EP0104364B1 - Vérin sans tige de piston avec frein - Google Patents

Vérin sans tige de piston avec frein Download PDF

Info

Publication number
EP0104364B1
EP0104364B1 EP83107549A EP83107549A EP0104364B1 EP 0104364 B1 EP0104364 B1 EP 0104364B1 EP 83107549 A EP83107549 A EP 83107549A EP 83107549 A EP83107549 A EP 83107549A EP 0104364 B1 EP0104364 B1 EP 0104364B1
Authority
EP
European Patent Office
Prior art keywords
working cylinder
guide chamber
housing
cylinder according
slot
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
Application number
EP83107549A
Other languages
German (de)
English (en)
Other versions
EP0104364A1 (fr
Inventor
Dieter Mai
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Knorr Bremse AG
Original Assignee
Knorr Bremse AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE19823229305 external-priority patent/DE3229305A1/de
Application filed by Knorr Bremse AG filed Critical Knorr Bremse AG
Priority to DE8585112239T priority Critical patent/DE3374707D1/de
Priority to AT85112239T priority patent/ATE31108T1/de
Priority to AT83107549T priority patent/ATE20123T1/de
Publication of EP0104364A1 publication Critical patent/EP0104364A1/fr
Application granted granted Critical
Publication of EP0104364B1 publication Critical patent/EP0104364B1/fr
Expired legal-status Critical Current

