotary shaft.
  • valves with quarter-turn actuation such as butterfly valves.
  • the patent FR 2260705 discloses in particular an actuator in which the jack comprises two cylinders assembled to each other and crossed, at their junction, by the control shaft. The drive of this shaft is ensured by a connecting rod directly articulated on a double piston which slides in the cylinder.
  • actuators of this kind have relatively complex structures using a relatively large number of workpieces, and are consequently heavy, bulky and of relatively high manufacturing cost.
  • the invention therefore more particularly aims to simplify this structure, while retaining the main advantages of this type of actuator, in order to obtain a more compact, lighter and more economical assembly.
  • an actuator making a cylinder cooperate, comprising a tubular body closed at each of its ends by a respective cylinder head, and provided with a cylindrical bore inside which slides a piston comprising a circular cover provided, at its periphery, of a seal ensuring a sliding seal with the cylindrical surface of the bore, this cover delimiting, inside said bore, two chambers, at least one of which constitutes a working chamber into which opens a pressurized fluid inlet duct and, on the other hand, a device for converting the rectilinear movement of the piston into a rotational movement of an operating shaft which extends inside said bore and passes through d '' at least one orifice provided in said body, this conversion device comprising at least one connecting rod, one end of which is articulated on the piston and the other end of which is articulated to a lever arm mounted fixedly on said control shaft, said rod and said arm extending in orthogonal to the axis of said actuating shaft plans.
  • the operating shaft can be an integral part of the actuator and include means for coupling with the actuating shaft of the controlled device.
  • the cylinder body may advantageously comprise a second orifice diametrically opposite and coaxial with the first, the operating shaft then being mounted to rotate at the level of these two orifices.
  • This operating shaft can also consist of a section of the actuating shaft of the controlled device, which then engages in the bore of the body of the jack passing through at least one of the above-mentioned orifices.
  • the above-mentioned cylinder is of the double-acting type.
  • the piston delimits, inside the bore of the cylinder body, two opposite working chambers into which open two respective intake ducts, one of the two chambers housing the above-mentioned conversion device.
  • sealing means must be provided at the pivoting of the operating shaft in the orifices of the cylinder body.
  • the actuator comprises a tubular body 1 with a cylindrical bore 2, inside which slides a piston 3, this tubular body 1 being closed at each of its ends by a respective cylinder head 4, 5.
  • This piston 3 has at one of its ends a circular cover 6 of diameter substantially equal to that of the bore 2 and provided, at its periphery, with a seal (O-ring 7) which provides a sliding seal with the cylindrical surface of bore 2.
  • This cover 6 therefore delimits two chambers 8, 9 with variable volume hermetically isolated from one another. It is held coaxially with the bore 2 thanks to a guide element 10 consisting of a flat part which extends radially in the bore and has two circular edges 11, 12 opposite substantially the diameter of the bore 2, provided with anti-friction linings, and two opposite edges 13, 14 possibly rectilinear which extend between the opposite ends of the circular edges 11, 12.
  • This guide element 10 is connected to the cover 6 by four axial longitudinal members 16, 17, 18 , 19 in the form of an angle iron arranged symmetrically with respect to the longitudinal axis of symmetry XX ′ of the bore 2 with their concavities oriented opposite to said axis.
  • These longitudinal members 16 to 19 delimit between them an axially elongated free volume, of cruciform section which has two perpendicular branches 22, 23 and extends axially over a distance greater than the stroke of the piston 3.
  • the body 1 of the jack comprises two substantially radial orifices 20, 21 diametrically opposite which open into the bore 2 in line with one of the two branches 22, 23 of the free volume.
  • These orifices 20, 21 are equipped with bearings 24, 25 in which are rotatably mounted sealingly the ends of the operating shaft 26 which passes right through the bore 2, passing through the branch 23 of the cruciform free volume.
  • the branch 22 of the cruciform free volume serves, for its part, to receive and allow the movement of the elements of the device for converting the rectilinear movement of the piston 3 into a rotational movement of the operating shaft 26.
  • this device involves a lever 27, one end of which is fixedly mounted on the operating shaft 26, so as to extend substantially in the longitudinal median plane of the branch 22 and the other end of which is articulated at one end of a pair of rods 28, 28 ′ by means of a transverse axis 29, and the other end of which is pivotally mounted around a transverse axis 30 carried by the two longitudinal members 16, 17.
  • the two links 28, 28 ′ of this couple extend on either side of the lever 27 and are kept apart from one another at the level of the axis 30 by means of a spacer sleeve 32.
  • this spacer sleeve 32 is then provided so as to maintain the ends of the links 28, 28 ′ applied against the faces 33, 34 of the side members 16, 17 bordering the branch 22 of the cruciform free volume, and thus ensuring guiding permanent links 28, 28 ′ during their pivoting.
  • the coupling of the operating shaft 26 and the control shaft of the controlled device is obtained by engaging an operating square provided at the head of the control shaft, in a axial recess 35, of complementary shape, provided in the end 36 of the operating shaft 26.
  • the operating shaft 26 drives, at its other end, a device 37 for signaling the state of the actuator, housed in a housing 38 secured to the cylinder body.
  • This structure has the advantage of allowing the body to be produced by extrusion or by a similar process.
  • the operation of the previously described actuator can be of the single-acting or double-acting type.
  • the chamber 8 may for example constitute the working chamber of the actuator.
  • the supply of this chamber 8 with pressurized fluid, for example compressed air, will be ensured by an axial duct 39 provided on the body of the jack, which communicates with the internal volume of the chamber 8 by means of an inlet port 40 .
  • this conduit 41 can be used as a conduit for admitting the pressurized fluid into the chamber 9 which then constitutes a second working chamber.
  • the piston stroke can be adjusted by means of two adjustable stops 42, 43 respectively provided on the cover 6 and on the guide element 10. These two stops 42, 43 coming to bear at the end of the race on the cylinder head 5 or on the cylinder head 4.
  • An important advantage of the structure described above is that it becomes possible to produce actuators of the single-acting type, with spring return, in which the bore of the cylinder body accommodates in addition to the conversion device 27, 28 , the spring elements ensuring the return.
  • FIG. 4 illustrates an exemplary embodiment of such an actuator using cartridge springs.
  • the actuator cylinder has a body 43 of structure similar to that previously described but much more elongated.
  • This spring cartridge comprises, between two circular support shells 48, 49, a plurality of axial coil springs 50 held in their central region by an axially sliding holding disc 51.
  • One of these shells 49 is supported on the cylinder head 44 ′, while the other, slidingly mounted with sealing in the bore 52, is integral with a coaxial rod 53 which slides, with sealing, in a through hole 54 provided in the center of the partition 45 and which bears on the piston 3.
  • This rod 53 extends into the cartridge passing through a central orifice 55 forming a bearing of the holding disc 51.
  • the space between the partition 45 and the shell 48 then forms an auxiliary working chamber 48 ′ which communicates with the intake channel 56 via an orifice 57.
  • the volume between the two shells 48, 49 is connected to the chamber 8 of the jack by means of a decompression channel 58 produced in the rod 53.

