EP0089568B1 - Fluid operated linear-to-rotary actuator - Google Patents

Fluid operated linear-to-rotary actuator Download PDF

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Publication number
EP0089568B1
EP0089568B1 EP83102387A EP83102387A EP0089568B1 EP 0089568 B1 EP0089568 B1 EP 0089568B1 EP 83102387 A EP83102387 A EP 83102387A EP 83102387 A EP83102387 A EP 83102387A EP 0089568 B1 EP0089568 B1 EP 0089568B1
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EP
European Patent Office
Prior art keywords
cylinder
piston
guide
guides
pistons
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Expired
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EP83102387A
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German (de)
French (fr)
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EP0089568A1 (en
Inventor
Gerhardus Marinus Jozef Pierik
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Cessione tebel Pneumatiek Bv
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P M I de Jong BV
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Application filed by P M I de Jong BV filed Critical P M I de Jong BV
Priority to AT83102387T priority Critical patent/ATE15402T1/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
    • F15B15/065—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 rack-and-pinion type

Definitions

  • the invention relates to a pressure-actuated rotary drive or actuator according to the preamble of the main claim.
  • a device of this type is known from DE-B No. 2647385.
  • tilting moments occur during operation, which tend to cause the piston to tilt. This creates high frictional forces, which generate large surface pressures and thus severely impair the efficiency of the device and shorten the service life.
  • additional guides are provided in the known device which are laterally offset with respect to the drive guide, but whose effect is not satisfactory.
  • the object of the present invention is to increase the operational safety and the service life of the device and to improve its efficiency.
  • the guide provided with a toothed rack has, in its surface facing the cylinder wall, a groove which is arranged parallel and symmetrically to the cylinder axis and which receives the guide, which is offset by 180 ° around the longitudinal axis of the cylinder, in a form-fitting, sliding manner without a toothed rack of the other piston.
  • a cylinder is shown at 1 with two cylinder covers 2 and an inner line 3 and outer line 4 for the inflow and outflow of the medium.
  • two pistons 5 are arranged to be movable in the direction of the cylinder axis. They each have two guides 6 and 7, the guides 6 being provided with a toothed rack 8 which interact with a pinion of an actuating shaft 9.
  • the pistons 5 have circumferential sealing rings 10 and sliding rings 11 in the region of the piston crowns.
  • a sliding ring 12 is attached circumferentially to the cylinder inner wall, along which the guides 6 and the guides 7 slide together.
  • an additional channel 15 is provided which enlarges the remaining gap of the bore 3 and which runs parallel to the cylinder axis, so that the pressure medium during Inflow into the space formed between the piston crowns does not flow perpendicular to the direction of movement of the two, but rather in the direction of movement of the two pistons and thus supports the diverging movement.
  • bumps are attached to the outside of the piston crowns in order to fix springs which run coaxially to the cylinder axis and which are supported on the cylinder covers and return the pistons from the open position to the closed position that, for example, due to a leak with the pressure medium, pressure can no longer be built up.
  • the racks 8 are positively and non-positively fitted into the guides 6, so that they no longer leave their position without additional fasteners, even in alternating operation.
  • pins 16 can also be provided, which either glue or connect the toothed racks 8 to the guides 6 as dowel pins. If the toothed rack shape is less precisely matched to the shape of the guides 6, the toothed racks are held by means of screws, forces which want to lift the toothed racks out of the guides only have to be absorbed by the screws.
  • the guides 6 provided with a toothed rack 8 are provided in their surface facing the cylinder wall with a groove 23 oriented parallel and symmetrically to the cylinder axis, which guides the opposite guide 7 without toothed rack, offset by 180 ° about the longitudinal axis of the cylinder the other piston slidably receives.
  • each guide 6, apart from the groove 23, is equipped with symmetrically arranged guide surfaces 24 which are wide in the direction of the circumference of the cylinder inner wall and substantially exceed the width of the toothed racks.
  • the piston 5a is formed so that the seals 10a and g s 11 receiving guide surfaces 17 are aligned so that a far-reaching driving interengagement of auffactzubewegten piston is possible.
  • the cylinder cover 2 is then designed accordingly, so that there is still sufficient space for the air to enter.
  • FIG. 5 shows the embodiment of a device in which springs 20 per se belonging to the prior art are used. While in this embodiment the piston is designed, for example, in accordance with the embodiment in accordance with FIG. 1, but can also be designed in the same way in accordance with the embodiment in accordance with FIG to accomplish.
  • a damping device is additionally provided in a modification of the embodiment shown in FIGS. 1 to 5.
  • the cylinder space is penetrated by a web 25 which does not hinder the movements of the guides 6 and which serves to accommodate bores for the pressure medium supply and discharge lines and which at the same time represents the damper device on one side of the cylinder.
  • Bores 26 and 27 are provided both in the web 25 and in the cylinder cover 2.
  • the actual damping device 28 is installed in the piston 5 and, in the exemplary embodiment shown, is formed from two projections 29 and 30 projecting beyond the piston surfaces on both sides.
  • the plungers are dimensioned and arranged such that they are aligned with the bores 26 and 27 and can be guided into these bores 26 and 27, the bores having sealing rings, so that the plungers are tightly guided within the bores.
  • a throttle bore 31 is additionally provided and a bypass line 32, which is formed from a check valve, which in the illustrated embodiment consists of a ball 33 (FIG. 8), which is arranged in a ball cage which has a valve seat 34 .
  • the ball In the position shown in Fig. 8, the ball is in a position in which the bypass line is not closed, i. H. the ball does not rest on a valve seat, but, for example, on holding fingers, which allow the pressure medium to flow around it.
  • a bypass line 35 designed in the same way is provided in the cylinder cover 2 and a throttle bore 36 is also arranged in the cylinder cover 2, the two components 35 and 36 creating a connection between the cylinder space and the associated pressure medium supply and discharge line.
  • the ball of the check valve in the bypass line 35 bears against the valve seat, i. H. seals.
  • the pressure medium inlet and outlet lines can also be seen in the drawing, the line system, for example serving as a line, subsequently consisting of lines 401, 402 and 403, i.e. the compressed air supplied here leads to the rear of the plunger 30, lifts the valve ball 33 of the bypass line 32 from and can thereby apply pressure to the piston surface A of the piston 5.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