Links

Images

Classifications

    • 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
    • F15B15/08—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 working cylinder with a braking device according to the preamble of patent claim 1.
  • Fluid-driven rodless working cylinders which have power take-offs guided on the outside of the cylinder tube, which can be magnetically or mechanically connected to the piston.
  • the mechanical connection is made via a circumferential transmission element, in particular a belt, or via a rigid holder which projects through a sealable slot in the cylinder tube.
  • the invention relates preferably, but not exclusively, to band cylinders which carry rollers on their end faces, over which a band is preferably guided, which connects the piston to the power consumer.
  • a known braking device for a band cylinder comprises the cylinder tube concentrically with at least one brake pad and is integrated in the power take-off (EP-A-29188).
  • the power take-off also comprises the cylinder tube concentrically.
  • the known braking device can then be designed as a bellows, which is arranged on the cylindrical inner wall of the power take-off comprising play and which concentrically surrounds the cylinder tube.
  • the bellows is expanded by supplying a fluid, the brake linings coming to bear against the cylindrical outer circumference of the cylinder tube for braking or stopping the force transducer moved by the piston.
  • an external casing can be provided to prevent rotation of the power take-off concentrically surrounding the cylinder tube, which is fixed to the ends of the cylinder tube and on whose profiled inner surfaces the power take-off can be rotated in the longitudinal direction of the cylinder tube.
  • the forces acting on the power take-off are only partially absorbed by the housing of the working cylinder.
  • the power take-off is arranged on a carriage provided with rollers, which is guided in a longitudinally displaceable manner in a guide space extending over the length of the working cylinder, the housing of which is firmly connected to the cylinder housing of the working cylinder .
  • the known working cylinder does not have a braking device which holds the power consumer in a desired position on the cylinder housing.
  • the object of the invention is to provide an improved piston rodless cylinder of the type mentioned, the power take-off is guided against rotation and is provided with at least one braking device.
  • the forces acting on the power consumer are to be absorbed completely by the housing of the working cylinder, the diameter of the working cylinder thus being kept largely small for the power consumer and the braking device.
  • All exemplary embodiments show working cylinders according to the invention in cross section through the power consumer.
  • the same reference symbols in the figures denote the same or corresponding parts.
  • the exemplary embodiments according to FIGS. 1 to 4 and 6 are band or rope cylinders.
  • the exemplary embodiment according to the figure is a slotted working cylinder that works together with a masking tape. It is clear that the exemplary embodiments according to FIGS. 1 and 2 can be provided with a cylinder wall opening corresponding to FIG. 5.
  • the cylinder tube of a band cylinder is denoted by 1, which in the example is designed as a square tube with flat surfaces.
  • the cylinder tube 1 On the long sides of the cylinder tube 1 there are L-shaped profile parts 2 and 3 which project above the cylinder tube and whose inwardly directed sections 2 'and 3' have a shaft-like guide space 4 with a rectangular cross-section which extends over the length of the cylinder tube 1 delimit the middle, in the axial direction of the cylinder tube extending guide gap 5 between the opposite forehead is open to the outside at the free ends of the sections 2 'and 3'.
  • the housing of the guide space 4 is designated 1 '.
  • a slide-like body 6 is displaceable in the shaft-shaped guide space 4, on which an arm 7, which projects vertically upwards and engages through the gap 5, engages in the center.
  • the arm 7 forms, together with the sled-like body 6, the power take-off 8 of the band cylinder.
  • the power take-off 8 is connected to the piston in a manner known per se via a circulating belt.
  • the band can be divided in a known manner into two sections, one section of which engages with one end at the front longitudinal end of the sled-like body 6 and is guided in a pressure-tight manner via a first roller at the front end of the cylinder tube through a sealed slot in the front cylinder head to attack with its front end on one side of the piston.
