EP0104364A1 - Vérin sans tige de piston avec frein - Google Patents

Vérin sans tige de piston avec frein Download PDF

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Publication number
EP0104364A1
EP0104364A1 EP83107549A EP83107549A EP0104364A1 EP 0104364 A1 EP0104364 A1 EP 0104364A1 EP 83107549 A EP83107549 A EP 83107549A EP 83107549 A EP83107549 A EP 83107549A EP 0104364 A1 EP0104364 A1 EP 0104364A1
Authority
EP
European Patent Office
Prior art keywords
working cylinder
guide space
cylinder according
housing
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.)
Granted
Application number
EP83107549A
Other languages
German (de)
English (en)
Other versions
EP0104364B1 (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 AT85112239T priority Critical patent/ATE31108T1/de
Priority to DE8585112239T priority patent/DE3374707D1/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

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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 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, which can be magnetically or mechanically connected to the piston.
  • the mechanical connection takes place via a circumferential transmission element, in particular a band, 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.
  • the power take-off also comprises the cylinder tube concentrically.
  • the known braking device can then be designed as a bellows, which is fixed to the cylindrical inner wall of the power take-off comprising play and which concentrically surrounds the cylinder tube. By The bellows is expanded when a fluid is supplied, the brake linings coming to rest on the cylindrical outer circumference of the cylinder tube for braking or stopping the force transducer moved by the piston.
  • the known rodless cylinder must be provided to prevent rotation of the cylinder tube concentrically comprising the power consumer with an outer casing, which is held on the cylinder tube ends and on the profiled inner surfaces of the force transducer in the longitudinal direction of the cylinder tube is rotatably displaceable.
  • the object of the invention is to provide an improved rodless cylinder of the type mentioned, which takes up only a small space with largely simplified manufacture and assembly and in particular still has a relatively small diameter when the braking device is integrated in the power consumer.
  • FIGS. 1 to 6 and 8 are band or rope cylinders.
  • FIG. 7 ' is a slit work cylinder that works with a masking tape. It is clear that the exemplary embodiments according to FIGS. 1 to 4 can be provided with a cylinder wall opening corresponding to FIG. 7.
  • 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 protrude above the cylinder tube and whose inwardly directed sections 2 1 and 3 1 have a shaft-like guide space 4 with a rectangular cross-section that extends over the length of the cylinder tube 1 limit, which is open to the outside via a central guide gap 5 running in the axial direction of the cylinder tube between the mutually opposite end faces at the free ends of the sections 2 'and 3'.
  • 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 force consumer 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. Neither the band nor the piston are shown in Figure 1.
  • 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 edge engages with its one end on 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 in order to with its: others Attack the end on the opposite other side of the piston.
  • Such a division and guidance of the band between a power take-off and the piston of a band cylinder is e.g. made known by DE-OS 29 45 133.
  • the band cylinder It is also part of the state of the art of the band cylinder not to clamp the ends of the two sections of the two-part band on the slide and on the piston, but rather to allow them to engage in an articulated manner.
  • the required belt tension can be applied solely from the belt or partially from the belt and by additional springs which act on the reinforced belt ends on the power take-off and / or on the piston.
  • a turnbuckle-like device in the power take-off, to which the band ends are connected in an articulated manner and with which the degree of tension of the band in relation to the spring tension can be adjusted.
  • 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 can be integrated into the sled-like body 6.
  • the sled-like body 6 is double T-shaped in cross section.
  • recesses 9 and 10 with a rectangular cross-section are formed on the two long sides of the sled-like body-6, in which brake bodies 11 and 12 are slidably guided, which have brake linings 13 and 14 on their outer end faces, the inner surface sections 15 and 16 the profile parts 2 and 3 on the longitudinal side of the cylinder tube 1 are opposite.
  • 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 9.
  • 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.
  • Pressure medium source via the bore 27, 25 and 26, the pressure bodies 11 and 12 with their friction linings 13 and 14 are pressed against the surface-mounted surface sections 15 and 16, in order to slow down the movement of the force transducer 8 and / or to hold or hold the force transducer 8 in a specific position to position.
  • 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 slide-like part 6 of the power take-off 8, which e.g. can 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 FIG. 1. 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 one 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 integral with the cylinder tube or can belong to housing parts that are held on the cylinder barrel.
