EP0602417B1 - Rodless power cylinder - Google Patents

Rodless power cylinder Download PDF

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Publication number
EP0602417B1
EP0602417B1 EP93118855A EP93118855A EP0602417B1 EP 0602417 B1 EP0602417 B1 EP 0602417B1 EP 93118855 A EP93118855 A EP 93118855A EP 93118855 A EP93118855 A EP 93118855A EP 0602417 B1 EP0602417 B1 EP 0602417B1
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EP
European Patent Office
Prior art keywords
pressure
power cylinder
pistons
cylinder according
piston
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
EP93118855A
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German (de)
French (fr)
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EP0602417A1 (en
Inventor
Gunther Dipl.-Ing. Strobel (Fh)
Manfred Moeck
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP0602417A1 publication Critical patent/EP0602417A1/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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/265—Locking mechanisms specially adapted for rodless pistons or slotted cylinders
    • 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
    • F15B15/082—Characterised by the construction of the motor unit the motor being of the slotted cylinder type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B15/262—Locking mechanisms using friction, e.g. brake pads

Definitions

  • the invention relates to a rodless cylinder according to the preamble of the main claim.
  • a rodless cylinder with all generic features in which a braking device is already integrated in the power take-off, whereby a uniformly acting braking force can be generated precisely and quickly.
  • a braking device is already integrated in the power take-off, whereby a uniformly acting braking force can be generated precisely and quickly.
  • a slide-shaped guide body has a brake piston on opposite sides, which in rectangular recesses of the guide body are movably guided.
  • Each brake piston carries a brake lining on the outside, which lies opposite surface sections on profile parts of the cylinder tube, while it has a rubber-like sealing element on its pressurized inside.
  • the rodless working cylinder according to the invention has the advantage that a force acting in the longitudinal direction on the seals of the pressure pistons is avoided by the separation of the pressure piston and brake plate. A possible leakage, which can lead to brake failure, is therefore excluded. Furthermore, the separation of these two components allows the force to be introduced off-center.
  • the brake unit can be designed as a pressure brake or as a pressure drop brake. Formations according to claims 7 and 8 are particularly favorable. As a result, the braking forces act uniformly from both sides on the housing profile and are supported on the power take-off; furthermore, no additional lateral forces and moments act on the guide when braking. Further advantageous embodiments of the invention emerge from the remaining subclaims, which favor a compact and inexpensive braking device and permit unrestricted attachment of electrical switches and fastening parts.
  • FIG. 4 shows a cross section through a braking device designed as a pressure drop brake.
  • the housing 10 of a rodless working cylinder is shown in cross section and only in dashed lines, since it is not directly essential to the invention.
  • the movement of the working piston 11B is transmitted via a band to a guide 11C sliding on the housing for power take-off 11, which is arranged outside the housing 10 and is used for power transmission.
  • a first housing part 12 is screwed on the left and a second housing part 13 of the braking device 14 according to the invention is screwed on the right.
  • the two housing parts are identical.
  • the housing part 12 has four blind holes 15 to 18, the axes of which are perpendicular to the longitudinal axis of the housing 10 of the working cylinder, but are arranged in the same horizontal plane.
  • the holes 15 to 18 penetrate into the housing part 12 from the side facing the housing 10, the bottom of the holes is each flat.
  • a pressure piston 19 is arranged, which has a sealing ring 20 on its outer circumference.