  • the other section of the band engages with its one end at the opposite rear longitudinal end of the sled-like body 6 and is pressure-tightly guided via a second roller at the rear end of the cylinder tube through a further sealed slot in the rear cylinder head, with its other end at the opposite one Side of the piston.
  • the axial length of the force transducer 8 can be selected in accordance with the axial length of the force transducer of known band cylinders.
  • the braking device is integrated in the sled-like body 6.
  • the sled-like body 6 is double T-shaped in cross section.
  • 6 recesses 9 and 10 are formed with a rectangular cross-section on the two long sides of the sled-like body, in which brake bodies 11 and 12 are slidably guided, the brake pads 13 and 14 carry on their outer end faces, the inner surface portions 15 and 16 on the existing profile parts 2 and 3 on the longitudinal side of the cylinder tube 1.
  • the surface sections 15 and 16 can be formed by flat parts 17 and 18, which are held on the inner surfaces of the profile parts 2 and 3.
  • Pressure pad-like sealing elements 19 and 20 are provided on the inner end faces of the brake bodies 11 and 12, the outer edges 21 and 22 of which lie like lips on the inner guide surfaces of the recesses 9 and 10 in the slide-like body 6. In this way, pressure-tight spaces 23 and 24 are formed between the pressure pad-like sealing elements 19 and 20 made of rubber or plastic and the inner boundaries of the recess 9 and 10. The spaces are connected via cross bores 25 and 26 to a longitudinal bore 27 in the arm 7.
  • the arm 7 has at its upper end a connection for a flexible hose, which is not shown here and is connected to the longitudinal bore 27 via the pressure medium from a pressure medium source, in particular a compressed air source.
  • the pressure-tight spaces 23 and 24 can also be connected to a pressure medium source in a manner other than that shown. Furthermore, it is clear that instead of the two pressure bodies 11 and 12 which can be spread apart for braking, only a single pressure body can be arranged displaceably in the sled-like part 6 of the power take-off 8, which, for. B. be pressed pneumatically with a friction lining against the outer tubular profile surface 28 of the square cylinder tube 1 in order to brake and / or position the power consumer 8.
  • the shaft-like guide space 4 on the one hand represents a rotation-proof guide for the power take-off 8 and has surfaces 15, 16 on which the braking device 11-15 and 19-22 integrated in the power take-off 8 can be supported when pressure medium is applied.
  • the shaft-like guide space 4 with the guide slot 5 need not have the shape shown in the figure. It is correct that the inner housing-fixed surfaces 15 and 16 in the broadest sense are to be understood as housing-fixed profile sections 15 and 16 of the cylinder tube 1, on which the braking device 11-14 and 19-22 can be supported within the power take-off 6. It has already been said above that the braking device has at least one pressure body and that accordingly only a profile section of the cylinder tube 1 must be present, on which the braking device can be supported.
  • the cylinder tube need not have the profile shape shown in Figure 1.
  • the person skilled in the art recognizes that the cylinder tube can be profiled in various ways, the profile surfaces for the braking device being able to be made in one piece with the cylinder tube or can belong to housing parts which are held on the cylinder tube.
  • first profile surfaces including the reference number 28
  • second profile surfaces 15, 16 for supporting the braking device 11-14 and 19-22.
  • the forces acting on the force transducer 8 are essentially absorbed by a profile surface 28 of the cylinder tube, the surface dimensions of which are independent of the diameter of the cylinder tube 1.
  • the force transducer 8 contains the braking device 11 -14 and 19-22 without this covering the cylinder barrel.
  • the profile surfaces 15 and 16 fixed to the housing can be selected regardless of the diameter of the cylinder tube in terms of their surface size and surface shape in such a way that optimum braking and positioning of the force transducer 8 is possible, the friction flows of the brake device in the released state also largely reducing the ease of displacement of the force transducer exert little influence.
  • the embodiment according to FIG. 2 differs from the embodiment according to FIG. 1 in that the shaft-shaped guide space 4, in which the power consumer 8 can be displaced, is not rectangular, but hexagonal. In this way, the surfaces 15 and 16 fixed to the housing can be designed in a wedge shape, as shown in FIG.
  • the front end faces of the pressure bodies 11 and 12 can be wedge-shaped, so that wedge-shaped brake pads 13 and 14 are provided, which come into contact with the wedge-shaped surfaces 15 and 16.