Description

La présente invention concerne un actionneur utilisant un fluide sous pression pour l'entraînement en rotation d'un arbre rotatif.The present invention relates to an actuator using a pressurized fluid for the rotary drive of a rotary shaft.

Elle s'applique plus particulièrement, mais non exclusivement, à la commande de robinets à actionnement quart de tour, tels que des robinets à papillon.It applies more particularly, but not exclusively, to the control of valves with quarter-turn actuation, such as butterfly valves.

D'une manière générale, on sait que pour assurer la commande d'un robinet, on a déjà proposé de nombreux types d'actionneurs hydrauliques ou pneumatiques faisant intervenir au moins un vérin dont la tige se déplace perpendiculairement à l'arbre de commande du robinet, et un dispositif cinématique assurant la conversion du mouvement rectiligne alternatif de la tige, en un mouvement circulaire alternatif de l'arbre de commande.In general, we know that to control a valve, we have already proposed many types of hydraulic or pneumatic actuators involving at least one actuator whose rod moves perpendicular to the control shaft of the tap, and a kinematic device ensuring the conversion of the reciprocating rectilinear movement of the rod, into an alternating circular movement of the control shaft.

Par le brevet FR 2260705 on connaît notamment un actionneur dans lequel le vérin comprend deux cylindres assemblés l'un à l'autre et traversés, au niveau de leur jonction, par l'arbre de commande. L'entraînement de cet arbre est assuré par une bielle directement articulée sur un double piston qui coulisse dans le cylindre.The patent FR 2260705 discloses in particular an actuator in which the jack comprises two cylinders assembled to each other and crossed, at their junction, by the control shaft. The drive of this shaft is ensured by a connecting rod directly articulated on a double piston which slides in the cylinder.

Il s'avère que les actionneurs de ce genre présentent des structures relativement complexes utilisant un nombre relativement élevé de pièces à usiner, et sont en conséquence lourds, encombrants et d'un coût de fabrication relativement élevé.It turns out that actuators of this kind have relatively complex structures using a relatively large number of workpieces, and are consequently heavy, bulky and of relatively high manufacturing cost.

L'invention a donc plus particulièrement pour but de simplifier cette structure, en conservant les principaux avantages de ce type d'actionneurs, afin d'obtenir un ensemble plus compact, plus léger et plus économique.The invention therefore more particularly aims to simplify this structure, while retaining the main advantages of this type of actuator, in order to obtain a more compact, lighter and more economical assembly.

Elle propose donc à cet effet un actionneur faisant coopérer un vérin comportant un corps tubulaire fermé à chacune de ses extrémités par une culasse respective, et muni d'un alésage cylindrique à l'intérieur duquel coulisse un piston comportant un opercule circulaire muni, à sa périphérie, d'une garniture d'étanchéité assurant une étanchéité coulissante avec la surface cylindrique de l'alésage, cet opercule délimitant, à l'intérieur dudit alésage, deux chambres dont au moins l'une constitue une chambre de travail dans laquelle débouche un conduit d'admission de fluide sous pression et, d'autre part, un dispositif de conversion du mouvement rectiligne du piston en un mouvement de rotation d'un arbre de manoeuvre qui s'étend à l'intérieur dudit alésage et passe au travers d'au moins un orifice prévu dans ledit corps, ce dispositif de conversion comprenant au moins une bielle dont l'une des extrémités est articulée sur le piston et dont l'autre extrémité est articulée à un bras de levier monté fixement sur ledit arbre de manoeuvre, ladite bielle et ledit bras s'étendant dans des plans orthogonaux à l'axe dudit arbre de manoeuvre.To this end, it therefore proposes an actuator making a cylinder cooperate, comprising a tubular body closed at each of its ends by a respective cylinder head, and provided with a cylindrical bore inside which slides a piston comprising a circular cover provided, at its periphery, of a seal ensuring a sliding seal with the cylindrical surface of the bore, this cover delimiting, inside said bore, two chambers, at least one of which constitutes a working chamber into which opens a pressurized fluid inlet duct and, on the other hand, a device for converting the rectilinear movement of the piston into a rotational movement of an operating shaft which extends inside said bore and passes through d '' at least one orifice provided in said body, this conversion device comprising at least one connecting rod, one end of which is articulated on the piston and the other end of which is articulated to a lever arm mounted fixedly on said control shaft, said rod and said arm extending in orthogonal to the axis of said actuating shaft plans.

