EP0472862B1 - Fluid powered rodless cylinder - Google Patents
Fluid powered rodless cylinder Download PDFInfo
- Publication number
- EP0472862B1 EP0472862B1 EP91111283A EP91111283A EP0472862B1 EP 0472862 B1 EP0472862 B1 EP 0472862B1 EP 91111283 A EP91111283 A EP 91111283A EP 91111283 A EP91111283 A EP 91111283A EP 0472862 B1 EP0472862 B1 EP 0472862B1
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- European Patent Office
- Prior art keywords
- band
- piston
- space
- cylinder
- cylinder housing
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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
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/084—Characterised by the construction of the motor unit the motor being of the rodless piston type, e.g. with cable, belt or chain
Definitions
- the invention relates to a fluid-driven rodless cylinder according to the preamble of claim 1.
- Fluid-driven piston rodless working cylinders which have power take-offs guided on the outside of the cylinder tube. These can be mechanically or magnetically coupled to the piston.
- the mechanical connection can take place via a circumferential transmission element, in particular a belt or rope (EP-B-O 177 880), or via a rigid power bridge between the piston and the power consumer. In the latter case, the power bridge protrudes through a sealable slot in the cylinder tube (EP-A-0 190 760, DE-A-3509891).
- the present invention relates to a working cylinder with a likewise purely mechanical coupling between the piston and the power consumer.
- WO-A-88/01698 shows a further rod cylinder without internal pressure.
- the translatory movement of the piston is converted into a rotational movement of deflection rollers and afterwards outside the cylinder, this rotational movement is converted back into a translatory movement of a power consumer.
- This of course means losses accompanying.
- the strip is guided in a strip space which is pressurized with the same pressure as one side of the piston space.
- a sealing element slidably mounted in the belt space connects the two ends of the belt designed as a toothed belt within the belt space.
- this sealing element acts more or less like a small piston which is pushed in the same direction as the working piston due to the pressurization of the band chamber.
- This sealing element therefore, as a part designed in the opposite direction to the piston, causes a force due to its effective area which is opposite to the action force of the piston, whereby the efficiency of the cylinder is considerably reduced.
- the power take-up be gripped around the cylinder tube in a clamp-like manner in order to counteract widening in the area of the longitudinal slot.
- This task is solved by the special shape of the inner profile of the cylinder housing. Its interior is divided into a piston space and a band space, and the outside is completely closed - except for the slits for the band at the cylinder ends.
- the piston space and the band space are connected to one another by a longitudinal slot which is sealed by means of a sealing band.
- the band space is depressurized when the piston space is pressurized.
- the piston is provided with a power bridge, which engages in the band space through the longitudinal slot and through the sealing band which is then deflected radially to the band space.
- the dimensions of the power bridge are very small compared to the power bridges of known slot cylinders.
- the power bridge in turn is connected to the belt at its end protruding into the belt space. This can be accomplished in a suitable manner, for example welding or by means of a knee joint.
- the band exits at the end faces of the cylinder housing, more precisely in the region of the band space, in order to be connected in a known manner to the force consumer guided on the cylinder housing by means of two deflection wheels.
- the tightness of the working cylinder can be increased further by the fact that the end faces of the cylinder housing are additionally sealed in the region of the passage of the band, that is to say at the ends of the band space.
- the band space according to the proposal according to the invention is in any case practically depressurized when the piston space is pressurized. However, the further sealing increases the efficiency even further.
- this measure allows that the belt is not - as usual - designed as a steel belt or rope, but as a toothed belt or chain. In the case of conventional constructions of the inner profile of the cylinder, this would only be possible by accepting extreme leaks in the cylinder.
- the usual deflection wheels are designed as toothed belt wheels or as chain wheels.
- the advantage of this measure which is only possible due to the inner profile of the cylinder according to the invention, can be seen in the fact that, in addition to the frictional connection between the belt and the deflection wheel, a form closure occurs which has other functions Deflection wheels permitted.
- FIG. 1 An exemplary embodiment of the working cylinder is shown in the drawing. This shows a cross section through the working cylinder according to the invention.