  • the section sections 2 and 3 delimiting the shaft-shaped guide space 4 are, in the example, in one piece with the cylinder tube 1. It is of course clear that the section sections 2 and 3 can also belong to a section body connected to the cylinder tube 1.
  • the wedge-shaped braking device can be advantageous over the braking device according to FIG. 1, since the available braking surface is enlarged and the wedge knitting can be used depending on the selected wedge angle for braking. It is clear that springs are then expediently present which move the brake bodies back into their release position after braking.
  • FIG. 2 It is particularly clear from FIG. 2 that the invention is not restricted to the embodiment according to FIG. 1.
  • Figure 3 shows a cross section through a working cylinder similar to that of Figure 1 and Figure 2.
  • the guide space 4 here has a special elongated cross section, each with outwardly rounded side surfaces 45 and 46 and a force transducer 8 which is formed by the sled-like body 6 and an arm or driver 7 which engages centrally on the body 6 and which is formed by the gap 5 of the lead room protrudes outwards.
  • the sled-like body 6 is partially broken open in FIG. 4 compared to FIG. 3 as a detail and shown in section.
  • the one rope ends of the rope sections, not shown, are held, each of which is connected from one side of the arm to one side of the piston via a roller at one end of the working cylinder.
  • a cover tape (not shown in FIG. 3) is guided through a gap 47 in the driver 7 of the power take-off 8 and is held with its two ends at the ends of the working cylinder and closes the gap 5 of the guide space 4 largely dust-tight.
  • channels 27 with a connection 51 to a pressure medium source, not shown, for operating a braking device which is integrated in the carriage-like body 6.
  • the channels 50 connect to a tube 52 in a transverse bore 53 which penetrates the driver.
  • the carriage-like body 6 shown as a whole in FIG. 4 is 54 and 55 with its two ends specially adapted to the shape of the inner boundary walls of the guide space 4, which is elongate in cross section. Between the two ends 54 and 55, the carriage-like recesses 56 and 57 of the same type on both sides, in which movable membrane holders 58 and 59 are arranged, which have bores 60 and 61, in which the ends of the tube 52 slidably engage.
  • the bores 60 and 61 are connected to channels 62 and 63 (FIG. 6) which are connected to the pressure medium connection 51 via the bores 60 and 61, the tube 52 and the channels 50.
  • the membrane holders 58 and 59 carry membranes 64 and 65, which overlap the membrane holder like a shoe.
  • the folded membrane ends are held on the rear sides of the membrane holders 58 and 59 with a plate 66 and 67.
  • the plates 66 and 67 can be screwed to the membrane holders 58 and 59 with screws, not shown.
  • the membrane holder 58 and 59 are held with the membranes 64 and 65 in the recesses 56 and 57 of the sled-like body 6 with little play on the Rochrenden the tube 52.
  • sealing rings 68 and 69 are provided, which are located in grooves in the borehole walls of the bore 60 and 61.
  • strip-shaped brake pads 70 and 71 which, when the membranes are pressurized by supplying pressure medium via the connection 51, the channels 50, the tube 52 and the channels 62 and 63 by expanding the membranes 64 and 65 be pressed against the inner walls of the guide space 4 in order to hold the sled-like body 6 and thus the power take-off 8 in a desired position on the brake cylinder or to brake the piston movement. Thanks to the movable mounting of the membrane retainers 58 and 59 at the ends of the tube 52, this is pressed into the correct position when pressure is applied.
  • the horizontal extent of the guide space in FIG. 1 is advantageously somewhat larger than the diameter of the cylinder cavity 73 for the cylindrical piston shown cut in its central section.
  • the width / height ratio of the guide space 4 is advantageously greater than 2: 1, preferably about 3: 1.
  • Relative to the elongated cross section of the stirring space, the average length of the cross section being greater than the average width, the length / width ratio is advantageously greater than 2: 1, preferably about 3: 1.
  • FIG. 5 shows a cross section through a working cylinder according to the invention corresponding to FIG. 3.
  • the section here lies in one plane in the region of one end 54 or 55 of the sled-like body 6, that is to say outside the braking device.
  • Figure 5 differs from Figure 3 essentially only in that the housing partition 74 between the cylinder cavity 73 and the guide space 4 has a gap or slot 75 through which an arm, not shown, engages around the piston, also not shown, in the cylinder cavity to connect the power take-off 8.