1. Fluid operated rotary drive or actuator device, with (a) a cylinder (1) and two pistons (5) which are adapted to move to and fro therein oppositely in mutual dependency, (b) a control shaft (9) with pinion, which shaft extends transversely with respect to the cylinder axis and is arranged symmetrically with respect to the two pistons (5) and the cylinder axis, (c) two guides (6, 7) which start from the piston heads are disposed parallel to the cylinder axis, extend to over the control shaft (9), are arranged on each of the two pistons (5) and comprise, at their outer side, guide surfaces which guide the piston in the cylinder (1), and the said guides are situated approximately opposite one another relatively to the longitudinal axis of the cylinder, one guide (6) comprising at its inner side a rack (8) (drive guide) which co-operates with the pinion, characterised in that the guides (6) provided with a rack (8) comprise, in their surface facing towards the cylinder wall, in each case a groove (23) which is situated parallel and symmetrically with respect to the cylinder longitudinal axis, and in the said groove there is positively and slidably accommodated the non-rack guide (7) of the other piston which is situated opposite offset by 180 degrees about the longitudinal axis of the cylinder.

Description

Die Erfindung bezieht sich auf eine druckmittelbetätigte Drehantriebs- oder -stellvorrichtung nach dem Oberbegriff des Hauptanspruches.The invention relates to a pressure-actuated rotary drive or actuator according to the preamble of the main claim.

Eine Vorrichtung dieser Art ist aus der DE-B Nr. 2647385 bekannt. Bei Vorrichtungen mit nur je einer Antriebsführung an jedem Kolben treten Kippmomente während des Betriebes auf, die dazu tendieren, dass sich der Kolben verkanten kann. Dabei treten hohe Reibungskräfte auf, die grosse Flächenpressungen erzeugen und damit den Wirkungsgrad der Vorrichtung stark beeinträchtigen sowie die Lebensdauer verkürzen. Um diese Nachteile so gering wie möglich zu halten, sind bei der bekannten Einrichtung zusätzliche, gegenüber der Antriebsführung seitlich versetzte Führungen vorgesehen, deren Wirkung aber nicht zufriedenstellend ist.A device of this type is known from DE-B No. 2647385. In devices with only one drive guide on each piston, tilting moments occur during operation, which tend to cause the piston to tilt. This creates high frictional forces, which generate large surface pressures and thus severely impair the efficiency of the device and shorten the service life. In order to keep these disadvantages as low as possible, additional guides are provided in the known device which are laterally offset with respect to the drive guide, but whose effect is not satisfactory.

Der vorliegenden Erfindung liegt die Aufgabe zugrunde, die Betriebssicherheit und die Lebensdauer der Vorrichtung zu erhöhen sowie deren Wirkungsgrad zu verbessern.The object of the present invention is to increase the operational safety and the service life of the device and to improve its efficiency.

Diese Aufgabe wird dadurch gelöst, dass die mit einer Zahnstange versehene Führung in ihrer der Zylinderwand zugewandten Oberfläche eine parallel und symmetrisch zur Zylinderachse angeordnete Nut aufweist, welche die um 180° um die Zylinderlängsachse versetzt gegenüberliegende Führung ohne Zahnstange des anderen Kolbens formschlüssig gleitend aufnimmt.This object is achieved in that the guide provided with a toothed rack has, in its surface facing the cylinder wall, a groove which is arranged parallel and symmetrically to the cylinder axis and which receives the guide, which is offset by 180 ° around the longitudinal axis of the cylinder, in a form-fitting, sliding manner without a toothed rack of the other piston.