- cylinder housing 4 Shown is the cylinder housing 4 with the piston chamber 8 and the belt chamber 9. It is essential that the inner profile of the housing is completely closed to the outside, so that leaks when the piston chamber 8 is pressurized are not possible via connecting pieces (not shown).
- the band space 9 is connected to the piston space 8 via a longitudinal slot 10.
- the longitudinal slot 10 is sealed by a sealing tape 5. Only at the point of passage of the force bridge 6 between the piston and the band 7 does it bend radially inward from the slot 10 into the piston chamber 8, as is indicated schematically in the enlarged view of this point.
- the band 7 running in the band space 9 is connected to the power bridge 6.
- the band 7 emerges at the ends of the cylinder housing 4, it being possible for further seals to be arranged at these passage points in order to further increase the tightness of the system.
- the belt 7 is directed via deflection wheels to the power consumer 1 connected to it, which in the exemplary embodiment shown can be moved back and forth by means of prismatic guides 2, 11 on the top of the cylinder housing.
- the novel inner profile of the cylinder housing allows the use of toothed belts or chains as a "band", preferably when the passage slots for the band are additionally sealed at the cylinder ends.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Actuator (AREA)
- Fluid-Damping Devices (AREA)
- Nozzles (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Die Erfindung betrifft einen fluidgetriebenen kolbenstangenlosen Arbeitszylinder gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a fluid-driven rodless cylinder according to the preamble of claim 1.
Auf dem Gebiete der kolbenstangenlosen Arbeitszylinder haben sich in der Praxis verschiedene Arten der Kraftabnahme durchgesetzt. So sind fluidgetriebene kolbenstangenlose Arbeitszylinder bekannt, die außen auf dem Zylinderrohr geführte Kraftabnehmer aufweisen. Diese können mechanisch oder magnetisch mit dem Kolben gekoppelt sein. Die mechanische Verbindung kann über ein umlaufendes Übertragungsglied, insbesondere ein Band oder Seil (EP-B-O 177 880), oder über eine starre Kraftbrücke zwischen dem Kolben und dem Kraftabnehmer erfolgen. Im letzteren Fall ragt die Kraftbrücke durch einen abdichtbaren Schlitz im Zylinderrohr (EP-A-0 190 760, DE-A-3509891).In the field of rodless working cylinders, various types of power take-off have become established in practice. Fluid-driven piston rodless working cylinders are known which have power take-offs guided on the outside of the cylinder tube. These can be mechanically or magnetically coupled to the piston. The mechanical connection can take place via a circumferential transmission element, in particular a belt or rope (EP-B-O 177 880), or via a rigid power bridge between the piston and the power consumer. In the latter case, the power bridge protrudes through a sealable slot in the cylinder tube (EP-A-0 190 760, DE-A-3509891).
Die vorliegende Erfindung betrifft einen Arbeitszylinder mit einer ebenfalls rein mechanischen Kopplung zwischen Kolben und Kraftabnehmer.The present invention relates to a working cylinder with a likewise purely mechanical coupling between the piston and the power consumer.
Bei den bekannten Band- oder Seilzylindern ist die Abdichtung der Zylinderstirnseiten, in denen das Band oder Seil durchtritt, problematisch. Meist handelt es sich bei den Bändern um Stahlbänder mit annähernd rechteckigem Querschnitt. Es ist einsichtig, daß die Abdichtung an den Zylinderenden bei einer raschen Bewegung des Kolbens, an dem die Bänder befestigt sind, äußerst schwer zu handhaben ist. Es müssen sich nämlich die Dichtlippen der Abdichtungen innerhalb kürzester Zeit dem Band anpassen.In the known band or rope cylinders, the sealing of the cylinder end faces, in which the band or rope passes, is problematic. Most of the tapes are steel tapes with an approximately rectangular cross-section. It will be appreciated that the seal at the cylinder ends is extremely difficult to handle with rapid movement of the piston to which the bands are attached is. The sealing lips of the seals have to adapt to the tape within a very short time.