  • a cover band 76 is provided which engages to cover the gap 75 in a groove 77, wherein it connects on the inside to the cylindrical inner wall of the cylinder cavity.
  • the band On the outside, the band has a profile with longitudinal, rib-shaped elevations 78 and 79, which engage or press into corresponding groove-shaped depressions along the edges of the slot 75 in order to close the gap 75 in a pressure-tight manner.
  • the further cover strip which in the example has no profile, for covering the slot-shaped opening 5 of the guide space 4 is designated by 84. It can be seen from FIGS. 3 and 5 that the same tubular profile, which on the one hand includes the cylinder cavity 73 and on the other hand the guide space 4 for the power take-off 8, can be used for a band or cable cylinder and for a so-called slotted cylinder.
  • the profile according to the invention which includes the cylinder cavity 73 and the guide space 4 and can be referred to as a double tube, can, for. B. made of aluminum in the extrusion process.
  • FIG. 6 shows yet another cross section through a working cylinder according to the invention, in which a cylindrical tube 1 for receiving the piston, not shown, is connected via a connecting web 81 which extends over the tube length to a frame-like housing 1 ', which has the guide space 4 in its interior forms the power consumer 8.
  • the power take-off 8 here consists of a sled-like body 6, in the form of a tube section, which comprises the cylindrical tube 1 and has a slot 83 through which the connecting web 81 engages.
  • a driver 7 engages, which together with the sled-like body 6 Power take-off 8 forms.
  • the driver 7 projects through a slot-like opening 5 into the frame-like housing 1 '.
  • the driver 7 can be designed corresponding to the drivers in Figures 3 and 5.
  • the masking tape for the opening 5 is designated 84 as in FIG. 5.
  • the power take-off 8 is guided in the opening 5 and / or on the connecting web 81 so that it cannot rotate.
  • materials known per se are arranged in the gaps or slots between the opening edges of the opening 5 and the driver 7 and / or between the opening edges of the opening 83 and the connecting web 81, which enable good sliding guidance.
  • a bellows 85 is arranged on the tubular inner wall of the sled-like body 6 and brake linings 85 'are present between the bellows 85 and the outer surface of the cylindrical tube 8, the interruptions of which in the form of ring segments are not shown.
  • the driver 7 which can be connected to a pressure medium source according to FIG. 3, the space between the inner wall of the slide-like body 6 and the bellows 85 can be acted upon with pressure medium.
  • the driver has, according to FIG. 3, channels which ensure the pressure medium influence on the space between the inner wall of the slide-like body 6 and the bellows 85.
  • the brake linings are pressed against the outer wall of the cylindrical tube 1.
  • the covering can also be composed of two half-shell-shaped halves, which each extend from the attachment of the driver on the tubular segment-like body 6 to the opening edge of the opening 83 in the body 6.
  • the cylindrical tube 1 can have a slot 74 as shown in FIG, which can be sealed with a cover tape 76 as shown in Figure 5.
  • the profile according to the invention shown in FIG. 1, with an internal cylindrical tube 1 for the piston (not shown) and a guide space 4 for the power take-off, the slide-like part of which engages around the cylindrical tube in the manner of a tube segment, can be used both for a band or rope cylinder and for a so-called slotted cylinder may be suitable.
  • Profiles 3 and 5 made of aluminum in the extrusion process.
  • the frame-like housing 1 'for forming the guide space 4 can also have a different cross section than that shown in FIG. In particular, it does not need to have a rectangular inner and / or outer border.
  • the invention shows the designer basic ways of specifying profiles for a rodless working cylinder that can be found in the Have the extrusion process made of aluminum and use a low profile. It is clear that the invention is not restricted to rodless working cylinders which have a braking device integrated in a carriage-like body of the power consumer. In particular, the explanations according to FIGS. 3 to 6 show basic solutions which are provided with braking devices.
  • the masking tape 84 serves to protect the slot 5 against contamination, as a result of which the guide space 4 can be kept clean even when the cylinder is used in a very dirty environment and trouble-free operation of the cylinder can be ensured.