Hiermit werden die ggf. auftretenden Kippmomente beherrscht und eine sichere Führung der Kolben erreicht, so dass Wirkungsweise und Lebensdauer der Einrichtung verbessert werden.In this way, any tilting moments that may occur are controlled and the pistons are guided securely, so that the mode of operation and service life of the device are improved.

Vorteilhafte Ausgestaltungen der im Hauptanspruch definierten Einrichtung sind in den Unteransprüchen erfasst.Advantageous refinements of the device defined in the main claim are covered in the subclaims.

Durch die Merkmale des Anspruches 7 wird erreicht, die Bewegungen der beiden Kolben in ihren jeweiligen Endstellungen zu dämpfen, um dadurch ein zu hartes Anschlagen der durch die Kolben betätigten Einrichtung, z. B. einem grossen Scheibenwischer od. dgl., zu vermeiden. In den Ansprüchen 8 bis 10 sind vorteilhafte Ausgestaltungen dieser Dämpfungseinrichtung erläutert.It is achieved by the features of claim 7 to dampen the movements of the two pistons in their respective end positions, thereby causing the device actuated by the pistons to strike too hard, e.g. B. a large wiper or the like. To avoid. Advantageous embodiments of this damping device are explained in claims 8 to 10.

Ausführungsbeispiel werden anhand der Zeichnungen erläutert. Die Zeichnungen zeigen in

  • Fig. 1 einen Längsschnitt durch eine Stellvorrichtung, wobei sich die Kolben in der sogenannten geschlossenen Stellung befinden, in
  • Fig. 2 einen Längsschnitt gemäss Fig. 1, jedoch befinden sich hier die Kolben in der sogenannten offenen Stellung, in
  • Fig. 3 einen Querschnitt durch die Vorrichtung gemäss der Linie 3-3 in Fig. 1, in
  • Fig. 4 eine zweite Ausführungsform der neuen Vorrichtung, die eine kürzere Bauweise ermöglicht, in
  • Fig. 5 eine Ausführungsform der Vorrichtung mit eingesetzten Federn, in
  • Fig. 6 einen Schnitt durch eine abgewandelte Ausführungsform mit eingebauter Dämpfereinrichtung gemäss der Linie 6-6 in Fig. 7, in
  • Fig. 7 einen Schnitt durch die Einrichtung gemäss Fig. 6 entsprechend der Linie 7-7 in Fig. 6 und in
  • Fig. 8 eine Fig. 7 vergleichbare Darstellung, bei der aber die Kolben sich bereits aus einer Endlage in eine Mittellage bewegt haben.
Embodiment will be explained with reference to the drawings. The drawings show in
  • Fig. 1 shows a longitudinal section through an adjusting device, wherein the pistons are in the so-called closed position, in
  • Fig. 2 is a longitudinal section according to FIG. 1, but here the pistons are in the so-called open position, in
  • Fig. 3 shows a cross section through the device along the line 3-3 in Fig. 1, in
  • Fig. 4 shows a second embodiment of the new device, which enables a shorter design, in
  • Fig. 5 shows an embodiment of the device with inserted springs, in
  • Fig. 6 shows a section through a modified embodiment with built-in damper device according to the line 6-6 in Fig. 7, in
  • Fig. 7 shows a section through the device of FIG. 6 along the line 7-7 in Fig. 6 and in
  • FIG. 8 shows a representation comparable to FIG. 7, but in which the pistons have already moved from an end position into a central position.

In der Zeichnung ist bei 1 ein Zylinder dargestellt mit zwei Zylinderdeckeln 2 und einer inneren Leitung 3 und äusseren Leitung 4 zum Zu- und Abfliessen des Mediums. In dem Zylinder 1 sind zwei Kolben 5 in Richtung der Zylinderachse bewegbar angeordnet. Sie weisen je zwei Führungen 6 und 7 auf, wobei die Führungen 6 mit einer Zahnstange 8 versehen sind, die mit einem Ritzel einer Stellwelle 9 zusammenwirken. Die Kolben 5 weisen im Bereich der Kolbenböden Dichtringe 10 und Gleitringe 11 umfangsmässig auf. An der Zylinderinnenwand ist ein Gleitring 12 umfangsmässig angebracht, an dem die Führungen 6 und die Führungen 7 gemeinsam entlanggleiten.In the drawing, a cylinder is shown at 1 with two cylinder covers 2 and an inner line 3 and outer line 4 for the inflow and outflow of the medium. In the cylinder 1, two pistons 5 are arranged to be movable in the direction of the cylinder axis. They each have two guides 6 and 7, the guides 6 being provided with a toothed rack 8 which interact with a pinion of an actuating shaft 9. The pistons 5 have circumferential sealing rings 10 and sliding rings 11 in the region of the piston crowns. A sliding ring 12 is attached circumferentially to the cylinder inner wall, along which the guides 6 and the guides 7 slide together.