  • first profile surfaces (identified, inter alia, by the reference number 28) for the rotationally secure guidance of the force transducer 8 and 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 housing-fixed profile surfaces 15 and 16 can be selected regardless of the diameter of the cylinder tube in terms of their area size and shape so that optimal braking and positioning of the force transducer 8 is possible, with the frictional influences of the braking device in the released state on the easy 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 force transducer 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 profile sections 2 and 3 delimiting the shaft-shaped guide space 4 are, in the example, integral with the cylinder tube 1. It is of course clear that the profile - sections 2 and 3 can also belong to a profile body connected to the cylinder tube 1.
  • the wedge-shaped braking device can be advantageous compared to the braking device according to FIG. 1, since the available braking surface is enlarged and the wedge effect can be used for braking depending on the wedge angle selected. 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.
  • FIG. 3 shows a further embodiment of a brake cylinder according to the invention, in which the power take-off 8 comprises a cylinder tube 1 designed as an octagonal tube.
  • the power consumer is supported by four wheels or rollers 31-34 on diametrically opposite surfaces of the octagonal cylinder tube 1.
  • a pressure body 36 is displaceable in the upper part of the power take-off 8 in which a pressure body 36 is displaceable.
  • the pressure body 36 has wedge surfaces drawn inwards on its front side for carrying a wedge-shaped brake lining 37.
  • a pressure pad-like sealing element 38 is provided on the back of the pressure body 36, which is designed in accordance with one of the sealing elements 19, 20 in FIG. 1.
  • the profile surface 28 of the cylinder tube 1 between two adjacent profile surfaces / which serve as guide surfaces for the power consumer carries an angled profile plate 39 which forms wedge-shaped contact surfaces for the wedge-shaped brake pads.
  • the flat profile surface 28 itself can serve as a contact surface for the braking device if a wedge-shaped braking device is dispensed with.
  • the profiled sheet 39 can be an integral part of the profiled tube 1, which is then two Has profile surfaces, which serve on the one hand for the rotationally secure guidance of the power consumer 8, and on the other hand serve as a system for the braking device 36-38 integrated in the power consumer 8.
  • the power take-up comprises the cylinder tube in the example, the special shape of the cylinder tube allows the power take-off to be rotated so that special devices for securing the power take-off against rotation are no longer required.
  • the power take-off according to FIG. 3 can also be designed symmetrically, so that the part of the power take-off diametrically opposite the part of the power take-off with the braking device 35-38 can then have a similar braking device, the two braking devices being opposite each other during braking Act.
  • the pressure medium source (not shown) for actuating one or more braking devices is connected to the pressure-tight space 35 or spaces 35 via at least one flexible hose (not shown) and connection bores (also not shown).
  • the guide rollers or guide wheels 31-34 can also be replaced by sliding bands or sliding coverings which are attached to the profile surfaces of the cylinder tube or correspondingly to the power consumer. It is also clear that the power take-off 8 does not necessarily have to be guided by means of four guide wheels or guide rollers or along four sliding belts. In a similar construction, three guide rollers or slideways, which are offset by 120 ° to each other, can be sufficient.
  • the embodiment of the invention according to FIG. 4 is similar to that according to FIG. 3. The main difference is that the cylinder tube 1 has a wedge-shaped profile part 40 has, which is placed on the cylinder tube 1 or forms a unit with this.
  • the wedge-shaped profile part 40 has such a shape that the wedge-shaped inward-facing inner surfaces of the profile part 40 serve as contact surfaces of a wedge-shaped braking device 35-38 which, in contrast to the embodiment according to FIG are correspondingly directed outwards in a wedge shape.
  • the outer counter surfaces 41 and 42 on the profile part 40 serve as non-rotatable guide surfaces for the force transducer 8, which is displaceably guided on the counter surfaces 41 and 42 with rollers or sliding surfaces.
  • Two corresponding rollers and / or wheels 43 and 44 are shown in dashed lines in FIG.
  • the force collector 8 according to FIG. 4 is guided by means of two rollers or wheels or by means of two slideways.
  • the power take-off 8 comprises the cylindrical outer surface of the cylinder tube. Thanks to the profile part 40 on the cylinder tube, a braking device 35-38 integrated in the power consumer can be provided, which does not concentrically encompass the cylinder tube.
  • FIG. 5 shows a cross section through a working cylinder similar to that according to FIGS. 1 and 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 in FIG. 6 5 enlarged as a detail partially broken away and shown in section.
  • the one rope ends of the rope sections, not shown, are held, each of which is connected to one side of the piston from one side of the arm via a roller at one end of the working cylinder.
  • a cover band (not shown in FIG. 5) 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 50 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 slide-like body 6 shown as a whole in FIG. 6 is particularly adapted with its two ends 54 and 55 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 sled-like body 6 has on both sides Similar recesses 56 and 57, 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 via the bores 60 and 61 to the tube 52 and the channels 50 to the pressure medium connection 51.