Darüberhinaus ergibt sich das folgende Problem, da in der Praxis meist Stahlbänder von 2/10 mm Dicke als Bänder verwendet werden. Diese sind so empfindlich, daß sie aufgrund von Kerbwirkungen, die ihrerseits auf Kratzer in der Oberfläche - etwa infolge von Berührungen mit einem Werkzeugzurückzuführen sind, zum Reißen neigen.In addition, the following problem arises because in practice, steel tapes of 2/10 mm in thickness are mostly used as tapes. These are so sensitive that they tend to crack due to notch effects, which in turn are due to scratches in the surface, for example as a result of contact with a tool.
Im Falle der Verwendung eines Seils tritt das Problem auf, daß die Oberfläche des Seils per se uneben ist und schon von daher Undichtigkeiten vorprogrammiert sind.In the case of the use of a rope, the problem arises that the surface of the rope is uneven per se and therefore leaks are preprogrammed.
In der DE-C-952 308 ist die Verwendung einer Kette oder Zahnkette als "Band" vorgeschlagen worden, allerdings bei einem Arbeitszylinder, bei dem der vom Kolbenraum getrennte Bandraum mit Druck beaufschlagt ist, wenn Druckmittel in den Kolbenraum geleitet wird, um den Kolben in die eine oder andere Richtung zu bewegen. Bei dem in der genannten Druckschrift beschriebenen Arbeitszylinder handelt es sich um einen innendruckbeaufschlagten Arbeitszylinder, bei dem der Bandraum vom Kolbenraum druckmäßig nicht voneinander getrennt sind.In DE-C-952 308 the use of a chain or toothed chain as a "band" has been proposed, however in a working cylinder in which the band space separated from the piston space is pressurized when pressure medium is passed into the piston space around the piston to move in one direction or the other. The working cylinder described in the cited publication is a working cylinder subjected to internal pressure, in which the band space is not separated from one another in terms of pressure by the piston space.
Einen weiteren innendruckbeaufschlagten kolbenstangenlosen Arbeitszylinder zeigt die WO-A-88/01698. Darin wird die translatorische Bewegung des Kolbens in eine rotatorische Bewegung von Umlenkrollen und hernach außerhalb des Zylinders diese rotatorische Bewegung wieder in eine translatorische Bewegung eines Kraftabnehmers gewandelt. Hiermit sind selbstverständlich Verluste einhergehend. Das Band wird wie im Falle der DE-C-952308 in einem Bandraum geführt, der mit dem selben Druck beaufschlagt ist wie die eine Seite des Kolbenraumes. Ein in dem Bandraum gleitend gelagertes Dichtelement verbindet innerhalb des Bandraumes die beiden Enden des als Zahnriemen ausgebildeten Bandes. Dadurch, daß der Zylinder ein innendruckbeaufschlagter Zylinder ist, der Bandraum daher vom Kolbenraum druckmäßig nicht getrennt ist, wirkt dieses Dichtelement quasi wie ein kleiner Kolben, der in die selbe Richtung wie der Arbeitskolben gedrängt wird aufgrund der Druckbeaufschlagung des Bandraumes. Dieses Dichtelement bewirkt daher als ein dem Kolben gegenläufig konzipiertes Teil aufgrund seiner wirksamen Fläche eine Kraft, die der Aktionskraft des Kolbens entgegengesetzt ist, wodurch der Wirkungsgrad des Zylinders erheblich reduziert wird.WO-A-88/01698 shows a further rod cylinder without internal pressure. In it, the translatory movement of the piston is converted into a rotational movement of deflection rollers and afterwards outside the cylinder, this rotational movement is converted back into a translatory movement of a power consumer. This of course means losses accompanying. As in the case of DE-C-952308, the strip is guided in a strip space which is pressurized with the same pressure as one side of the piston space. A sealing element slidably mounted in the belt space connects the two ends of the belt designed as a toothed belt within the belt space. Because the cylinder is an internal pressurized cylinder, the band space is therefore not separated from the piston chamber in terms of pressure, this sealing element acts more or less like a small piston which is pushed in the same direction as the working piston due to the pressurization of the band chamber. This sealing element therefore, as a part designed in the opposite direction to the piston, causes a force due to its effective area which is opposite to the action force of the piston, whereby the efficiency of the cylinder is considerably reduced.