Sollen die Kolben 5 von der in Fig. 1 dargestellten geschlossenen Stellung in die in Fig. 2 dargestellte offene Stellung bewegt werden, gelangt über die innere Leitung 3 Druckmittel in den zwischen den beiden Kolbenböden gebildeten Raum und drückt diese auseinander. Dabei kämmen die Zahnstangen 8 der beiden Führungen 6 mit dem Ritzel der Stellwelle 9, so dass sich die Stellwelle um einen gewissen Betrag dreht, bis die Kolben 5 sich in der in Fig. 2 dargestellten offenen Stellung befinden. Um den Drehwinkel der Stellwelle 9 zu beschränken, kann der Kolbenhub mittels einer verstellbaren Anschlagvorrichtung 14 begrenzt werden. Da die beiden Kolben über das Ritzel der Stellwelle 9 fest miteinander verbunden sind, genügt es, diese Anschlagvorrichtung 14 an einer Seite des Zylinders vorzusehen. Sie kann jedoch zusätzlich auch an der zweiten Seite angebracht werden.If the pistons 5 are to be moved from the closed position shown in FIG. 1 to the open position shown in FIG. 2, pressure medium passes through the inner line 3 into the space formed between the two piston heads and presses them apart. The racks 8 of the two guides 6 mesh with the pinion of the actuating shaft 9, so that the actuating shaft rotates by a certain amount until the pistons 5 are in the open position shown in FIG. 2. In order to limit the angle of rotation of the adjusting shaft 9, the piston stroke can be limited by means of an adjustable stop device 14. Since the two pistons are firmly connected to one another via the pinion of the adjusting shaft 9, it is sufficient to provide this stop device 14 on one side of the cylinder. However, it can also be attached to the second side.

Da die senkrecht zur Zylinderachse verlaufende Bohrung der Leitung 3 aus Einfachheitsgründen der Fertigung teilweise von dem Gleitring 12 im Zylinder verdeckt wird, ist ein Zusatzkanal 15 vorgesehen, der den verbleibenden Spalt der Bohrung 3 vergrössert und der parallel zur Zylinderachse verläuft, so dass das Druckmedium beim Einströmen in den zwischen den Kolbenböden gebildeten Raum nicht senkrecht zur Bewegungsrichtung der beiden einströmt, sondern in Bewegungsrichtung der beiden Kolben und damit die auseinanderführende Bewegung noch unterstützt.Since the bore of the line 3 perpendicular to the cylinder axis is partially covered by the slide ring 12 in the cylinder for reasons of simplicity of manufacture, an additional channel 15 is provided which enlarges the remaining gap of the bore 3 and which runs parallel to the cylinder axis, so that the pressure medium during Inflow into the space formed between the piston crowns does not flow perpendicular to the direction of movement of the two, but rather in the direction of movement of the two pistons and thus supports the diverging movement.

Sollen die Kolben 5 von der in Fig. 2 dargestellten offenen Stellung wieder in die geschlossene Stellung zurückgeführt werden, wird durch die äussere Leitung 4 Druckmedium in die Räume geführt, die zwischen den Kolbenböden und den Zylinderdeckeln gebildet sind. Dabei ist es bei kompressilen Druckmitteln, wie beispielsweise Luft, von Vorteil, einen möglichst kleinen Raum füllen zu müssen, da sich dann der Druck schneller aufbaut. Zu diesem Zweck sind die beiden Zylinderdeckel 2 nach innen eingezogen und verringern so den zwischen ihnen und den Kolbenböden gebildeten Raum. Bei der Bewegung der beiden Kolben aufeinanderzu wird das zwischen ihnen befindliche Druckmedium durch die innere Leitung 3 wieder abgeführt. Die Stellwelle 9 wird bei dieser Bewegung wieder in ihre Ausgangslage zurückgeführt.If the pistons 5 are to be returned from the open position shown in FIG. 2 to the closed position, pressure medium is fed through the outer line 4 into the spaces which are formed between the piston crowns and the cylinder covers. In the case of compressible pressure media, such as air, it is advantageous to have to fill the smallest possible space, since the pressure then builds up more quickly. For this purpose, the two cylinder covers 2 are drawn inwards and thus reduce the space formed between them and the piston crowns. When the two pistons move towards each other, this becomes between them che pressure medium discharged through the inner line 3 again. The actuating shaft 9 is returned to its starting position during this movement.

Um im Falle einer Betriebsstörung das Einnehmen dieser Ausgangsstellung zu gewährleisten, sind an der Aussenseite der Kolbenböden Erhebungen angebracht zum Fixieren von koaxial zur Zylinderachse verlaufenden Federn, die sich an den Zylinderdeckeln abstützen und die Kolben aus der offenen Stellung in die geschlossene Stellung zurückführen, im Falle, dass beispielsweise durch ein Leck mit dem Druckmittel kein Druck mehr aufgebaut werden kann.In order to ensure that this starting position is assumed in the event of a malfunction, bumps are attached to the outside of the piston crowns in order to fix springs which run coaxially to the cylinder axis and which are supported on the cylinder covers and return the pistons from the open position to the closed position that, for example, due to a leak with the pressure medium, pressure can no longer be built up.