  • 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 holders 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 tube ends of 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.
  • the membranes 64 and 65 there are 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 can be pressed against the inner walls of the guide space 4 in order to hold the slide-like body 6 and thus the force transducer 8 in a desired position on the brake cylinder or to brake the piston movement. Thanks to the movable mounting of the membrane holders 58 and 59 at the ends of the tube 52, these are pressed into the correct position when pressure is applied.
  • the horizontal width extension of the guide space in FIG. 5 is advantageously somewhat larger than the diameter of the cylinder cavity 73 for the cylindrical piston shown cut into its central section.
  • the width / height ratio of the guide space 4 is advantageously greater than 2: 1, preferably about 3: 1.
  • the mean length of the cross section being greater than the mean width, the length / width ratio is advantageously greater than 2: 1, preferably about 3: 1.
  • FIG. 7 shows a cross section through a working cylinder according to the invention corresponding to FIG. 5.
  • the section lies here in a plane in the area of one end 54 or 55 of the slide-like body 6, that is to say outside the braking device.
  • Fig. 7 differs from Fig. 5 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 to be connected to the power take-off 8 in the cylinder cavity.
  • a cover band 76 is provided which engages in a groove 77 to cover the gap 75, the inside of which adjoins 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 embodiment according to FIG. 7 therefore does not hit a rope or band cylinder, but rather a rodless cylinder with a slotted cylinder housing, the piston being rigidly connected to the force pickup in the guide space 4 with one arm.
  • the cover band is located in a manner known per se in front of and behind the piston in its sealing position and is only lifted out of its sealing position in the immediate area of the piston.
  • 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 is clear from FIGS. 5 and 7 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 be manufactured, for example, from aluminum in the extrusion process.
  • the outer contours to choose different from the cross sections shown in Figures 5 and 7, in such a manner 5 that are obtained over the circumference about substantially the same wall thicknesses.
  • FIG 8 shows yet another cross section through a working cylinder according to the invention, in which a cylindrical tube 80 for receiving the piston, not shown, is connected via a connecting web 81 which extends over the length 80 to a frame-like body 82 which has the guide space 4 in its interior forms for 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 80 and has a slot 83 through which the connecting web 81 engages.
  • a driver 7 engages in the sled-like body 6 and, together with the sled-like body 6, forms the force transducer 8.
  • the driver 7 protrudes through a slot-like opening 5 of the frame-like body 82.
  • the driver 7 can be designed in accordance with the drivers in FIGS. 5 and 7.
  • the masking tape for the opening 5 is designated 84 as in FIG. 7.
  • 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. 5, 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. 5, channels which ensure the influence of pressure medium 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 80.
  • the topping also consists of two half-shell halves can be set, each extending from the neck 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 80 can have a slot 74 according to FIG. 7, which can be sealed with a cover tape 76 according to FIG. 7.
  • the profile according to the invention shown in FIG. 8 with an internal cylindrical tube 80 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 for a band or rope cylinder as well also be suitable for a so-called slotted cylinder.
  • the ; 8 can be produced according to the profile according to Figures 5 and 7 from aluminum in the extrusion process.
  • the frame-like body 82 for forming the guide space 4 can also have a different cross section than that shown in FIG. 8. In particular, it does not need to have a rectangular inner and / or outer border.
  • the invention shows the designer basic ways, profiles for a rodless cylinder Specify that can be made from aluminum in the extrusion process and require a low overall height. It is clear that the invention is not restricted to rodless working cylinders which integrate a braking device in a carriage-like body of the power consumer to have.
  • the explanations according to FIGS. 5 to 8 show basic solutions that can be designed with or without a braking device. Without a braking device, the carriage-like body according to FIGS. 5 to 7 can be made axially shorter and, if appropriate, also flatter.
  • the masking tape 84 serves to protect the slot 5 from contamination, which means that 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Braking Arrangements (AREA)
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
AT85112239T ATE31108T1 (de) 1982-08-05 1983-08-01 Fluidgetriebener kolbenstangenloser arbeitszylinder.
DE8585112239T DE3374707D1 (en) 1982-08-05 1983-08-01 Rodless hydraulic ram
AT83107549T ATE20123T1 (de) 1982-08-05 1983-08-01 Kolbenstangenloser arbeitszylinder mit bremsvorrichtung.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3229305 1982-08-05
DE19823229305 DE3229305A1 (de) 1982-08-05 1982-08-05 Bremseinrichtung fuer fluidgetriebene kolbenstangenlose arbeitszylinder
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 true EP0104364A1 (fr) 1984-04-04
EP0104364B1 EP0104364B1 (fr) 1986-05-28