Selon l'invention, cet actionneur est caractérisé en ce que le susdit piston comprend, axialement décalé par rapport audit opercule, un élément de guidage coulissant sur l'alésage, sans réaliser de séparation étanche du volume délimité par ledit alésage, cet élément de guidage étant relié à l'opercule par quatre longerons disposés symétriquement par rapport à l'axe longitudinal de symétrie de l'alésage de manière à délimiter au moins un volume libre de section cruciforme présentant deux branches perpendiculaires, à savoir:

  • ― une première branche au travers de laquelle passe le susdit arbre de manoeuvre, et
  • ― une deuxième branche dans laquelle peuvent se débattre le susdit bras de levier et la susdite bielle.
According to the invention, this actuator is characterized in that the aforesaid piston comprises, axially offset with respect to said cover, a guide element sliding on the bore, without effecting a tight separation of the volume delimited by said bore, this guide element being connected to the cover by four beams arranged symmetrically by relative to the longitudinal axis of symmetry of the bore so as to delimit at least one free volume of cruciform section having two perpendicular branches, namely:
  • - a first branch through which the aforesaid operating shaft passes, and
  • - a second branch in which the aforementioned lever arm and the aforesaid connecting rod can be discussed.

Il convient de noter que l'arbre de manoeuvre peut faire partie intégrante de l'actionneur et comprendre des moyens d'accouplement avec l'arbre d'actionnement du dispositif commandé. Dans ce cas, le corps du vérin pourra avantageusement comprendre un deuxième orifice diamétralement opposé et coaxial au premier, l'arbre de manoeuvre étant alors monté rotatif au niveau de ces deux orifices.It should be noted that the operating shaft can be an integral part of the actuator and include means for coupling with the actuating shaft of the controlled device. In this case, the cylinder body may advantageously comprise a second orifice diametrically opposite and coaxial with the first, the operating shaft then being mounted to rotate at the level of these two orifices.

Cet arbre de manoeuvre peut également consister en un tronçon de l'arbre d'actionnement du dispositif commandé, qui vient alors s'engager dans l'alésage du corps du vérin en passant par l'un au moins des susdits orifices.This operating shaft can also consist of a section of the actuating shaft of the controlled device, which then engages in the bore of the body of the jack passing through at least one of the above-mentioned orifices.

Selon une autre caractéristique de l'invention, le susdit vérin est de type à double effet. Dans ce cas, le piston délimite, à l'intérieur de l'alésage du corps du vérin, deux chambres de travail opposées dans lesquelles débouchent deux conduits d'admission respectifs, l'une des deux chambres logeant le susdit dispositif de conversion. Dans ce cas, des moyens d'étanchéité devront être prévus au niveau des pivoteries de l'arbre de manoeuvre dans les orifices du corps du vérin.According to another characteristic of the invention, the above-mentioned cylinder is of the double-acting type. In this case, the piston delimits, inside the bore of the cylinder body, two opposite working chambers into which open two respective intake ducts, one of the two chambers housing the above-mentioned conversion device. In this case, sealing means must be provided at the pivoting of the operating shaft in the orifices of the cylinder body.

Des modes de réalisation de l'invention seront décrits ci-après, à titre d'exemples non limitatifs, avec référence aux dessins annexés dans lesquels:

  • La figure 1 est une coupe axiale, dans un plan perpendiculaire à l'arbre de manoeuvre, d'un actionneur selon un mode d'exécution préféré de l'invention;
  • La figure 2 est une coupe transversale selon B-B de la figure 1;
  • La figure 3 est coupe axiale de l'actionneur représenté figure 1, dans un plan passant par l'axe de l'arbre de manoeuvre;
  • La figure 4 est une vue, partiellement en coupe, d'un actionneur du type de celui représenté sur la figure 1, mais dans lequel le vérin est à simple effet avec rappel par ressort.
Embodiments of the invention will be described below, by way of nonlimiting examples, with reference to the appended drawings in which:
  • Figure 1 is an axial section, in a plane perpendicular to the operating shaft, of an actuator according to a preferred embodiment of the invention;
  • Figure 2 is a cross section along BB of Figure 1;
  • Figure 3 is an axial section of the actuator shown in Figure 1, in a plane passing through the axis of the operating shaft;
  • Figure 4 is a view, partially in section, of an actuator of the type shown in Figure 1, but wherein the cylinder is single acting with spring return.