Bei der derzeit möglichen und zum Standard gehörenden hohen Fertigungsgenauigkeit sind die Zahnstangen 8 form- und kraftschlüssig in die Führungen 6 eingepasst, so dass sie ohne weitere Befestigungsmittel ihre eingenommene Stellung auch im wechsellastigen Betrieb nicht mehr verlassen. Als zusätzliche Sicherung können jedoch noch Stifte 16 vorgesehen sein, die entweder verklebt oder als Passstifte die zahnstangen 8 mit den Führungen 6 verbinden. Bei einer weniger genauen Abstimmung der Zahnstangenform auf die Form der Führungen 6 werden die Zahnstangen mittels Schrauben gehalten, wobei Kräfte, die die Zahnstangen aus den Führungen herausheben wollen, nur von den Schrauben aufgefangen werden müssen.Given the currently high standard of manufacturing accuracy, the racks 8 are positively and non-positively fitted into the guides 6, so that they no longer leave their position without additional fasteners, even in alternating operation. As an additional safeguard, however, pins 16 can also be provided, which either glue or connect the toothed racks 8 to the guides 6 as dowel pins. If the toothed rack shape is less precisely matched to the shape of the guides 6, the toothed racks are held by means of screws, forces which want to lift the toothed racks out of the guides only have to be absorbed by the screws.

Wie aus Fig. 3 und 6 ersichtlich, sind die mit einer Zahnstange 8 versehenen Führungen 6 in ihrer der Zylinderwand zugewandten Oberfläche mit einer parallel und symmetrisch zur Zylinderachse ausgerichteten Nut 23 versehen, die die um 180° um die Zylinderlängsachse versetzt gegenüberliegende Führung 7 ohne Zahnstange des anderen Kolbens formschlüssig gleitend aufnimmt.As can be seen from FIGS. 3 and 6, the guides 6 provided with a toothed rack 8 are provided in their surface facing the cylinder wall with a groove 23 oriented parallel and symmetrically to the cylinder axis, which guides the opposite guide 7 without toothed rack, offset by 180 ° about the longitudinal axis of the cylinder the other piston slidably receives.

Wenn also im Betrieb ein Kippmoment, welches von dem Ritzel der Stellwelle 9 über die Zahnstange auf die Führung 6 und damit den Kolben 5 übertragen wird, auftritt, kann sich dieser mittels seiner der Führung 6 genau gegenüberliegenden Führung 7 optimal abstützen. Die Führung 7 stützt sich dabei an den Seitenwänden der Nut 23 ab.If a tilting moment occurs during operation, which is transmitted from the pinion of the actuating shaft 9 via the rack to the guide 6 and thus the piston 5, this can be optimally supported by means of its guide 7 which is exactly opposite the guide 6. The guide 7 is supported on the side walls of the groove 23.

Um den Kolben möglichst sicher zu führen, ist dabei jede Führung 6 ausser der Nut 23 mit in Richtung des Umfangs der Zylinderinnenwand breiten und die Breite der Zahnstangen wesentlich überschreitenden symmetrisch angeordneten Führungsflächen 24 ausgerüstet.In order to guide the piston as securely as possible, each guide 6, apart from the groove 23, is equipped with symmetrically arranged guide surfaces 24 which are wide in the direction of the circumference of the cylinder inner wall and substantially exceed the width of the toothed racks.

Bei der in Fig. 4 dargestellten Ausführungsform ist der Kolben 5a so ausgebildet, dass die Dichtun- gen 10a und 11 aufnehmende Führungsflächen 17 so ausgerichtet sind, dass ein weitgehendes Ineinanderfahren der aufeinanderzubewegten Kolben möglich ist. Bei dieser Ausführungsform wird dann der Zylinderdeckel 2 entsprechend ausgebildet, so dass hier noch ein genügender Raum für den Lufteintritt vorhanden ist.In the illustrated in Fig. 4 embodiment, the piston 5a is formed so that the seals 10a and g s 11 receiving guide surfaces 17 are aligned so that a far-reaching driving interengagement of aufeinanderzubewegten piston is possible. In this embodiment, the cylinder cover 2 is then designed accordingly, so that there is still sufficient space for the air to enter.

Während bei der Ausführungsform gemäss Fig. und 2 dieZylinderdeckel 2 eine abgeschrägte äussere Vertiefung 18 aufweisen, ist diese Vertiefung bei der Ausführungsform gemäss Fig. 4 stufenförmig ausgebildet, so dass jeweils ein Griffrand 19 geschaffen wird.While in the embodiment according to FIGS. 2 and 2 the cylinder covers 2 have a beveled outer recess 18, in the embodiment according to FIG. 4 this recess is of stepped design, so that a grip edge 19 is created in each case.