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Family Applications (2)

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

Family Applications After (1)

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

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EP (2) EP0104364B1 (fr)
DE (2) DE3363754D1 (fr)

Cited By (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2568955A1 (fr) * 1984-08-13 1986-02-14 Herion Werke Kg Verin a piston sans tige
EP0190760A1 (fr) * 1985-02-08 1986-08-13 ORIGA GmbH Pneumatik Vérin à fluide
EP0221517A1 (fr) * 1985-11-04 1987-05-13 Knorr-Bremse Ag Servomoteur sans tige de piston actionné par fluide
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
EP0135041B1 (fr) * 1983-08-10 1988-06-08 Robert Bosch Gmbh Cylindre actionneur sans tige
EP0280309A1 (fr) * 1987-02-27 1988-08-31 Tol-O-Matic, Inc. Cylindre pneumatique et son mécanisme de blocage
DE3709164A1 (de) * 1987-03-20 1988-09-29 Knorr Bremse Ag Bremseinrichtung fuer druckmittelzylinder
US4856415A (en) * 1987-01-30 1989-08-15 Howa Machinery, Ltd. Rodless cylinder assembly
DE3822103A1 (de) * 1988-06-30 1990-02-08 Winkler Duennebier Kg Masch Vorrichtung zum verschieben von teilen
US4926982A (en) * 1987-11-11 1990-05-22 Bo Granbom Braking device in an arrangement for linear movement
EP0385188A1 (fr) * 1989-02-28 1990-09-05 Hygrama Ag Vérin à fluide sous pression
US4991494A (en) * 1988-06-08 1991-02-12 Univer S.P.A. Sealing device for rodless pneumatic cylinders
US4998459A (en) * 1989-09-22 1991-03-12 Blatt John A Rodless fluid actuated motor with improved sealing characteristics
EP0447379A1 (fr) * 1990-02-09 1991-09-18 Bo Granbom Dispositif de freinage dans un organe à mouvement rectiligne
US5138935A (en) * 1990-02-09 1992-08-18 Hygrama Ag Arrangement for attaching a rail to a piston-cylinder type control device
EP0502810A1 (fr) * 1991-03-04 1992-09-09 Ascolectric Limited Moteur linéaire avec vérin à piston sans tige
US5168792A (en) * 1991-09-30 1992-12-08 Coors Brewing Company Apparatus for mounting a rodless cylinder
EP0536799A1 (fr) * 1991-10-11 1993-04-14 Smc Kabushiki Kaisha Vérin sans tige
JPH05106611A (ja) * 1991-10-14 1993-04-27 Smc Corp ロツドレスシリンダ
JPH05126111A (ja) * 1991-11-01 1993-05-21 Smc Corp ロツドレスシリンダ
US5279207A (en) * 1991-11-11 1994-01-18 Smc Kabushiki Kaisha Rodless cylinder
US5311810A (en) * 1991-11-01 1994-05-17 Smc Kabushiki Kaisha Rodless cylinder
EP0662566A1 (fr) * 1994-01-11 1995-07-12 Maschimpex Handels- und Consulting AG Entraînement linéaire
EP0662567A2 (fr) * 1994-01-11 1995-07-12 Invest Tech AG Actionneur linéaire sans tige
US6336393B1 (en) 1998-07-01 2002-01-08 Parker-Hannifin Corporation Rodless pneumatic cylinder