  • a rectangular recess 22 is formed, in which a plate 23 is suitably arranged, against which the end faces of the pistons bear.
  • a brake pad 24 is fixedly attached, which abuts the side wall 25 of the housing 10 of the working cylinder serving almost as a braking surface.
  • a pressure chamber 26 is located between each piston 19 and the base of the bores 15 to 18, a channel 27 opening into each of these pressure chambers, which channel is connected to a tube 28 which is inserted in the housing part 13.
  • Compressed air is supplied to this housing part via a channel system 29 by means not shown, namely via a valve system, also not shown, since this is not essential to the invention.
  • the housing parts 13 and 14 are connected to the power take-off 11 by means of screws 30. These screws can be clearly seen in FIGS. 2 and 3.
  • the pressure chambers 26 When the pressure chambers 26 are pressurized with compressed air at the bores receiving the pistons 19, they press on the rectangular plate 23 and this is pressed with its brake lining 24 onto the corresponding braking surface on the housing 10 of the working cylinder.
  • Such training has the advantage that a relatively large force - four pistons - presses evenly on the plate 23. Since the piston and brake plate are designed separately, the force can also be applied off-center. It can be seen from what has been described above that the braking device is designed as a pressure brake.
  • the exemplary embodiment 2 according to FIG. 4 is designed as a pressure drop brake, ie the brake is released when the pistons are acted on.
  • the power take-off - designated 11A - in turn has a plurality of bores 31, in which two pistons 32, 33 are guided, which are again sealed on the outside by sealing rings (not further designated).
  • Both pistons have a central bore 34 or 35, a screw pin 36 being screwed into the bore 35 and being held by a nut 37 or being able to be adjusted in its axial direction and its pin part 38 penetrating through the bore 34. Both bores are in turn sealed by sealing rings, which are not further specified.
  • the pressure chamber is designated by 40 and lies between the two pistons 32, 33.
  • a channel 41 opens into the pressure chamber 40, which in turn can be pressurized with compressed air via a channel system (not shown).
  • the piston 33 acts Belleville washer 43, which is supported on a shoulder of the bore 31.
  • a circular plate 23A with a brake pad 24A is a circular plate 23A with a brake pad 24A; the plate 23A is separated from the pin part 38.
  • the plate spring assembly 43 presses the brake plate and its brake lining against the braking surface 10B of the housing 10 of the working cylinder via the piston 33 and the screw pin 36.
  • the power take-off 11A is now braked.
  • the piston 33 By acting on the pressure chamber 40, the piston 33 is displaced against the force of the plate spring assembly 43 in such a way that the pin 38 lifts off the plate 23A.
  • the piston 32 is always supported on a snap ring 44.
  • the power take-off is now released and can be moved by the piston of the working cylinder.
  • the right side of FIG. 4 shows how the piston 33 is displaced in the direction of the piston 32 by the plate spring assembly 43.
  • the position of the threaded pin 36 can be adjusted by the nut 37 and thus the distance between the face of the threaded pin and the plate 23A; the braking force is thereby variably adjustable, which is particularly advantageous.
  • the housing part 12A, 13A of the braking device of this exemplary embodiment naturally also has a plurality of bores 31 again, such as the exemplary embodiment according to FIGS. 1 to 3.
  • a common brake plate for several pressure pistons can also be used instead of a circular brake plate.
  • the braking device is not limited to a type of working cylinder with a drawstring, but is generally applicable to rodless working cylinders.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Braking Arrangements (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem kolbenstangenlosen Arbeitszylinder nach der Gattung des Hauptanspruchs.The invention relates to a rodless cylinder according to the preamble of the main claim.