Fig. 5 zeigt die Ausführungsform einer Vorrichtung, bei der an sich zum Stand der Technik gehörende Federn 20 eingesetzt sind. Während bei dieser Ausführungsform der Kolben beispielsweise entsprechend der Ausführungsform gemäss Fig. 1 ausgebildet ist, aber in gleicher Weise.auch gemäss der Ausführungsform entsprechend Fig. 4 ausgebildet sein kann, sind die Zylinderdeckel 21 entsprechend gross gestaltet, um damit den Aufnahmeraum für die Federn 20 zu schaffen.FIG. 5 shows the embodiment of a device in which springs 20 per se belonging to the prior art are used. While in this embodiment the piston is designed, for example, in accordance with the embodiment in accordance with FIG. 1, but can also be designed in the same way in accordance with the embodiment in accordance with FIG to accomplish.

Bei den in den Fig. 6 und 7 dargestellten Ausführungsbeispielen ist in Abwandlung der in den Fig. 1 bis 5 dargestellten Ausführungsform eine Dämpfungseinrichtung zusätzlich vorgesehen. Hierfür wird der Zylinderraum von einem Steg 25 durchsetzt, der die Bewegungen der Führungen 6 nicht behindert und der Aufnahme von Bohrungen für die Druckmittelzu- und -abflussleitungen dient und der gleichzeitig die Dämpfereinrichtung auf der einen Seite des Zylinders darstellt.In the exemplary embodiments shown in FIGS. 6 and 7, a damping device is additionally provided in a modification of the embodiment shown in FIGS. 1 to 5. For this purpose, the cylinder space is penetrated by a web 25 which does not hinder the movements of the guides 6 and which serves to accommodate bores for the pressure medium supply and discharge lines and which at the same time represents the damper device on one side of the cylinder.

Sowohl in dem Steg 25 wie auch in dem Zylinderdeckel 2 sind Bohrungen 26 und 27 vorgesehen. In dem Kolben 5 ist die eigentliche Dämpfungseinrichtung 28 eingebaut, die bei dem dargestellten Ausführungsbeispiel aus zwei über die beiderseitigen Kolbenflächen vorstehenden Stössein 29 und 30 gebildet sind. Die Stössel sind so dimensioniert und angeordnet, dass sie mit den Bohrungen 26 und 27 fluchten und in diese Bohrungen 26 und 27 hineingeführt werden können, wobei die Bohrungen Dichtringe aufweisen, so dass eine dichte Führung der Stössel innerhalb der Bohrungen erfolgt.Bores 26 and 27 are provided both in the web 25 and in the cylinder cover 2. The actual damping device 28 is installed in the piston 5 and, in the exemplary embodiment shown, is formed from two projections 29 and 30 projecting beyond the piston surfaces on both sides. The plungers are dimensioned and arranged such that they are aligned with the bores 26 and 27 and can be guided into these bores 26 and 27, the bores having sealing rings, so that the plungers are tightly guided within the bores.

In dem Steg 25 ist zusätzlich eine Drosselbohrung 31 vorgesehen und eine Bypassleitung 32, die aus einem Rückschlagventil gebildet wird, das bei dem dargestellten Ausführungsbeispiel aus einer Kugel 33 besteht (Fig. 8), die in einem Kugelkäfig angeordnet ist, der einen Ventilsitz 34 besitzt. In der in Fig. 8 dargestellten Stellung befindet sich die Kugel in einer Stellung, in der die Bypassleitung nicht verschlossen wird, d. h. die Kugel liegt nicht an einem Ventilsitz auf, sondern beispielsweise an Haltefingern, die eine Umströmung durch das Druckmittel möglich machen.In the web 25, a throttle bore 31 is additionally provided and a bypass line 32, which is formed from a check valve, which in the illustrated embodiment consists of a ball 33 (FIG. 8), which is arranged in a ball cage which has a valve seat 34 . In the position shown in Fig. 8, the ball is in a position in which the bypass line is not closed, i. H. the ball does not rest on a valve seat, but, for example, on holding fingers, which allow the pressure medium to flow around it.

Eine in gleicher Weise ausgebildete Bypassleitung 35 ist im Zylinderdeckel 2 vorgesehen und auch im Zylinderdeckel 2 ist eine Drosselbohrung 36 angeordnet, wobei die beiden Bauteile 35 und 36 eine Verbindung zwischen dem Zylinderraum und der zugeordneten Druckmittelzu- bzw. -abflussleitung schaffen. Bei der in Fig. 7 und 8 dargestellten Ausführungsform liegt die Kugel des Rückschlagventiles in der Bypassleitung 35 an dem Ventilsitz an, d. h. dichtet ab.A bypass line 35 designed in the same way is provided in the cylinder cover 2 and a throttle bore 36 is also arranged in the cylinder cover 2, the two components 35 and 36 creating a connection between the cylinder space and the associated pressure medium supply and discharge line. In the embodiment shown in FIGS. 7 and 8, the ball of the check valve in the bypass line 35 bears against the valve seat, i. H. seals.