Tel que représenté sur les figures 1 à 3, l'actionneur comprend un corps tubulaire 1 à alésage cylindrique 2, à l'intérieur duquel coulisse avec étanchéité un piston 3, ce corps tubulaire 1 étant fermé à chacune de ses extrémités par une culasse respective 4, 5.As shown in Figures 1 to 3, the actuator comprises a tubular body 1 with a cylindrical bore 2, inside which slides a piston 3, this tubular body 1 being closed at each of its ends by a respective cylinder head 4, 5.

Ce piston 3 comporte à l'une de ses extrémités un opercule circulaire 6 de diamètre sensiblement égal à celui de l'alésage 2 et muni, à sa périphérie, d'une garniture d'étanchéité (joint torique 7) qui assure une étanchéité coulissante avec la surface cylindrique de l'alésage 2.This piston 3 has at one of its ends a circular cover 6 of diameter substantially equal to that of the bore 2 and provided, at its periphery, with a seal (O-ring 7) which provides a sliding seal with the cylindrical surface of bore 2.

Cet opercule 6 délimite donc deux chambres 8, 9 à volume variable hermétiquement isolées l'une de l'autre. Il est maintenu coaxialement à l'alésage 2 grâce à un élément de guidage 10 consistant en une pièce plate qui s'étend radialement dans l'alésage et présente deux bordures circulaires 11, 12 opposées sensiblement au diamètre de l'alésage 2, munies de garnitures anti-friction, et deux bordures opposées 13, 14 éventuellement rectilignes qui s'étendent entre les extrémités opposées des bordures circulaires 11, 12. Cet élément de guidage 10 est relié à l'opercule 6 par quatre longerons axiaux 16, 17, 18, 19 en forme de cornière disposés symétriquement par rapport à l'axe longitudinal de symétrie XX′ de l'alésage 2 avec leurs concavités orientées à l'opposé dudit axe.This cover 6 therefore delimits two chambers 8, 9 with variable volume hermetically isolated from one another. It is held coaxially with the bore 2 thanks to a guide element 10 consisting of a flat part which extends radially in the bore and has two circular edges 11, 12 opposite substantially the diameter of the bore 2, provided with anti-friction linings, and two opposite edges 13, 14 possibly rectilinear which extend between the opposite ends of the circular edges 11, 12. This guide element 10 is connected to the cover 6 by four axial longitudinal members 16, 17, 18 , 19 in the form of an angle iron arranged symmetrically with respect to the longitudinal axis of symmetry XX ′ of the bore 2 with their concavities oriented opposite to said axis.

Ces longerons 16 à 19 délimitent entre eux un volume libre axialement allongé, de section cruciforme qui présente deux branches perpendiculaires 22, 23 et s'étend axialement sur une distance supérieure à la course du piston 3.These longitudinal members 16 to 19 delimit between them an axially elongated free volume, of cruciform section which has two perpendicular branches 22, 23 and extends axially over a distance greater than the stroke of the piston 3.

Par ailleurs, le corps 1 du vérin comprend deux orifices sensiblement radiaux 20, 21 diamétralement opposés qui débouchent dans l'alésage 2 au droit de l'une des deux branches 22, 23 du volume libre.Furthermore, the body 1 of the jack comprises two substantially radial orifices 20, 21 diametrically opposite which open into the bore 2 in line with one of the two branches 22, 23 of the free volume.

Ces orifices 20, 21 sont équipés de paliers 24, 25 dans lesquels sont montées rotatives avec étanchéité les extrémités de l'arbre de manoeuvre 26 qui traverse de part en part l'alésage 2, en passant par la branche 23 du volume libre cruciforme.These orifices 20, 21 are equipped with bearings 24, 25 in which are rotatably mounted sealingly the ends of the operating shaft 26 which passes right through the bore 2, passing through the branch 23 of the cruciform free volume.

Pour faire en sorte que le piston 3 puisse coulisser selon une course déterminée, il conviendra de faire en sorte que la longueur (axiale) de la branche 23 du volume libre cruciforme soit au moins égale à la somme de la course du piston 3 et du diamètre de l'arbre de manoeuvre 26.To ensure that the piston 3 can slide along a determined stroke, it will be necessary to ensure that the (axial) length of the branch 23 of the cruciform free volume is at least equal to the sum of the stroke of the piston 3 and the operating shaft diameter 26.

La branche 22 du volume libre cruciforme sert, quant à elle, à recevoir et à permettre le débattement des éléments du dispositif de conversion du mouvement rectiligne du piston 3 en un mouvement de rotation de l'arbre de manoeuvre 26.The branch 22 of the cruciform free volume serves, for its part, to receive and allow the movement of the elements of the device for converting the rectilinear movement of the piston 3 into a rotational movement of the operating shaft 26.

Tel que représenté sur ces figures, ce dispositif fait intervenir un levier 27 dont une extrémité est montée fixement sur l'arbre de manoeuvre 26, de manière à s'étendre sensiblement dans le plan médian longitudinal de la branche 22 et dont l'autre extrémité est articulée à l'une des extrémités d'un couple de biellettes 28, 28′ au moyen d'un axe transversal 29, et dont l'autre extrémité est montée pivotante autour d'un axe transversal 30 porté par les deux longerons 16, 17.As shown in these figures, this device involves a lever 27, one end of which is fixedly mounted on the operating shaft 26, so as to extend substantially in the longitudinal median plane of the branch 22 and the other end of which is articulated at one end of a pair of rods 28, 28 ′ by means of a transverse axis 29, and the other end of which is pivotally mounted around a transverse axis 30 carried by the two longitudinal members 16, 17.