In den Fällen eines Arbeitszylinders mit starrer Kraftbrücke zwischen Kolben und Kraftabnehmer entsteht das Problem der Undichtigkeit zum einen bereits an der Durchtrittsstelle der Kraftbrücke. Desweiteren ist zu bedenken, daß im Falle der Druckbeaufschlagung des Zylinderrohres, um den Kolben darin zu verfahren, dieses dazu neigen wird, sich auszudehnen. Selbstverständlich bietet hier der Schlitz für die Kraftbrücke den geeigneten Ort für ein Aufspreizen des Zylinderrohres, so daß also im Moment der Betätigung des Kolbens, d.h. bei Druckbeaufschlagung des Zylinderrohres, die Undichtigkeit des Zylinders zunimmt. Zur Behebung dieses Problems ist auch schon vorgeschlagen worden, ein Zylinderrohr mit unstetiger Wanddicke zu verwenden, dergestalt, daß die Wanddicke auf der dem Schlitz gegenüberliegenden Seite am größten ist (EP-A-0190760, Fig. 2, DE-A-3509891). Hierdurch soll das dickere Material einem Aufbiegen des Rohres entgegenwirken.In the case of a working cylinder with a rigid power bridge between the piston and the power consumer, the problem of leakage arises on the one hand at the point of passage of the power bridge. Furthermore, it should be borne in mind that if the cylinder tube is pressurized to move the piston therein, it will tend to expand. Of course, the slot for the power bridge provides the suitable place for spreading the cylinder tube, so that when the piston is actuated, ie when the cylinder tube is pressurized, the leakage of the cylinder increases. To solve this problem, it has also been proposed to use a cylinder tube with a discontinuous wall thickness such that the wall thickness is greatest on the side opposite the slot (EP-A-0190760, Fig. 2, DE-A-3509891). The thicker material is intended to counteract bending of the tube.
Gemäß einem anderen Vorschlag (EP-A-0068088) ist vorgesehen, den Kraftabnehmer das Zylinderrohr klammerartig umgreifen zu lassen, um einem Aufweiten im Bereich des Längsschlitzes entgegenzuwirken.According to another proposal (EP-A-0068088) it is provided that the power take-up be gripped around the cylinder tube in a clamp-like manner in order to counteract widening in the area of the longitudinal slot.
Bedenkt man nun, daß bekannte Arbeitszylinder mit ca. 6 - 10 bar Luftdruck betrieben werden, wird deutlich, daß Aufweitungen auch nur um wenige Zehntelmillimeter den Wirkungsgrad eines solchen Zylinders drastisch reduzieren.If one now considers that known working cylinders are operated with an air pressure of approx. 6-10 bar, it becomes clear that widening by only a few tenths of a millimeter drastically reduces the efficiency of such a cylinder.
Vor dem aufgezeigten Hintergrund ist es nun die Aufgabe der vorliegenden Erfindung, einen kolbenstangenlosen Arbeitszylinder zu schaffen, bei dem die angesprochenen Dichtungsprobleme bekannter Arbeitszylinder nicht mehr aufteten.Against the background shown, it is the object of the present invention to create a rodless cylinder in which the sealing problems of known cylinders no longer occur.
Gelöst wird diese Aufgabe durch die spezielle Formgebung des Innenprofils des Zylindergehäuses. So ist dessen Inneres in einen Kolbenraum und in einen Bandraum unterteilt und nach außen hin - bis auf die Durchtrittsschlitze für das Band an den Zylinderenden - vollkommen geschlossen. Der Kolbenraum und der Bandraum stehen untereinander durch einen Längsschlitz in Verbindung, der mittels eines Dichtbandes abgedichtet ist. Hierdurch ist der Bandraum bei Druckbeaufschlagung des Kolbenraums drucklos. Der Kolben ist mit einer Kraftbrücke versehen, die durch den Längsschlitz und durch das dann radial zum Bandraum ausgelenkte Dichtband in den Bandraum greift. Die Dimensionen der Kraftbrücke sind im Vergleich zu den Kraftbrücken bekannter Schlitzzylinder sehr klein.This task is solved by the special shape of the inner profile of the cylinder housing. Its interior is divided into a piston space and a band space, and the outside is completely closed - except for the slits for the band at the cylinder ends. The piston space and the band space are connected to one another by a longitudinal slot which is sealed by means of a sealing band. As a result, the band space is depressurized when the piston space is pressurized. The piston is provided with a power bridge, which engages in the band space through the longitudinal slot and through the sealing band which is then deflected radially to the band space. The dimensions of the power bridge are very small compared to the power bridges of known slot cylinders.