In der Zeichnung sind weiterhin die Druckmittelzu- und abflussleitungen erkennbar, wobei im nachfolgenden das beispielsweise als Zuleitung dienende Leitungssystem aus den Leitungen 401, 402 und 403 besteht, d. h. die hier aufgegebene Druckluft führt auf die Rückseite des Stössels 30, hebt die Ventilkugel 33 der Bypassleitung 32 ab und kann dadurch die Kolbenfläche A des Kolbens 5 mit Druck beaufschlagen.The pressure medium inlet and outlet lines can also be seen in the drawing, the line system, for example serving as a line, subsequently consisting of lines 401, 402 and 403, i.e. the compressed air supplied here leads to the rear of the plunger 30, lifts the valve ball 33 of the bypass line 32 from and can thereby apply pressure to the piston surface A of the piston 5.

Die zur Abführung der in den Zylinderräumen noch befindlichen Luft dienenden Leitungen sind ebenfalls aus der Zeichnung erkennbar und tragen die Bezugszeichen 501, 502 und 503.The lines used to discharge the air still in the cylinder chambers can also be seen in the drawing and bear the reference numerals 501, 502 and 503.

Es ist erkennbar, dass bei einer Bewegung des Kolbens aus der in Fig. 7 dargestellten, in die in Fig. 8 dargestellte Stellung nunmehr die auf der Kolbenseite B ruhende Druckluft über die Bohrung 26, die Leitung 502 und 501 nach aussen abgeführt wird, während die in der gegenüberliegenden Zylinderkammer befindliche Luft über die Leitung 503 zur Kolbenseite B und von dort ebenfalls über die Bohrung 26 die Leitung 502 und die Leitung 501 abgeführt wird.It can be seen that when the piston moves from the position shown in FIG. 7 to the position shown in FIG. 8, the compressed air resting on the piston side B is now discharged to the outside via the bore 26, the lines 502 and 501, while the air in the opposite cylinder chamber is discharged via line 503 to piston side B and from there also via line 26, line 502 and line 501.

Wird der Kolben 5 aus der in Fig. 8 dargestellten Stellung weiter bewegt, gelangt der Stössel 29 in die Bohrung 26 und dichtet damit die Hauptabflussleitung ab. Gleichzeitig wird durch den auftretenden Druck die Bypassleitung 35 geschlossen und nunmehr muss die sich in dem Zylinderraum auf der Kolbenfläche B befindliche Luft durch die Drosselbohrung 36 zwängen, wodurch die Bewegung des Kolbens 5 erheblich verlangsamt wird. Da die beiden Kolben 5 über die Zahnstangen 8 mit dem in den Fig. 6 bis 8 nicht dargestellten Ritzel zwangsgekoppelt sind, erfolgt eine Dämpfung beider Kolben in ihrer Endbewegung. Diese Dämpfung kann durch Wahl der Grösse der Drosselbohrung variiert werden.If the piston 5 is moved further from the position shown in FIG. 8, the tappet 29 enters the bore 26 and thus seals the main drain line. At the same time, the bypass line 35 is closed by the pressure occurring and now the air located in the cylinder space on the piston surface B must force through the throttle bore 36, whereby the movement of the piston 5 is considerably slowed down. Since the two pistons 5 are positively coupled via the racks 8 to the pinion (not shown in FIGS. 6 to 8), both pistons are damped in their end movement. This damping can be varied by choosing the size of the throttle bore.

Es ist aus der vorausgehenden Beschreibung und den Darstellungen in den Fig. 6 bis 8 ersichtlich, dass bei einer Umkehrung der Druckmittelzufuhr die gleiche Wirkung hinsichtlich der Drosselbohrung 31 im Steg 25 auftritt.It can be seen from the preceding description and the illustrations in FIGS. 6 to 8 that if the pressure medium supply is reversed, the same effect occurs with regard to the throttle bore 31 in the web 25.

Claims (10)