Bei derartigen kolbenstangenlosen Arbeitszylindern ist es wesentlich, daß die Kraftabnahme schnell und sehr genau positioniert werden kann. Zu diesem Zweck ist es bekannt, um den Kolben eine druckbeaufschlagbare Manschette zu legen, die über ein Ventil angesteuert wird und durch Aufblasen eine Bremskraft auf den Kolben ausübt. Es hat sich gezeigt, daß eine solche Bremseinrichtung für die meisten Anwendungsfälle genügt, die wirksame Anpreßkraft jedoch nicht optimal wirksam wird.With such rodless working cylinders, it is essential that the power take-off can be positioned quickly and very precisely. For this purpose, it is known to place a pressurizable sleeve on the piston, which is controlled by a valve and exerts a braking force on the piston by inflation. It has been shown that such a braking device is sufficient for most applications, but the effective contact pressure is not optimally effective.

Ferner ist aus der DE-A 34 03 830 ein kolbenstangenloser Arbeitszylinder mit allen gattungsbildenden Merkmalen bekannt, bei dem in die Kraftabnahme bereits eine Bremseinrichtung integriert ist, wodurch sich präzise und schnell eine gleichmäßig wirkende Bremskraft erzeugen läßt. Durch die Einleitung der Bremskräfte in der Ebene der Führung werden zudem die Momente in Längsrichtung vermindert. Bei dieser Bremseinrichtung weist ein schlittenförmiger Führungskörper auf entgegengesetzten Seiten jeweils einen Bremskolben auf, die in rechteckförmigen Ausnehmungen des Führungskörpers beweglich geführt sind. Jeder Bremskolben trägt außen einen Bremsbelag, der Flächenabschnitten an Profilteilen des Zylinderrohres gegenüberliegt, während er an seiner druckbeaufschlagten Innenseite ein gummiartiges Abdichtungselement aufweist. Nachteilig bei dieser Bauart ist nun, daß beim Abbremsen oder Halten der Kraftabnahme auftretende Längskräfte von diesen Bremskolben aufgenommen und übertragen werden, wobei die Funktion der Abdichtungselemente störend beeinflußt werden kann; in ungünstigen Fällen kann dies zu einer Leckage und damit zum vorzeitigen Ausfall der Bremse führen.Furthermore, from DE-A 34 03 830 a rodless cylinder with all generic features is known, in which a braking device is already integrated in the power take-off, whereby a uniformly acting braking force can be generated precisely and quickly. By introducing the braking forces in the plane of the guide, the moments in the longitudinal direction are also reduced. In this braking device, a slide-shaped guide body has a brake piston on opposite sides, which in rectangular recesses of the guide body are movably guided. Each brake piston carries a brake lining on the outside, which lies opposite surface sections on profile parts of the cylinder tube, while it has a rubber-like sealing element on its pressurized inside. The disadvantage of this type of construction is that longitudinal forces occurring when braking or holding the power take-off are absorbed and transmitted by these brake pistons, and the function of the sealing elements can be disrupted; in unfavorable cases, this can lead to leakage and thus to premature brake failure.

Erfindungsgemäß werden diese Nachteile durch die im Kennzeichnen des Anspruchs 1 genannten Merkmale vermieden.According to the invention, these disadvantages are avoided by the features mentioned in the characterizing part of claim 1.

Vorteile der ErfindungAdvantages of the invention

Der erfindungsgemäße kolbenstangenlose Arbeitszylinder hat demgegenüber den Vorteil, daß durch die Trennung von Druckkolben und Bremsplatte eine in Längsrichtung wirkende Kraft auf die Dichtungen der Druckkolben vermieden wird. Eine dadurch mögliche Leckage, die zum Ausfall der Bremse führen kann, ist somit ausgeschlossen. Ferner kann durch die Trennung dieser beiden Bauelemente die Krafteinleitung auch außermittig erfolgen. Die Bremseinheit kann als Druckbremse oder auch als Druckausfallbremse ausgeführt sein. Besonders günstig sind Ausbildungen nach den Ansprüchen 7 und 8. Dadurch wirken die Bremskräfte von beiden Seiten gleichmäßig auf das Gehäuseprofil und stützen sich an der Kraftabnahme ab; ferner wirken beim Bremsen keine zusätzlichen seitlichen Kräfte und Momente auf die Führung. Weitere vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den übrigen Unteransprüchen, die eine kompakte und kostengünstige Bremseinrichtung begünstigen und einen uneingeschränkten Anbau von elektrischen Schaltern und Befestigungsteilen gestatten.In contrast, the rodless working cylinder according to the invention has the advantage that a force acting in the longitudinal direction on the seals of the pressure pistons is avoided by the separation of the pressure piston and brake plate. A possible leakage, which can lead to brake failure, is therefore excluded. Furthermore, the separation of these two components allows the force to be introduced off-center. The brake unit can be designed as a pressure brake or as a pressure drop brake. Formations according to claims 7 and 8 are particularly favorable. As a result, the braking forces act uniformly from both sides on the housing profile and are supported on the power take-off; furthermore, no additional lateral forces and moments act on the guide when braking. Further advantageous embodiments of the invention emerge from the remaining subclaims, which favor a compact and inexpensive braking device and permit unrestricted attachment of electrical switches and fastening parts.