Die Kraftbrücke ihrerseits ist auf ihrem in den Bandraum ragenden Ende mit dem Band verbunden. Dies kann auf geeignete Weise, beispielsweise Schweißen oder mittels eines Kniegelenks bewerkstelligt sein.The power bridge in turn is connected to the belt at its end protruding into the belt space. This can be accomplished in a suitable manner, for example welding or by means of a knee joint.
Das Band tritt an den Stirnseiten des Zylindergehäuses, genauer gesagt im Bereich des Bandraumes aus, um über zwei Umlenkräder in bekannter Weise mit dem auf dem Zylindergehäuse geführten Kraftabnehmer kraftschlüssig verbunden zu werden.The band exits at the end faces of the cylinder housing, more precisely in the region of the band space, in order to be connected in a known manner to the force consumer guided on the cylinder housing by means of two deflection wheels.
Die Dichtigkeit des Arbeitszylinders kann noch dadurch erhöht werden, daß die Stirnseiten des Zylindergehäuses im Bereich des Durchtritts des Bandes, also an den Enden des Bandraumes, zusätzlich abgedichtet sind. Zwar ist der Bandraum nach dem erfindungsgemäßen Vorschlag ohnehin praktisch drucklos bei Druckbeaufschlagung des Kolbenraumes. Die weitere Abdichtung erhöht jedoch den Wirkungsgrad noch weiter.The tightness of the working cylinder can be increased further by the fact that the end faces of the cylinder housing are additionally sealed in the region of the passage of the band, that is to say at the ends of the band space. The band space according to the proposal according to the invention is in any case practically depressurized when the piston space is pressurized. However, the further sealing increases the efficiency even further.
Darüberhinaus gestattet diese Maßnahme, daß das Band nicht - wie üblich - als stahlband oder Seil, sondern als Zahnriemen oder Kette ausgebildet ist. Bei herkömmlichen Konstruktionen des Innenprofils des Zylinders wäre dies nur unter Inkaufnahme extremer Undichtigkeiten des Zylinders möglich.In addition, this measure allows that the belt is not - as usual - designed as a steel belt or rope, but as a toothed belt or chain. In the case of conventional constructions of the inner profile of the cylinder, this would only be possible by accepting extreme leaks in the cylinder.
Der Ausbildung des Bandes als Zahnriemen oder Kette entsprechend sind die üblichen Umlenkräder als Zahnriemenräder bzw. als Kettenräder ausgebildet. Der Vorteil dieser Maßnahme, die nur möglich ist aufgrund des erfindungsgemäßen Innenprofils des Zylinders, ist darin zu sehen, daß neben dem Kraftschluß zwischen Band und Umlenkrad ein Formenschluß tritt, der weitere Funktionen der Umlenkräder gestattet. So ist es beispielsweise möglich, eine stationäre Bremse auf das Umlenkrad wirken zu lassen. Aufgrund der Formen- und Kraftschlusses zwischen dem Umlenkrad und dem Zahnriemen bzw. der Kette tritt beim Bremsen kein Schlupf wie beispielsweise bei Stahlbändern auf, wodurch eine absolut exakte und reproduzierbare Positionierung des Kolbens bzw. Kraftabnehmers möglich wird.Corresponding to the design of the belt as a toothed belt or chain, the usual deflection wheels are designed as toothed belt wheels or as chain wheels. The advantage of this measure, which is only possible due to the inner profile of the cylinder according to the invention, can be seen in the fact that, in addition to the frictional connection between the belt and the deflection wheel, a form closure occurs which has other functions Deflection wheels permitted. For example, it is possible to have a stationary brake act on the idler wheel. Due to the positive and non-positive connection between the deflection wheel and the toothed belt or chain, no slippage occurs during braking, as is the case with steel belts, which enables absolutely precise and reproducible positioning of the piston or power take-off.