Les deux biellettes 28, 28′ de ce couple s'étendent de part et d'autre du levier 27 et sont maintenues écartées l'une de l'autre au niveau de l'axe 30 grâce à une douille entretoise 32.The two links 28, 28 ′ of this couple extend on either side of the lever 27 and are kept apart from one another at the level of the axis 30 by means of a spacer sleeve 32.

La longueur de cette douille entretoise 32 est alors prévue de manière à maintenir les extrémités des biellettes 28, 28′ appliquées contre les faces 33, 34 des longerons 16, 17 bordant la branche 22 du volume libre cruciforme, et d'assurer ainsi un guidage permanent des biellettes 28, 28′ au cours de leur pivotement.The length of this spacer sleeve 32 is then provided so as to maintain the ends of the links 28, 28 ′ applied against the faces 33, 34 of the side members 16, 17 bordering the branch 22 of the cruciform free volume, and thus ensuring guiding permanent links 28, 28 ′ during their pivoting.

Cette disposition s'avère particulièrement avantageuse en comparaison des solutions classiques dans lesquelles le guidage des pieds des biellettes s'obtient habituellement grâce à des rainures usinées dans le carter (disposition par ailleurs incompatible avec la solution proposée par l'invention).This arrangement proves to be particularly advantageous in comparison with conventional solutions in which the guidance of the feet of the links is usually obtained by means of grooves machined in the casing (arrangement which is also incompatible with the solution proposed by the invention).

Le principe de fonctionnement du dispositif de conversion à levier 27 et biellettes 28, 28′ est bien connu et ne fera donc pas l'objet d'une description détaillée. Il suffira simplement de rappeler qu'un déplacement en translation du piston 3 engendrera, par le biais des biellettes 28, 28′ et du levier 27, un mouvement de rotation de l'arbre de manoeuvre 26 lequel, grâce à un dispositif d'accouplement approprié, entraînera en rotation l'arbre de commande du dispositif commandé.The operating principle of the lever conversion device 27 and links 28, 28 ′ is well known and will therefore not be described in detail. It will suffice simply to recall that a translational movement of the piston 3 will generate, by means of the links 28, 28 ′ and of the lever 27, a movement of rotation of the operating shaft 26 which, thanks to a coupling device appropriate, will rotate the control shaft of the controlled device.

Dans l'exemple représenté, l'accouplement de l'arbre de manoeuvre 26 et de l'arbre de commande du dispositif commandé s'obtient par un engagement d'un carré de manoeuvre prévu en tête de l'arbre de commande, dans un évidement axial 35, de forme complémentaire, prévu dans l'extrémité 36 de l'arbre de manoeuvre 26.In the example shown, the coupling of the operating shaft 26 and the control shaft of the controlled device is obtained by engaging an operating square provided at the head of the control shaft, in a axial recess 35, of complementary shape, provided in the end 36 of the operating shaft 26.

Par ailleurs, l'arbre de manoeuvre 26 entraîne, à son autre extrémité, un dispositif de signalisation 37 de l'état de l'actionneur, logé dans un boîtier 38 solidaire du corps du vérin.Furthermore, the operating shaft 26 drives, at its other end, a device 37 for signaling the state of the actuator, housed in a housing 38 secured to the cylinder body.

A cet effet, le corps présente une forme prismatique délimitant deux chambres s'étendant axialement côte à côte, à savoir:

  • ― une chambre cylindrique (délimitée par l'alésage 2), qui est dévolue à la fourniture de puissance, et
  • ― une chambre S, de section sensiblement trapézoïdale, refermée à ses deux extrémités par deux culasses respectives C₁, C₂, qui peut servir à recevoir un dispositif de signalisation intégré (par exemple un dispositif de signalisation électrique).
To this end, the body has a prismatic shape delimiting two chambers extending axially side by side, namely:
  • - a cylindrical chamber (delimited by bore 2), which is used for the supply of power, and
  • - A chamber S, of substantially trapezoidal section, closed at its two ends by two respective cylinder heads C₁, C₂, which can be used to receive an integrated signaling device (for example an electrical signaling device).

Cette structure présente l'avantage de permettre la réalisation du corps par extrusion ou par un procédé similaire.This structure has the advantage of allowing the body to be produced by extrusion or by a similar process.

Le fonctionnement de l'actionneur précédemment décrit peut être de type simple effet ou double effet.The operation of the previously described actuator can be of the single-acting or double-acting type.

Ainsi, dans le cas d'un fonctionnement de type simple effet, la chambre 8 pourra par exemple constituer la chambre de travail de l'actionneur. L'alimentation de cette chambre 8 en fluide sous pression, par exemple en air comprimé, sera assurée par un conduit axial 39 prévu sur le corps du vérin, qui communique avec le volume intérieur de la chambre 8 grâce à un orifice d'admission 40.Thus, in the case of a single-acting type of operation, the chamber 8 may for example constitute the working chamber of the actuator. The supply of this chamber 8 with pressurized fluid, for example compressed air, will be ensured by an axial duct 39 provided on the body of the jack, which communicates with the internal volume of the chamber 8 by means of an inlet port 40 .

L'écoulement du fluide contenu dans la chambre 9 qui contient le dispositif de conversion 27, 28 peut alors s'effectuer au moyen d'un conduit d'échappement 41.The flow of the fluid contained in the chamber 9 which contains the conversion device 27, 28 can then take place by means of an exhaust duct 41.