Zeichnungdrawing

Die Zeichnung zeigt in den Figuren 1 bis 3 ein erstes Ausführungsbeispiel einer Bremseinrichtung für einen kolbenstangenlosen Arbeitszylinder, und zwar in Figur 1 einen Querschnitt durch die Bremseinrichtung, in Figur 2 eine Seitenansicht und in Figur 3 eine Draufsicht. Die Figur 4 zeigt einen Querschnitt durch eine als Druckausfallbremse ausgebildete Bremseinrichtung.The drawing shows in Figures 1 to 3 a first embodiment of a braking device for a rodless cylinder, in Figure 1 a cross section through the braking device, in Figure 2 a side view and in Figure 3 a plan view. FIG. 4 shows a cross section through a braking device designed as a pressure drop brake.

Beschreibung der ErfindungDescription of the invention

In Figur 1 ist das Gehäuse 10 eines kolbenstangenlosen Arbeitszylinders im Querschnitt und lediglich gestrichelt dargestellt, da nicht unmittelbar erfindungswesentlich. Die Bewegung des Arbeitskolbens 11B wird über ein Band auf eine am Gehäuse gleitende Führung 11C zur Kraftabnahme 11 übertragen, die außerhalb des Gehäuses 10 angeordnet ist und zur Kraftübertragung dient. Beidseitig an die Kraftabnahme 11 ist links ein erstes Gehäuseteil 12 und rechts ein zweites Gehäuseteil 13 der erfindungsgemäßen Bremseinrichtung 14 angeschraubt. Die beiden Gehäuseteile sind identisch ausgebildet. Das Gehäuseteil 12 weist vier sacklochartige Bohrungen 15 bis 18 auf, deren Achsen senkrecht zur Längsachse des Gehäuses 10 des Arbeitszylinders verlaufen, jedoch in derselben horizontalen Ebene angeordnet sind. Die Bohrungen 15 bis 18 dringen in das Gehäuseteil 12 von der dem Gehäuse 10 zugewandten Seite ein, der Grund der Bohrungen ist jeweils flach. In jeder Bohrung, deren axiale Baulänge sehr kurz ist, ist ein Druckkolben 19 angeordnet, welcher an seinem Außenumfang einen Dichtring 20 aufweist. In einer auf die Bohrungen 15 bis 18 folgenden Stufe ist eine rechteckige Ausnehmung 22 ausgebildet, in welcher passend eine Platte 23 geführt angeordnet ist, gegen welche sich die Stirnseiten der Kolben anlegen. An der Platte 23 ist ein Bremsbelag 24 fest angebracht, welcher fast unmittelbar an der als Bremsfläche dienenden Seitenwand 25 des Gehäuses 10 des Arbeitszylinders anliegt.In Figure 1, the housing 10 of a rodless working cylinder is shown in cross section and only in dashed lines, since it is not directly essential to the invention. The movement of the working piston 11B is transmitted via a band to a guide 11C sliding on the housing for power take-off 11, which is arranged outside the housing 10 and is used for power transmission. On both sides of the power take-off 11, a first housing part 12 is screwed on the left and a second housing part 13 of the braking device 14 according to the invention is screwed on the right. The two housing parts are identical. The housing part 12 has four blind holes 15 to 18, the axes of which are perpendicular to the longitudinal axis of the housing 10 of the working cylinder, but are arranged in the same horizontal plane. The holes 15 to 18 penetrate into the housing part 12 from the side facing the housing 10, the bottom of the holes is each flat. In each bore, the axial length of which is very short, a pressure piston 19 is arranged, which has a sealing ring 20 on its outer circumference. In a step following the bores 15 to 18, a rectangular recess 22 is formed, in which a plate 23 is suitably arranged, against which the end faces of the pistons bear. On the plate 23, a brake pad 24 is fixedly attached, which abuts the side wall 25 of the housing 10 of the working cylinder serving almost as a braking surface.