1. Fluid operated rotary drive or actuator device, with
(a) a cylinder (1) and two pistons (5) which are adapted to move to and fro therein oppositely in mutual dependency,
(b) a control shaft (9) with pinion, which shaft extends transversely with respect to the cylinder axis and is arranged symmetrically with respect to the two pistons (5) and the cylinder axis,
(c) two guides (6, 7) which start from the piston heads are disposed parallel to the cylinder axis, extend to over the control shaft (9), are arranged on each of the two pistons (5) and comprise, at' their outer side, guide surfaces which guide the piston in the cylinder (1 ), and the said guides are situated approximately opposite one another relatively to the longitudinal axis of the cylinder, one guide (6) comprising at its inner side a rack (8) (drive guide) which co-operates with the pinion, characterised in that the guides (6) provided with a rack (8) comprise, in their surface facing towards the cylinder wall, in each case a groove (23) which is situated parallel and symmetrically with respect to the cylinder longitudinal axis, and in the said groove there is positively and slidably accommodated the non-rack guide (7) of the other piston which is situated opposite offset by 180° about the longitudinal axis of the cylinder.
2. Device according to Claim 1, characterised in that the guides (6) provided with the rack (8) comprise symmetrically arranged guide surfaces (24) which are wide in the direction of the circumference of the inner wall of the cylinder and substantially exceed the width of the racks.
3. Device according to Claim 1 or 2, characterised in thatthe non-rack guide (7) is arranged to be freely movable in the space formed by the groove (23).
4. Device according to one or more of the preceding Claims 1 to 3, the racks (8) being fitted in shaped-retaining and force-retaining manner in the guide (6) supporting them, characterised by pins (16) arranged in aligned bores in the racks (8) and in the guides (6).
5. Device according to Claim 4, characterised in that the pins (16) are adhesively secured.
6. Device according to one or more of the preceding claims with a pressure medium supply port (3) debouching between the piston heads into the cylinder (1), and with an additional duct (15) connected with the said supply port (3), characterised in that the additional duct (15) comprises a groove in the inner side of the cylinder wall parallel to the longitudinal axis of the cylinder and extending to the vicinity of the piston head when the latter is full-in in its dead centre position.
7. Device according to Claim 1, characterised by a damping device (28) projecting beyond the two piston faces at least at one piston (5), for damping the end movements of the piston (5).
8. Device according to Claim 7, characterised by a web (25) not impeding the movements of the guides (6 and 7), bores (26, 27) arranged one in the web (25) and one in the cylinder head (2) associated with the piston (5) provided with the damping device (28), said bores communicating with the pressure fluid inlet and outlet conduits (401, 501), and by plungers (29, 30) which project above the two sides of the piston (5) and are in alignment with the bores and which engage with a sealing action in the bores (26, .27) in the end positions.
9. Device according to Claim 8, characterised by throttling bores (31, 36) which connect the cylinder chambers at the two sides of the piston face with the associated pressure fluid inlet and outlet conduits.
10. Device according to Claim 9, characterised by bypass conduits (32, 35) which are provided with non-return valves and which connect the cylinder chambers atthe two sides of the piston faces with the associated pressure fluid inlet and outlet conduits.
EP83102387A 1982-03-19 1983-03-11 Fluid operated linear-to-rotary actuator Expired EP0089568B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83102387T ATE15402T1 (en) 1982-03-19 1983-03-11 FLUID OPERATED ROTARY DRIVE ACTUATOR.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3210050 1982-03-19
DE3210050 1982-03-19

Publications (2)

Publication Number Publication Date
EP0089568A1 EP0089568A1 (en) 1983-09-28
EP0089568B1 true EP0089568B1 (en) 1985-09-04

Family

ID=6158697

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83102387A Expired EP0089568B1 (en) 1982-03-19 1983-03-11 Fluid operated linear-to-rotary actuator

Country Status (6)

Country Link
EP (1) EP0089568B1 (en)
AT (1) ATE15402T1 (en)
DE (1) DE3360703D1 (en)
HK (1) HK27586A (en)
MY (1) MY8600424A (en)
SG (1) SG95885G (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3443302A1 (en) * 1984-08-22 1986-03-06 Christian 5140 Erkelenz Kubanek Swivel drive actuated by fluid medium
JP6332688B2 (en) * 2014-09-02 2018-05-30 Smc株式会社 Rotary actuator
DE102019204446A1 (en) * 2019-03-29 2020-10-01 Festo Se & Co. Kg Fluid operated rotary drive device
CN113062894B (en) * 2021-03-16 2022-07-15 中煤科工集团重庆研究院有限公司 Swing motor for narrow space

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1229848B (en) * 1963-01-14 1966-12-01 Sihn Kg Wilhelm Jun Device for hydraulically braked pneumatic movement of machine parts
US3246581A (en) * 1963-10-23 1966-04-19 Flo Tork Inc Air actuator
FR1461217A (en) * 1965-04-23 1966-12-10 Mathews Engineering Company Lt Device with rotary engines actuated by pressurized fluid
NL174580C (en) * 1975-10-21 1984-07-02 El O Matic Bv DEVICE FOR A SWIVEL-PROVEN DRIVE.
GB1548683A (en) * 1976-10-06 1979-07-18 Norbo Pneumatics Ltd Pneumatic actuators
US4281588A (en) * 1979-06-18 1981-08-04 Sprague Devices, Inc. Reciprocating piston fluid powered motor

Also Published As

Publication number Publication date
EP0089568A1 (en) 1983-09-28
SG95885G (en) 1987-09-18
ATE15402T1 (en) 1985-09-15
DE3360703D1 (en) 1985-10-10
HK27586A (en) 1986-04-25
MY8600424A (en) 1986-12-31

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