Il est clair que dans le cas d'un fonctionnement de type à double effet, ce conduit 41 peut être utilisé en tant que conduit d'admission du fluide sous pression dans la chambre 9 qui constitue alors une deuxième chambre de travail.It is clear that in the case of a double-acting type of operation, this conduit 41 can be used as a conduit for admitting the pressurized fluid into the chamber 9 which then constitutes a second working chamber.

Dans tous les cas, la course du piston pourra être réglée au moyen de deux butées réglables 42, 43 respectivement prévues sur l'opercule 6 et sur l'élément de guidage 10. Ces deux butées 42, 43 venant porter en fin de course sur la culasse 5 ou sur la culasse 4.In all cases, the piston stroke can be adjusted by means of two adjustable stops 42, 43 respectively provided on the cover 6 and on the guide element 10. These two stops 42, 43 coming to bear at the end of the race on the cylinder head 5 or on the cylinder head 4.

Un avantage important de la structure précédemment décrite consiste en ce qu'il devient possible de réaliser des actionneurs de type à simple effet, avec rappel par ressort, dans lesquels l'alésage du corps du vérin loge en plus du dispositif de conversion 27, 28, les éléments de ressort assurant le rappel.An important advantage of the structure described above is that it becomes possible to produce actuators of the single-acting type, with spring return, in which the bore of the cylinder body accommodates in addition to the conversion device 27, 28 , the spring elements ensuring the return.

La figure 4 illustre un exemple de réalisation d'un tel actionneur utilisant des ressorts en cartouches.FIG. 4 illustrates an exemplary embodiment of such an actuator using cartridge springs.

Dans cet exemple, le vérin de l'actionneur présente un corps 43 de structure similaire à celle précédemment décrite mais beaucoup plus allongé.In this example, the actuator cylinder has a body 43 of structure similar to that previously described but much more elongated.

Le volume délimité par l'alésage de ce corps 43 et par les deux culasses 44, 44′ est alors divisé en deux parties par une cloison centrale 45, à savoir:

  • ― une première partie 46, située à droite de la figure 4, qui renferme tous les éléments de l'actionneur représenté figure 1 et, en particulier, le piston 3, l'arbre de manoeuvre 26 et le dispositif de conversion 27, 28, 28′; et
  • ― une deuxième partie 47 servant à loger une cartouche à ressorts.
The volume delimited by the bore of this body 43 and by the two cylinder heads 44, 44 ′ is then divided into two parts by a central partition 45, namely:
  • A first part 46, located to the right of FIG. 4, which contains all the elements of the actuator shown in FIG. 1 and, in particular, the piston 3, the operating shaft 26 and the conversion device 27, 28, 28 ′; and
  • - A second part 47 used to house a spring cartridge.

Cette cartouche à ressorts comprend, entre deux coquilles d'appui circulaires 48, 49, une pluralité de ressorts axiaux 50 hélicoïdaux maintenus dans leur région centrale par un disque de maintien axialement coulissant 51. L'une de ces coquilles 49 est en appui sur la culasse 44′, tandis que l'autre, montée coulissante avec étanchéité dans l'alésage 52, est solidaire d'une tige coaxiale 53 qui coulisse, avec étanchéité, dans un orifice de passage 54 prévu au centre de la cloison 45 et qui prend appui sur le piston 3.This spring cartridge comprises, between two circular support shells 48, 49, a plurality of axial coil springs 50 held in their central region by an axially sliding holding disc 51. One of these shells 49 is supported on the cylinder head 44 ′, while the other, slidingly mounted with sealing in the bore 52, is integral with a coaxial rod 53 which slides, with sealing, in a through hole 54 provided in the center of the partition 45 and which bears on the piston 3.

Cette tige 53 se prolonge dans la cartouche en passant par un orifice central 55 formant palier du disque de maintien 51.This rod 53 extends into the cartridge passing through a central orifice 55 forming a bearing of the holding disc 51.

L'espace compris entre la cloison 45 et la coquille 48 forme alors une chambre de travail auxiliaire 48′ qui communique avec le canal d'admission 56 par l'intermédiaire d'un orifice 57.The space between the partition 45 and the shell 48 then forms an auxiliary working chamber 48 ′ which communicates with the intake channel 56 via an orifice 57.

Par ailleurs, le volume compris entre les deux coquilles 48, 49 est relié à la chambre 8 du vérin grâce à un canal de décompression 58 réalisé dans la tige 53.Furthermore, the volume between the two shells 48, 49 is connected to the chamber 8 of the jack by means of a decompression channel 58 produced in the rod 53.

Il est clair que sous l'effet d'un fluide sous pression admis dans le canal d'admission 56, la pression engendrée dans la chambre 9 du vérin et dans la chambre auxiliaire 48′ provoquera un déplacement vers la gauche du piston 3 et de la coquille 48, contre l'effet des ressorts 50.It is clear that under the effect of a pressurized fluid admitted into the intake channel 56, the pressure generated in the chamber 9 of the jack and in the auxiliary chamber 48 ′ will cause a displacement to the left of the piston 3 and the shell 48, against the effect of the springs 50.

Ce déplacement se poursuivra jusqu'à ce que la butée réglable 59 prévue à l'extrémité de la tige 53 vienne en appui sur la culasse 44, 44′.This movement will continue until the adjustable stop 59 provided at the end of the rod 53 comes to bear on the cylinder head 44, 44 ′.