Zwischen jedem Kolben 19 und dem Grund der Bohrungen 15 bis 18 befindet sich ein Druckraum 26, wobei in jedem dieser Druckräume ein Kanal 27 mündet, der mit einem Rohr 28 verbunden ist, welches im Gehäuseteil 13 steckt. Diesem Gehäuseteil wird über ein Kanalsystem 29 über weiter nicht dargestellte Mittel Druckluft zugeführt, und zwar über ein ebenfalls nicht dargestelltes Ventilsystem, da dieses nicht erfindungswesentlich ist. Es sei noch erwähnt, daß die Gehäuseteile 13 und 14 mit Hilfe von Schrauben 30 mit der Kraftabnahme 11 verbunden sind. Diese Schrauben sind in den Figuren 2 und 3 gut zu erkennen.A pressure chamber 26 is located between each piston 19 and the base of the bores 15 to 18, a channel 27 opening into each of these pressure chambers, which channel is connected to a tube 28 which is inserted in the housing part 13. Compressed air is supplied to this housing part via a channel system 29 by means not shown, namely via a valve system, also not shown, since this is not essential to the invention. It should also be mentioned that the housing parts 13 and 14 are connected to the power take-off 11 by means of screws 30. These screws can be clearly seen in FIGS. 2 and 3.

Wenn die Druckräume 26 an den die Kolben 19 aufnehmenden Bohrungen mit Druckluft beaufschlagt werden, so drücken sie auf die rechteckige Platte 23 und diese wird mit ihrem Bremsbelag 24 an die entsprechende Bremsfläche am Gehäuse 10 des Arbeitszylinders angedrückt. Eine derartige Ausbildung hat den Vorteil, daß eine verhältnismäßig große Kraft - vier Kolben - gleichmäßig auf die Platte 23 drückt. Da Kolben und Bremsplatte getrennt ausgeführt sind, kann die Krafteinleitung auch außermittig erfolgen. Aus dem oben Beschriebenen ist zu erkennen, daß die Bremseinrichtung als Druckbremse ausgeführt ist.When the pressure chambers 26 are pressurized with compressed air at the bores receiving the pistons 19, they press on the rectangular plate 23 and this is pressed with its brake lining 24 onto the corresponding braking surface on the housing 10 of the working cylinder. Such training has the advantage that a relatively large force - four pistons - presses evenly on the plate 23. Since the piston and brake plate are designed separately, the force can also be applied off-center. It can be seen from what has been described above that the braking device is designed as a pressure brake.