Landscapes

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

Claims (19)

1. Cylindre de travail sans tige de piston, à commande par un fluide et à prise de force (8) guidée le long du carter de cylindre (1), sans pouvoir tourner, du type comportant un corps (6) en forme de chariot, qui est guidé longitudinalement dans une chambre de guidage (4) qui s'étend sensiblement sur la longueur du cylindre de travail et dont le carter (1') est relié rigidement au carter de cylindre (1), un entraîneur (7) porté par le corps (6) en forme de chariot se projetant hors de la chambre de guidage (4), caractérisé par le fait qu'au corps (6) en forme de chariot est intégré un dispositif de freinage (11-14) qui coagit par friction avec au moins une section de paroi limitant intérieurement la chambre de guidage (4).
2. Cylindre de travail selon la revendication 1, caractérisé par le fait que la chambre de guidage (4) comporte une ouverture en forme de fente (5) pour le passage de l'entraîneur (7).
3. Cylindre de travail selon la revendication 1 et 2, caractérisé par le fait que le carter (1) du cylindre de travail et le carter (1') de la chambre de guidage (4) constituent un double tube.
4. Cylindre de travail selon la revendication 3, caractérisé par le fait que le carter (1) du cylindre de travail se situe à l'intérieur du carter (1') de la chambre de guidage (4), le carter (1) du cylindre de travail étant relié fermement au carter (1') de la chambre de guidage (4) par l'intermédiaire d'une barrette de liaison allongée (81).
5. Cylindre de travail selon la revendication 4, caractérisé par le fait que le carter (1) du cylindre de travail comporte une surface latérale cylindrique qui se raccorde à la barrette de liaison (81).
6. Cylindre de travail selon la revendication 5, caractérisé par le fait que le corps (6) en forme de chariot de la prise de force (8) est constitué par une section tubulaire entourant sensiblement la surface latérale cylindrique du carter (1), et pourvue d'une fente longitudinale (83) pour le passage de la barrette de liaison (81).
7. Cylindre de travail selon la revendication 6, caractérisé par le fait que l'entraîneur (7) qui est porté par l'élément (6) en forme de chariot de la prise de force (8), est constitué par un appendice allongé qui passe, en vue du guidage, sans pouvoir tourner, de la prise de force, par l'ouverture (5) en forme de fente de la chambre de guidage (4).
8. Cylindre de travail selon la revendication 6 ou 7, caractérisé par le fait que les surfaces qui forment la fente longitudinale (43) et qui servent au guidage, sans rotation, de la prise de force (8), sont guidées au niveau de la barrette de liaison (81).
9. Cylindre de travail selon la revendication 2, caractérisé par le fait que la chambre de guidage (4) est séparée de la cavité (73) du cylindre de travail par une paroi de carter médiane.
10. Cylindre de travail selon la revendication 9, caractérisé par le fait que la chambre de guidage (4) comporte une section transversale allongée et la cavité (73) du cylindre de travail comporte une section transversale ronde, étant noté que le plan longitudinal passant par les deux axes de la cavité (73) du cylindre de travail et de la chambre de guidage (4), passe sensiblement par le milieu de l'ouverture (5) en forme de fente de la chambre de guidage et servant au passage de l'entraîneur porté par la prise de force (8).
11. Cylindre de travail selon la revendication 10, caractérisé par le fait que le diamètre longitudinal maximum de la chambre de guidage (4) est égal ou supérieur au diamètre de la cavité du cylindre de travail (73).
12. Cylindre de travail selon la revendication 10 ou 11, caractérisé par le fait que le rapport entre longueur/largeur de la chambre de guidage (4) est au moins égal à 2 : 1, de préférence à 3 : 1.
13. Cylindre de travail selon l'une des revendications 10 à 12, caractérisé par le fait que la chambre de guidage (4) est limitée respectivement par des surfaces latérales arrondies vers l'extérieur (45, 46) et par des surfaces longitudinales qui s'étendent sensiblement parallèlement entre elles.
14. Cylindre de travail selon la revendication 1, caractérisé par le fait que le dispositif de freinage est commandé par un milieu sous pression.
15. Cylindre de travail selon la revendication 14, caractérisé par le fait que le dispositif de freinage est constitué par au moins un support de membrane (58, 59) relié à une source de pression de freinage, et auquel est fixée de façon étanche, par ses bords, une membrane (64, 65), que le support de membrane (58, 59) possède au moins une ouverture qui relie la source de pression de freinage à la chambre située entre la membrane (64, 65) et le support de membrane (58, 59), et que sur les surfaces extérieures de la membrane (64, 65) sont prévues des garnitures de frein (70, 71) mobiles radialement, qui, dans le cas d'une charge en pression de la membrane, attaquent les sections de parois (45, 46) de la chambre de guidage (4).
16. Cylindre de travail selon la revendication 15, caractérisé par le fait que le dispositif de freinage comporte deux supports de membrane allongés (58, 59) dont chacun est disposé, avec jeu; dans des ouvertures latérales du corps en forme de chariot (6) et séparées par une barrette médiane, et qui sont reliées par un tube de raccord (52), à un perçage (50) ménagé dans la barrette médiane est relié à la source du milieu sous pression, et que le corps (6) en forme de chariot comporte, à l'extérieur de l'ouverture des surfaces de guidage qui sont adaptées aux surfaces de parois (45, 46) qui limitent l'ouverture prévue dans la chambre de guidage (4).
17. Cylindre de travail selon la revendication 1, caractérisé par le fait que pour recouvrir l'ouverture en forme de fente (5) de la chambre de guidage (4), il est prévu un ruban d'obturation (84) qui est relié, par ses deux extrémités, aux extrémités du cylindre de travail et qui est guidé par une fente (47) qui se situe à l'extérieur du cylindre de travail, dans la prise de force (8).
18. Cylindre de travail selon la revendication 1, caractérisé par le fait que la chambre de guidage (4) comporte des premières sections de parois (15, 16 ; 45, 46) qui sont réalisées sous la forme de surfaces de freinage, ainsi que des secondes sections de parois (5 ; 28) qui sont réalisées pour le guidage, sans rotation, de la prise de force (8).
19. Cylindre de travail selon une ou plusieurs des revendications précédentes, caractérisé par le fait que le piston du cylindre de travail est relié mécaniquement à la prise de force (8) à travers une ouverture en forme de fente (75) ménagée dans la paroi du carter du cylindre de travail, et qu'il est prévu un ruban (76) qui est fixé aux deux extrémités de la cavité du cylindre de travail (73) et qui est guidé par la liaison mécanique entre le cylindre de travail et la prise de force (8), lequel ruban (76) est réalisé de façon à être enfoncé à la manière de boutons ou à être refoulé dans les surfaces marginales profilées (77) qui limitent l'ouverture en forme de fente, en vue de recouvrir, de façon étanche au milieu sous pression, l'ouverture en forme de fente (75).
EP83107549A 1982-08-05 1983-08-01 Vérin sans tige de piston avec frein Expired EP0104364B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE8585112239T DE3374707D1 (en) 1982-08-05 1983-08-01 Rodless hydraulic ram
AT85112239T ATE31108T1 (de) 1982-08-05 1983-08-01 Fluidgetriebener kolbenstangenloser arbeitszylinder.
AT83107549T ATE20123T1 (de) 1982-08-05 1983-08-01 Kolbenstangenloser arbeitszylinder mit bremsvorrichtung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE19823229305 DE3229305A1 (de) 1982-08-05 1982-08-05 Bremseinrichtung fuer fluidgetriebene kolbenstangenlose arbeitszylinder
DE3229305 1982-08-05
DE3313206 1983-04-12
DE3313206 1983-04-12