Il convient de préciser qu'au cours de ce déplacement, l'énergie du fluide sous pression à l'intérieur de la chambre de travail auxiliaire servira essentiellement à assurer la compression des ressorts 50, de manière à conserver intégralement le couple utile que présenterait l'actionneur en l'absence des moyens élastiques de rappel.It should be noted that during this movement, the energy of the pressurized fluid inside the auxiliary working chamber will essentially be used to ensure the compression of the springs 50, so as to fully conserve the useful torque which would be present. 'actuator in the absence of elastic return means.

Il est clair qu'ensuite, le retour du piston 3 à sa position initiale sera assuré, lors d'une chute de pression du fluide d'admission, grâce à l'énergie emmagasinée par les ressorts 50.It is clear that thereafter, the return of the piston 3 to its initial position will be ensured, during a pressure drop of the intake fluid, thanks to the energy stored by the springs 50.

Il ressort de ce qui précède que la solution proposée par l'invention apporte les avantages suivants:

  • ― l'intégration de la cinématique à bielle et manivelle à l'intérieur du vérin amène une plus grande compacité par rapport aux solutions antérieures et permet un usinage plus simple de ce seul corps de vérin par rapport aux deux usinages qui étaient réalisés antérieurement;
  • ― le guidage des pieds de biellette qui se faisait jusqu'ici dans des rainures usinées dans le carter se fait maintenant par l'intermédiaire du piston lui-même et utilise ainsi l'usinage du cylindre comme surface de portée, ce qui simplifie à la fois construction et usinage.
It appears from the above that the solution proposed by the invention provides the following advantages:
  • - the integration of the kinematics with rod and crank inside the cylinder brings a greater compactness compared to the previous solutions and allows a simpler machining of this single cylinder body compared to the two machining operations which were carried out previously;
  • - the link rod guide which has hitherto been done in grooves machined in the housing is now done by means of the piston itself and thus uses the machining of the cylinder as a bearing surface, which simplifies the both construction and machining.

Claims (12)

1. Actuator using a pressurized fluid for driving a rotary shaft, this actuator comprising a thrustor having a tubular body (1) closed at each end by a respective cylinder head (4, 5), and having a cylindrical bore (2) inside which slides a piston (3) comprising a circular plug (6) having, at its periphery, a sealed packing (7) providing sliding sealing with the cylindrical surface of the bore, this plug defining, inside said bore, two chambers (8, 9) one at least of which forms a work chamber into which opens a pressurized fluid intake duct (39, 40) and, on the other hand, a device (27, 28, 28′) for converting the rectilinear movement of the piston (3) into a rotational movement of a control shaft (26) which extends inside said bore and passes through at least one orifice provided in said body, this conversion device comprising at least one link (28, 28′), one of the ends of which is articulated to the piston (3) and the other end of which is articulated to a lever arm (27) mounted fixedly on said control shaft (26), said link (28, 28′) and said arm (27) extending in planes orthogonal to the axis of said control shaft (26), characterized in that said tubular body (1) is in one piece and in that said piston (3) comprises, offset axially with respect to said plug (6), a guide element (10) sliding on the bore (2), without causing sealed separation of the volume defined by said bore (2), this guide element (10) being connected to the plug (6) by four longitudinal members (16 to 19) disposed symmetrically with respect to the longitudinal axis of symmetry (XX′) of the bore (2) so as to define at least one free volume having a cruciform cross section with two perpendicular branches, namely:
― a first branch (23) through which said control shaft passes, and
― a second branch (22) in which said lever arm (27) and said link may move.
2. Actuator according to claim 1, characterized in that said link (28, 28′) is mounted for rotation, by one of its ends about a transverse shaft (30) fast with two facing longitudinal members (16, 17).
3. Actuator according to one of the preceding claims, characterized in that said piston (3) comprises means for guiding said links (28, 28′).
4. Actuator according to one of the preceding claims, characterized in that said control shaft (26) forms an integral part of the actuator and comprises means for coupling with a drive shaft of the controlled device.
5. Actuator according to claim 4, characterized in that the body (1) of the thrustor comprises a second orifice (21) diametrically opposite and coaxial with the first one (20), and in that the control shaft (26) is mounted for rotation at the level of these two orifices (20, 21).
6. Actuator according to one of the preceding claims, characterized in that said control shaft (26) consists of a section of the drive shaft of the controlled device, which is then engaged in the bore (2) of the thrustor body (1) by passing through one at least of said orifices (20).
7. Actuator according to one of the preceding claims, characterized in that the piston (3) defines, inside the bore of the thrustor body, two opposite work chambers (8, 9) into which two respective intake ducts (39, 40 and 41) open, one of the two chambers (9) housing said conversion device and in that, in this case, sealing means are provided at the level of the journals of the control shaft (26) in the orifices (20, 21) of the thrustor body.
8. Actuator according to claim 5, characterized in that the control shaft (26) drives, through one of its ends situated opposite the controlled device, a device (37) signalling the state of the actuator, housed in a case (38) fast with the thrustor body.
9. Actuator according to claim 8, characterized in that said body has a prismatic shape defining two chambers extending axially side by side, namely:
― a cylindrical chamber defined by said bore (2), and
― a chamber (S), closed at both its ends by two respective cylinder heads (C₁, C₂), for receiving said signalling device (37).
10. Actuator according to claim 9, characterized in that said body (1) is obtained by extrusion.
11. Actuator according to one of the preceding claims, characterized in that said thrustor is of the single-acting type and in that said bore (2) further contains resilient means (50) for return of the piston (3).
12. Actuator according to claim 11, characterized in that the volume defined by said bore is divided into two parts by a transverse dividing wall, namely:
― a first part (46) containing the piston (3), the control shaft (26) and the conversion device device (27, 28, 28′); and
― a second part (47) for housing a spring cartridge and which comprises, facing said dividing wall (45), a shell (48) on which said resilient means (50) come to bear, this shell (48) being mounted for sealingly sliding in said bore (52) and is connected to said piston (3) by a coaxial rod (53) which slides sealingly in a passage orifice (54) provided in the centre of the dividing wall (45), the space between the dividing wall (45) and the shell (48) forming an auxiliary work chamber into which opens a pressurized fluid intake channel (56).
EP88400548A 1988-03-09 1988-03-09 Fluid actuator for driving a rotary shaft Expired - Lifetime EP0331854B1 (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
DE8888400548T DE3864814D1 (en) 1988-03-09 1988-03-09 PRESSURE-OPERATED DEVICE FOR DRIVING A TURN SHAFT.
EP88400548A EP0331854B1 (en) 1988-03-09 1988-03-09 Fluid actuator for driving a rotary shaft
DE198888400548T DE331854T1 (en) 1988-03-09 1988-03-09 LIQUID ACTUATING DEVICE FOR DRIVING A TURN SHAFT.
ES88400548T ES2010174B3 (en) 1988-03-09 1988-03-09 ACTUATOR USING A PRESSURE FLUID TO DRAG A ROTATING TREE IN ROTATION
US07/321,195 US4995305A (en) 1988-03-09 1989-03-09 Actuator employing a fluid under pressure for the driving in rotation of a rotary shaft
JP1057665A JPH01312206A (en) 1988-03-09 1989-03-09 Actuator