Das Ausführungsbeispiel 2 nach der Figur 4 ist als Druckausfallbremse ausgebildet, d.h. bei Beaufschlagung der Kolben wird die Bremse gelöst. Darauf ist aber weiter unten noch eingegangen. Die Kraftabnahme - bezeichnet mit 11A - weist wiederum mehrere Bohrungen 31 auf, in welchen zwei Kolben 32, 33 geführt sind, welche außen wieder durch nicht weiter bezeichnete Dichtringe abgedichtet sind. Beide Kolben haben eine mittige Bohrung 34 bzw. 35, wobei in die Bohrung 35 ein Schraubstift 36 eingeschraubt ist und durch eine Mutter 37 festgehalten bzw. in seiner axialen Richtung eingestellt werden kann und sein Stiftteil 38 durch die Bohrung 34 dringt. Beide Bohrungen sind wiederum durch nicht weiter bezeichnete Dichtringe abgedichtet. Der Druckraum ist mit 40 bezeichnet und liegt zwischen den beiden Kolben 32, 33. In den Druckraum 40 mündet ein Kanal 41, welcher wiederum über ein nicht weiter dargestelltes Kanalsystem mit Druckluft beaufschlagt werden kann. Auf den Kolben 33 wirkt ein Tellerfederpaket 43 ein, das sich an einer Schulter der Bohrung 31 abstützt. Wiederum in der zylindrischen Ausnehmung geführt liegt eine kreisförmige Platte 23A mit Bremsbelag 24A; die Platte 23A ist vom Stiftteil 38 getrennt. Das Tellerfederpaket 43 drückt über den Kolben 33 und den Schraubstift 36 die Bremsplatte und ihren Bremsbelag gegen die Bremsfläche 10B des Gehäuses 10 des Arbeitszylinders. Die Kraftabnahme 11A ist nun festgebremst. Durch die Beaufschlagung des Druckraums 40 wird der Kolben 33 entgegen der Kraft des Tellerfederpakets 43 derart verschoben, daß sich der Stift 38 von der Platte 23A abhebt. Der Kolben 32 stützt sich stets an einem Sprengring 44 ab. Die Kraftabnahme ist nun gelöst und kann durch den Kolben des Arbeitszylinders bewegt werden. Die rechte Seite der Figur 4 zeigt, wie der Kolben 33 durch das Tellerfederpaket 43 in Richtung zum Kolben 32 hin verschoben wird. Durch die Mutter 37 kann die Lage des Gewindestifts 36 eingestellt werden und damit der Abstand zwischen der Stirnseite des Gewindestifts und der Platte 23A; die Bremskraft ist dadurch variabel einstellbar, was besonders vorteilhaft ist. Das Gehäuseteil 12A, 13A der Bremseinrichtung dieses Ausführungsbeispiels weist natürlich ebenfalls wieder mehrere Bohrungen 31 auf, so wie das Ausführungbeispiel nach den Figuren 1 bis 3.The exemplary embodiment 2 according to FIG. 4 is designed as a pressure drop brake, ie the brake is released when the pistons are acted on. However, this was discussed further below. The power take-off - designated 11A - in turn has a plurality of bores 31, in which two pistons 32, 33 are guided, which are again sealed on the outside by sealing rings (not further designated). Both pistons have a central bore 34 or 35, a screw pin 36 being screwed into the bore 35 and being held by a nut 37 or being able to be adjusted in its axial direction and its pin part 38 penetrating through the bore 34. Both bores are in turn sealed by sealing rings, which are not further specified. The pressure chamber is designated by 40 and lies between the two pistons 32, 33. A channel 41 opens into the pressure chamber 40, which in turn can be pressurized with compressed air via a channel system (not shown). The piston 33 acts Belleville washer 43, which is supported on a shoulder of the bore 31. Once again guided in the cylindrical recess is a circular plate 23A with a brake pad 24A; the plate 23A is separated from the pin part 38. The plate spring assembly 43 presses the brake plate and its brake lining against the braking surface 10B of the housing 10 of the working cylinder via the piston 33 and the screw pin 36. The power take-off 11A is now braked. By acting on the pressure chamber 40, the piston 33 is displaced against the force of the plate spring assembly 43 in such a way that the pin 38 lifts off the plate 23A. The piston 32 is always supported on a snap ring 44. The power take-off is now released and can be moved by the piston of the working cylinder. The right side of FIG. 4 shows how the piston 33 is displaced in the direction of the piston 32 by the plate spring assembly 43. The position of the threaded pin 36 can be adjusted by the nut 37 and thus the distance between the face of the threaded pin and the plate 23A; the braking force is thereby variably adjustable, which is particularly advantageous. The housing part 12A, 13A of the braking device of this exemplary embodiment naturally also has a plurality of bores 31 again, such as the exemplary embodiment according to FIGS. 1 to 3.

Selbstverständlich sind an den gezeigten Ausführungsformen Änderungen möglich, ohne vom Gedanken der Erfindung abzuweichen. So läßt sich in Figur 4 anstelle einer kreisförmigen Bremsplatte auch eine gemeinsame Bremsplatte für mehrere Druckkolben verwenden. Die Bremseinrichtung ist nicht auf eine Bauart des Arbeitszylinders mit Zugband begrenzt, sondern allgemein bei kolbenstangenlosen Arbeitszylindern anwendbar.Of course, changes are possible to the embodiments shown without departing from the spirit of the invention. Thus, in FIG. 4, a common brake plate for several pressure pistons can also be used instead of a circular brake plate. The braking device is not limited to a type of working cylinder with a drawstring, but is generally applicable to rodless working cylinders.