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP85112239.0 Division-Into 1985-09-27

Publications (2)

Publication Number Publication Date
EP0104364A1 EP0104364A1 (fr) 1984-04-04
EP0104364B1 true EP0104364B1 (fr) 1986-05-28

Family

ID=25803578

Family Applications (2)

Application Number Title Priority Date Filing Date
EP85112239A Expired EP0177850B1 (fr) 1982-08-05 1983-08-01 Vérin hydraulique sans tige
EP83107549A Expired EP0104364B1 (fr) 1982-08-05 1983-08-01 Vérin sans tige de piston avec frein

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP85112239A Expired EP0177850B1 (fr) 1982-08-05 1983-08-01 Vérin hydraulique sans tige

Country Status (2)

Country Link
EP (2) EP0177850B1 (fr)
DE (2) DE3363754D1 (fr)

Families Citing this family (27)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3328786A1 (de) * 1983-08-10 1985-02-28 Robert Bosch Gmbh, 7000 Stuttgart Kolbenstangenloser arbeitszylinder
DE3429783A1 (de) * 1984-08-13 1986-02-20 Herion-Werke Kg, 7012 Fellbach Kolbenstangenloser zylinder
DE3504269A1 (de) * 1985-02-08 1986-08-21 ORIGA GmbH Pneumatik, 7024 Filderstadt Druckmittelzylinder
DE3539074A1 (de) * 1985-11-04 1987-05-14 Knorr Bremse Ag Druckmittelgetriebener, kolbenstangenloser arbeitszylinder
JPS62180104A (ja) * 1986-01-31 1987-08-07 Howa Mach Ltd ロツドレスシリンダの定位置停止装置
DE3619473A1 (de) * 1986-06-10 1987-12-17 Knorr Bremse Ag Druckmittelgetriebener, kolbenstangenloser arbeitszylinder
JPH0765602B2 (ja) * 1987-01-30 1995-07-19 豊和工業株式会社 ロツドレスシリンダ
US4785716A (en) * 1987-02-27 1988-11-22 Tol-O-Matic, Inc. Pneumatic cylinder and brake mechanism therefor
DE3709164A1 (de) * 1987-03-20 1988-09-29 Knorr Bremse Ag Bremseinrichtung fuer druckmittelzylinder
SE464534B (sv) * 1987-11-11 1991-05-06 Bo Granbom Bromsanordning vid en anordning foer linjaer roerelse
IT1217812B (it) * 1988-06-08 1990-03-30 Univers S P A Dispositivo di tenuta per cilindri pneumatici senz,asta
DE3822103A1 (de) * 1988-06-30 1990-02-08 Winkler Duennebier Kg Masch Vorrichtung zum verschieben von teilen
EP0385188A1 (fr) * 1989-02-28 1990-09-05 Hygrama Ag Vérin à fluide sous pression
US4998459A (en) * 1989-09-22 1991-03-12 Blatt John A Rodless fluid actuated motor with improved sealing characteristics
DE69100636T2 (de) * 1990-02-09 1994-05-26 Bo Kungsoer Granbom Bremsvorrichtung in einer gradlinigen Bewegungsvorrichtung.
SE465787B (sv) * 1990-02-09 1991-10-28 Bo Granbom Fastsaettningsanordning foer fastsaettning av en skena vid en manoevercylinder
IE920673A1 (en) * 1991-03-04 1992-09-09 Ascolectric Ltd Linear drive
US5168792A (en) * 1991-09-30 1992-12-08 Coors Brewing Company Apparatus for mounting a rodless cylinder
US5275088A (en) * 1991-10-11 1994-01-04 Smc Kabushiki Kaisha Rodless cylinder
JP2512356B2 (ja) * 1991-11-01 1996-07-03 エスエムシー株式会社 ロッドレスシリンダ
JP2512354B2 (ja) * 1991-10-14 1996-07-03 エスエムシー株式会社 ロッドレスシリンダ
JP2575245B2 (ja) * 1991-11-01 1997-01-22 エスエムシー株式会社 ロッドレスシリンダ
DE69219278T2 (de) * 1991-11-11 1997-12-18 Smc K.K., Tokio/Tokyo Kolbenstangenloser Arbeitszylinder
DE69300855T2 (de) * 1992-07-21 1996-11-07 Smc K.K., Tokio/Tokyo Kolbenstangenloser Zylinder.
DE4400454C2 (de) * 1994-01-11 1996-11-07 Invest Tech Ag Kolbenstangenloser Linearantrieb
DE4400453C2 (de) * 1994-01-11 1996-11-07 Maschimpex Handels & Consulting Ag Linearantrieb
US6336393B1 (en) 1998-07-01 2002-01-08 Parker-Hannifin Corporation Rodless pneumatic cylinder