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP88400548A EP0331854B1 (en) 1988-03-09 1988-03-09 Fluid actuator for driving a rotary shaft

Publications (2)

Publication Number Publication Date
EP0331854A1 EP0331854A1 (en) 1989-09-13
EP0331854B1 true EP0331854B1 (en) 1991-09-11

Family

ID=8200360

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88400548A Expired - Lifetime EP0331854B1 (en) 1988-03-09 1988-03-09 Fluid actuator for driving a rotary shaft

Country Status (5)

Country Link
US (1) US4995305A (en)
EP (1) EP0331854B1 (en)
JP (1) JPH01312206A (en)
DE (2) DE3864814D1 (en)
ES (1) ES2010174B3 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1285060B1 (en) * 1996-04-26 1998-06-03 Magneti Marelli Spa ACTUATOR GROUP WITH FLUID CONTROL.
JP4944696B2 (en) * 2006-08-04 2012-06-06 株式会社キッツ Spring return pneumatic actuator
US20220403949A1 (en) * 2019-11-25 2022-12-22 Emerson Process Management Regulator Technologies, Inc. Scotch Yoke Actuator

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR535262A (en) * 1920-05-27 1922-04-12 Cie Gen De Signalisation Improvements to the remote control of motors of winches, capstans and other machines
GB255245A (en) * 1925-08-06 1926-07-22 John William Wood Improved variable stroke engine for operating jigging or reciprocating conveyors andlike appliances
GB838647A (en) * 1956-12-28 1960-06-22 Alfred Roland Cross Improvements in or relating to servo motors
US3088441A (en) * 1960-07-11 1963-05-07 Bacchi Ray Valve actuator
US3452961A (en) * 1966-05-02 1969-07-01 Keystone Valve Corp Disc valve operator with compound driving linkage
US3709106A (en) * 1970-09-14 1973-01-09 H Shafer Piston operator for imparting rotary motion
SE360721B (en) * 1971-10-19 1973-10-01 Saab Scania Ab
DE2344932A1 (en) * 1972-10-19 1974-04-25 Homer John Shafer DOUBLE CYLINDER DRIVE FOR GENERATING A ROTATING MOVEMENT
FI55396C (en) * 1974-02-11 1979-07-10 Neles Oy MANOEVRERINGSANORDNING
GB1476069A (en) * 1975-02-17 1977-06-10 Yazaki H Drive device for a valve actuaction shaft
GB1500404A (en) * 1976-09-03 1978-02-08 Kermode D Torque generating actuator
GB2069051B (en) * 1980-01-24 1983-06-22 Camtorc Ltd Rotary actuator
JPS5824605A (en) * 1981-08-04 1983-02-14 Tomoe Gijutsu Kenkyusho:Kk Rotary actuator
JPS58131412A (en) * 1982-01-28 1983-08-05 Hideo Nakagawa Fluid pressure cylinder
CA1271054A (en) * 1985-10-11 1990-07-03 Paul Anthony Richter Rotary/linear convertor

Also Published As

Publication number Publication date
ES2010174A4 (en) 1989-11-01
EP0331854A1 (en) 1989-09-13
DE3864814D1 (en) 1991-10-17
US4995305A (en) 1991-02-26
JPH01312206A (en) 1989-12-18
DE331854T1 (en) 1989-12-28
ES2010174B3 (en) 1992-03-01

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