Eine beispielhafte Ausführungsform des Arbeitszylinders ist in der Zeichnung dargestellt. Darin ist ein Querschnitt durch den erfindungsgemäßen Arbeitszylinder dargestellt.An exemplary embodiment of the working cylinder is shown in the drawing. This shows a cross section through the working cylinder according to the invention.
Aus Darstellungsgründen sind der Kolben und die Umlenkräder nicht abgebildet.For reasons of illustration, the piston and the deflection wheels are not shown.
Dargestellt ist das Zylindergehäuse 4 mit dem Kolbenraum 8 und dem Bandraum 9. Wesentlich ist, daß das Innenprofil des Gehäuses nach außen vollkommen geschlossen ist, so daß Undichtigkeiten bei Druckbeaufschlagung des Kolbenraumes 8 über nicht dargestellte Anschlußstutzen unmöglich sind.Shown is the cylinder housing 4 with the
Der Bandraum 9 ist mit dem Kolbenraum 8 über einen Längsschlitz 10 verbunden. Der Längsschlitz 10 ist durch ein Dichtband 5 abgedichtet. Lediglich an der Stelle des Durchtritts der Kraftbrücke 6 zwischen dem Kolben und dem Band 7 biegt es sich radial nach innen aus dem Schlitz 10 in den Kolbenraum 8, wie schematisch in der vergrößerten Ansicht dieser Stelle angedeutet ist. Mit der Kraftbrücke 6 ist das im Bandraum 9 laufende Band 7 verbunden.The
Das Band 7 tritt an den Enden des Zylindergehäuses 4 nach außen, wobei zur weiteren Erhöhung der Dichtigkeit des Systems an diesen Durchtrittsstellen weitere Dichtungen angeordnet sein können.The
Über Umlenkräder wird das Band 7 an den mit ihm verbundenen Kraftabnehmer 1 gelenkt, der im gezeigten Ausführungsbeispiel mittels prismatischer Führungen 2, 11 auf der Oberseite des Zylindergehäuses hin- und herbewegbar ist.The
Das neuartige Innenprofil des Zylindergehäuses gestattet den Einsatz von Zahnriemen oder Ketten als "Band", vorzugsweise dann, wenn die Durchtrittsschlitze für das Band an den Zylinderenden zusätzlich abgedichtet ist.The novel inner profile of the cylinder housing allows the use of toothed belts or chains as a "band", preferably when the passage slots for the band are additionally sealed at the cylinder ends.
Ein Aufweiten des Profils wie bei herkömmlichen Schlitzzylindern bei Druckbeaufschlagung ist nicht möglich. Auch das Dichtungsproblem herkömmlicher Bandzylinder an den Zylinderköpfen tritt nicht auf, da die Hauptdichtwirkung bei dem vorgeschlagenen Arbeitszylinder von dem Dichtband 5 im Innern des Profils erzielt wird, so daß der Bandraum 9 bereits drucklos ist.It is not possible to widen the profile as with conventional slot cylinders when pressurized. The sealing problem of conventional band cylinders on the cylinder heads does not occur, since the main sealing effect in the proposed working cylinder is achieved by the sealing
Claims (4)
- Fluid-driven working cylinder without a piston rod having a cylinder housing (4) which in cross-section is fully closed and along which a force takeaway (1) is guided without turning that is connected with a band (7) which extends respectively from each of the front ends of the front housing (4) and is fastened to the piston and externally guided over 2 reversing wheels,
characterized in that the interior of the cylinder housing (4) is subdivided into a piston space (8) wherein the working piston can be moved back and forth and into a band space (9) being separated from the piston space (8) and being unpressurized when pressure is applied to said piston space (8), the band space (9) being connected with said piston space (8) by means of a longitudinal slid (10) which is sealed off by a sealing strip (5) and in which band space (9) runs the band (7) which on its part is connected to the piston by means of a force linkage (6) which projects through the longitudenal slid (10). - Working cylinder according to claim 1, wherein the front ends of the cylinder housing (4) are additionally sealed at those sites where the band (7) exits the band space (9).