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE707679C (de) * 1935-02-05 1941-06-30 Francesco Merz Zylinder fuer eine kolbenbetaetigte Beschleunigungsvorrichtung, insbesondere Flugzugschleuder
FR1034290A (fr) * 1950-03-28 1953-07-21 Frein et embrayage actionnés par l'eau ou l'air comprimés
DE1187867B (de) * 1956-11-14 1965-02-25 Rockwell Federn Und Achsen A G Aussenbackenbremse
DE1475809A1 (de) * 1964-09-04 1969-03-13 Hermann Rasper Vorrichtung zum Versetzen eines ein Aggregat tragenden Kolbens in jede gewuenschte Lage an einem rohrfoermigen Zylinder entlang
DE1675119A1 (de) * 1968-03-08 1970-12-10 Bbc Brown Boveri & Cie Brems-und Haltevorrichtung
DE2404244A1 (de) * 1974-01-30 1975-08-07 Ahrendt & Birkendahl Ohg Kolbenstangenloser arbeitszylinder
DE2945133C2 (de) * 1979-11-08 1983-09-01 Robert Bosch Gmbh, 7000 Stuttgart Bremseinrichtung für fluidgetriebene, kolbenstangenlose Arbeitszylinder
DE3124915C2 (de) * 1981-06-25 1984-10-31 Kaiser, Siegmund H., Ing.(grad.), 7440 Nürtingen Druckmittelzylinder mit einem längsgeschlitzten endseitig verschlossenen Zylinderrohr

Also Published As

Publication number Publication date
EP0104364A1 (fr) 1984-04-04
DE3374707D1 (en) 1988-01-07
EP0177850B1 (fr) 1987-11-25
DE3363754D1 (en) 1986-07-03
EP0177850A1 (fr) 1986-04-16

Similar Documents

Publication Publication Date Title
EP0104364B1 (fr) Vérin sans tige de piston avec frein
EP0069199B1 (fr) Vérin à fluide
DD236370A5 (de) Kolbenstangenloser zylinder
DE3403830A1 (de) Fluidgetriebener kolbenstangenloser arbeitszylinder
DE8906987U1 (de) Dichtungsvorrichtung für triebstangenfreie pneumatische Zylinder
DE4023946C2 (de) Kolbendichtungsanordnung
EP0141405B1 (fr) Cylindre à fluide de pression
DE3811225A1 (de) Hydraulische stuetzvorrichtung
DE3911427C2 (fr)
EP1182359B1 (fr) Actionneur linéaire sans tige et son carter
DE2706163C2 (de) Zylinder mit einem darin beweglichen Kolben
DE3505167C2 (fr)
DE2718414C2 (de) Dichtungsanordnung an einer Walze
DE3229305A1 (de) Bremseinrichtung fuer fluidgetriebene kolbenstangenlose arbeitszylinder
DE2522560C3 (de) Druckmittelbetriebener Stellantrieb mit einem in einem geraden Zylinder hin und her verschiebbaren Arbeitskolben
DD243966A5 (de) Kolbenstangenloser zylinder
EP0621408B1 (fr) Vérin de travail actionné par fluide avec actionneurs intégrés
DE4027636C2 (de) Fluidgetriebener kolbenstangenloser Arbeitszylinder
DE4305891A1 (de) Dichtung für translatorisch bewegte Teile
DE8310794U1 (de) Fluidbetriebener kolbenstangenloser Arbeitszylinder
DE10118534B4 (de) Klemmsystem
DE1032629B (de) Elastischer Dichtungsring fuer zueinander bewegliche Teile
EP0519185A1 (fr) Vérin commandé par un fluide sous pression
DE10119358C2 (de) Druckmittelzylinder und Montagevorrichtung zu seiner Herstellung
DE3137141C2 (de) Arbeitszylinder

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT CH DE FR GB IT LI SE

17P Request for examination filed

Effective date: 19840509

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

ITF It: translation for a ep patent filed

Owner name: BARZANO' E ZANARDO ROMA S.P.A.

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT CH DE FR GB IT LI SE

REF Corresponds to:

Ref document number: 20123

Country of ref document: AT

Date of ref document: 19860615

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3363754

Country of ref document: DE

Date of ref document: 19860703

ET Fr: translation filed
RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: KNORR-BREMSE AG

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19920605

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19920609

Year of fee payment: 10

Ref country code: FR

Payment date: 19920609

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19920612

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19920720

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19920804

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19930801

Ref country code: AT

Effective date: 19930801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19930802

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19930831

Ref country code: CH

Effective date: 19930831

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19930801

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19940429

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19940503

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

EUG Se: european patent has lapsed

Ref document number: 83107549.4

Effective date: 19940310