Claims (12)

  1. Rodless power cylinder, the pressure-actuated piston of which drives a power take-off (11, 11A), and with a braking device (14, 14A) which by pressure actuation or pressure relief of a braking element, brakes the power take-off for the purpose of positioning, the braking device (14, 14A) being arranged on the power take-off (11, 11A), characterized in that the braking device (14, 14A) has a plurality of pistons (19; 33) which are arranged in bores (15 to 18; 31) and the axes of which extend perpendicularly to braking surfaces on the housing wall (25) of the power cylinder, and in that at least one pressure piston (19, 33) is assigned a brake plate (23, 23A) which is separated from the latter and is guided separately.
  2. Power cylinder according to Claim 1, characterized in that the pressure pistons (19) are pressed against the brake plate (23) by actuation by means of a pressure medium.
  3. Power cylinder according to Claim 1, characterized in that the pressure pistons (33) are loaded in the braking direction by a spring, in particular a Belleville spring (43), and in the release direction by the pressure of a pressure medium.
  4. Power cylinder according to one of Claims 1 to 4, characterized in that the bores (15 to 18; 31) accommodating the pressure pistons are arranged in a separate housing part (13, 14) which is secured on the power take-off (11).
  5. Power cylinder according to Claim 1, 3 and 4, characterized in that the bore (31) has arranged in it two pistons (32, 33), between which the pressure chamber (40) which can be pressurized by the pressure medium is situated, in that both pistons have an aligned central hole (34, 35) through which there leads a threaded pin, in that the free end of the threaded pin makes contact with the plate (23A), and the threaded pin is guided in a thread in the other, outer piston (33) and can be fixed with the aid of a nut (37).
  6. Power cylinder according to one of Claims 1 to 5, characterized in that each pressure piston (19; 33) is assigned a separate brake plate (23, 23A).
  7. Power cylinder according to one of Claims 1 to 6, characterized in that the housing parts (12, 13) of the braking device (14, 14A) are arranged symmetrically with respect to the power take-off (11, 11A) with the result that the pressure pistons lie essentially opposite one another on both sides.
  8. Power cylinder according to Claim 7, characterized in that it has a guide (11C) which is separate from the power piston (11B) and in that the guide (11C) and the axes of the pressure pistons (19; 33) lie essentially in the same plane.
  9. Power cylinder according to one or more of Claims 1 to 8, characterized in that a plurality of bores (15 to 18) with pressure pistons (19; 33) which are, in particular, of equal size, is arranged on one side of the braking device (14, 14A).
  10. Power cylinder according to one or more of Claims 1, 2, 4, 6 to 9, characterized in that the pressure pistons (19; 33) are each designed as circular plates, on the outer circumference of which a sealing ring (20) is arranged.
  11. Power cylinder according to Claim 10, characterized in that a plurality of pressure pistons (19) is assigned a common brake plate (23).
  12. Power cylinder according to one of Claims 4, 6 to 11, characterized in that the housing part (12, 13) has a depression which is open on one side and, on the inside, has pocket holes (15 to 18) that guide the pressure pistons (19) and which merges towards the outside into a recess (22) which guides the brake plate (23).
EP93118855A 1992-12-18 1993-11-24 Rodless power cylinder Expired - Lifetime EP0602417B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4242971 1992-12-18
DE4242971A DE4242971A1 (en) 1992-12-18 1992-12-18 Rodless cylinder

Publications (2)

Publication Number Publication Date
EP0602417A1 EP0602417A1 (en) 1994-06-22
EP0602417B1 true EP0602417B1 (en) 1997-06-04

Family

ID=6475772

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93118855A Expired - Lifetime EP0602417B1 (en) 1992-12-18 1993-11-24 Rodless power cylinder

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EP (1) EP0602417B1 (en)
DE (2) DE4242971A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3434369B2 (en) * 1994-11-14 2003-08-04 Ｓｍｃ株式会社 Rodless cylinder
DE19540502A1 (en) * 1995-10-31 1997-05-07 Festo Kg Fluid operated rodless linear actuator

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3403830A1 (en) * 1983-04-12 1984-10-18 Knorr-Bremse GmbH, 8000 München Fluid-operated, rodless working cylinder
DE3514074A1 (en) * 1985-04-18 1986-10-23 Herion-Werke Kg, 7012 Fellbach Rodless cylinder
SE464534B (en) * 1987-11-11 1991-05-06 Bo Granbom BRAKE DEVICE FOR A DEVICE FOR LINEAR MOVEMENT

Also Published As

Publication number Publication date
EP0602417A1 (en) 1994-06-22
DE4242971A1 (en) 1994-06-23
DE59306662D1 (en) 1997-07-10

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