- Working cylinder according to claims 1 or 2, wherein said band (7) is developed as a toothed belt and the reversing wheels are developed as tooth belt wheels.
- Working cylinder according to claims 1 or 2, wherein said band (7) is developed as a chain and the reversing wheels are developed as sprocket wheels.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT91111283T ATE89372T1 (en) | 1990-08-31 | 1991-07-06 | FLUID DRIVEN RODLESS POWER CYLINDER. |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4027636A DE4027636C2 (en) | 1990-08-31 | 1990-08-31 | Fluid powered rodless cylinder |
| DE4027636 | 1990-08-31 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP0472862A1 EP0472862A1 (en) | 1992-03-04 |
| EP0472862B1 true EP0472862B1 (en) | 1993-05-12 |
Family
ID=6413345
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP91111283A Expired - Lifetime EP0472862B1 (en) | 1990-08-31 | 1991-07-06 | Fluid powered rodless cylinder |
Country Status (6)
| Country | Link |
|---|---|
| US (1) | US5178056A (en) |
| EP (1) | EP0472862B1 (en) |
| JP (1) | JPH0784887B2 (en) |
| AT (1) | ATE89372T1 (en) |
| DE (2) | DE4027636C2 (en) |
| HU (1) | HU209349B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4332547A1 (en) * | 1993-09-24 | 1995-03-30 | Duewag Ag | Drive and guidance system for a load to be moved |
| DE4334681C2 (en) * | 1993-10-12 | 1995-09-28 | Norgren Martonair Gmbh | Movement unit for generating a linear movement |
| DE19754480A1 (en) * | 1997-12-08 | 1999-06-10 | Cherkasky Yakiv | Piston engine |
| FR2820068B1 (en) * | 2001-01-31 | 2003-05-16 | Jean Paul Coron | LINEAR GUIDE MODULE OF A TRAINARD INCLUDING A MOTOR COMPONENT |
| DE102007040678A1 (en) * | 2007-08-29 | 2009-03-05 | Manroland Ag | Turning bar unit of a web-fed printing machine |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0068088A1 (en) * | 1981-06-25 | 1983-01-05 | PROMA Produkt- und Marketing-Gesellschaft m.b.H. | Fluid pressure actuator with slotted cylinder and sealed ends |
| EP0190760A1 (en) * | 1985-02-08 | 1986-08-13 | ORIGA GmbH Pneumatik | Fluid actuator |
| DE3509891A1 (en) * | 1985-03-19 | 1986-09-25 | Herion-Werke Kg, 7012 Fellbach | PISTONLESS CYLINDER |
| EP0177880B1 (en) * | 1984-10-09 | 1988-03-02 | GAS Gesellschaft für Antriebs- und Steuerungstechnik mbH & Co.KG | Straight line drive |
| WO1988001698A1 (en) * | 1986-09-05 | 1988-03-10 | Clarke Douglas C | Fluid operable devices |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE952308C (en) * | 1942-04-26 | 1956-11-15 | Wilhelm Ludowici Dr Ing | Piston pressurized on both sides |
| YU37220B (en) * | 1976-06-25 | 1984-08-31 | Mirkovic Radivoje | Band cylinder |
| US4252285A (en) * | 1979-04-30 | 1981-02-24 | The United States Of America As Represented By The Secretary Of The Navy | Dynamic seal for slotted cylinder |
| YU143979A (en) * | 1979-06-19 | 1983-01-21 | Miln Dobljekar | Cylinder with a chain |
| IT1164702B (en) * | 1979-09-18 | 1987-04-15 | Sante Zelli | IMPROVEMENT IN TELESCOPIC ELEVATORS DEVICES ESPECIALLY FOR CINETELVISUAL SHOOTING TROLLEYS |
| DE2939153C2 (en) * | 1979-09-27 | 1983-12-22 | Dürkoppwerke GmbH, 4800 Bielefeld | Fluid-operated linear drive for an output member that moves in a straight line with a large stroke |
| CH660513A5 (en) * | 1983-05-17 | 1987-04-30 | Sft Ag Spontanfoerdertechnik | DRIVING DEVICE WITH A FORCE TRANSMISSION FOLLOWING A GENERAL RAILWAY MOVEMENT. |
| DE3505167A1 (en) * | 1985-02-15 | 1986-08-28 | GAS Gesellschaft für Antriebs- und Steuerungstechnik mbH & Co KG, 7742 St Georgen | Linear drive |
| CA1260360A (en) * | 1986-09-05 | 1989-09-26 | Alan G. Dry | Rodless cylinder |
| DE3631514A1 (en) * | 1986-09-17 | 1988-03-24 | Proma Prod & Marketing Gmbh | PRESSURE CYLINDER |
| JPH0765602B2 (en) * | 1987-01-30 | 1995-07-19 | 豊和工業株式会社 | Rotless dress cylinder |
| IT1217812B (en) * | 1988-06-08 | 1990-03-30 | Univers S P A | Seal for rodless pneumatic cylinder |
| DE3905561C2 (en) * | 1989-02-23 | 1995-04-20 | Rexroth Pneumatik Mannesmann | Working cylinder actuatable by pressure medium |
| DE3909344A1 (en) * | 1989-03-22 | 1990-09-27 | Rexroth Pneumatik Mannesmann | PRESSURE-OPERABLE WORKING CYLINDER |
| DE3914889A1 (en) * | 1989-05-05 | 1990-11-08 | Knorr Bremse Ag | PISTONLESS WORK CYLINDER |
-
1990
- 1990-08-31 DE DE4027636A patent/DE4027636C2/en not_active Expired - Fee Related
-
1991
- 1991-07-06 EP EP91111283A patent/EP0472862B1/en not_active Expired - Lifetime
- 1991-07-06 DE DE9191111283T patent/DE59100109D1/en not_active Expired - Fee Related
- 1991-07-06 AT AT91111283T patent/ATE89372T1/en not_active IP Right Cessation
- 1991-08-26 US US07/749,842 patent/US5178056A/en not_active Expired - Lifetime
- 1991-08-26 HU HU912788A patent/HU209349B/en not_active IP Right Cessation
- 1991-08-28 JP JP3242648A patent/JPH0784887B2/en not_active Expired - Lifetime
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0068088A1 (en) * | 1981-06-25 | 1983-01-05 | PROMA Produkt- und Marketing-Gesellschaft m.b.H. | Fluid pressure actuator with slotted cylinder and sealed ends |
| EP0177880B1 (en) * | 1984-10-09 | 1988-03-02 | GAS Gesellschaft für Antriebs- und Steuerungstechnik mbH & Co.KG | Straight line drive |
| EP0190760A1 (en) * | 1985-02-08 | 1986-08-13 | ORIGA GmbH Pneumatik | Fluid actuator |
| DE3509891A1 (en) * | 1985-03-19 | 1986-09-25 | Herion-Werke Kg, 7012 Fellbach | PISTONLESS CYLINDER |
| WO1988001698A1 (en) * | 1986-09-05 | 1988-03-10 | Clarke Douglas C | Fluid operable devices |
Also Published As
| Publication number | Publication date |
|---|---|
| ATE89372T1 (en) | 1993-05-15 |
| US5178056A (en) | 1993-01-12 |
| DE4027636A1 (en) | 1992-04-09 |
| HU209349B (en) | 1994-04-28 |
| EP0472862A1 (en) | 1992-03-04 |
| DE4027636C2 (en) | 1994-03-17 |
| HU912788D0 (en) | 1992-01-28 |
| DE59100109D1 (en) | 1993-06-17 |
| HUT59468A (en) | 1992-05-28 |
| JPH0784887B2 (en) | 1995-09-13 |
| JPH04341604A (en) | 1992-11-27 |
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