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5333535A (en) * 1992-07-21 1994-08-02 Smc Kabushiki Kaisha Rodless cylinder

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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
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EP0029188A2 (fr) * 1979-11-08 1981-05-27 Robert Bosch Gmbh Dispositif de freinage pour vérins sans tige de piston

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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
DE2404244A1 (de) * 1974-01-30 1975-08-07 Ahrendt & Birkendahl Ohg Kolbenstangenloser arbeitszylinder
EP0029188A2 (fr) * 1979-11-08 1981-05-27 Robert Bosch Gmbh Dispositif de freinage pour vérins sans tige de piston

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Cited By (32)

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Publication number Priority date Publication date Assignee Title
EP0135041B1 (fr) * 1983-08-10 1988-06-08 Robert Bosch Gmbh Cylindre actionneur sans tige
FR2568955A1 (fr) * 1984-08-13 1986-02-14 Herion Werke Kg Verin a piston sans tige
EP0190760A1 (fr) * 1985-02-08 1986-08-13 ORIGA GmbH Pneumatik Vérin à fluide
EP0221517A1 (fr) * 1985-11-04 1987-05-13 Knorr-Bremse Ag Servomoteur sans tige de piston actionné par fluide
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
US4856415A (en) * 1987-01-30 1989-08-15 Howa Machinery, Ltd. Rodless cylinder assembly
EP0280309A1 (fr) * 1987-02-27 1988-08-31 Tol-O-Matic, Inc. Cylindre pneumatique et son mécanisme de blocage
DE3709164A1 (de) * 1987-03-20 1988-09-29 Knorr Bremse Ag Bremseinrichtung fuer druckmittelzylinder
EP0283694B1 (fr) * 1987-03-20 1989-07-26 Knorr-Bremse Ag Dispositif de verrouillage pour vérin à fluide
EP0370157B1 (fr) * 1987-11-11 1992-07-29 Bo Granbom Dispositif de freinage dans un organe à mouvement rectiligne
US4926982A (en) * 1987-11-11 1990-05-22 Bo Granbom Braking device in an arrangement for linear movement
US4991494A (en) * 1988-06-08 1991-02-12 Univer S.P.A. Sealing device for rodless pneumatic cylinders
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
EP0447379A1 (fr) * 1990-02-09 1991-09-18 Bo Granbom Dispositif de freinage dans un organe à mouvement rectiligne
US5138935A (en) * 1990-02-09 1992-08-18 Hygrama Ag Arrangement for attaching a rail to a piston-cylinder type control device
EP0502810A1 (fr) * 1991-03-04 1992-09-09 Ascolectric Limited Moteur linéaire avec vérin à piston sans tige
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
EP0536799A1 (fr) * 1991-10-11 1993-04-14 Smc Kabushiki Kaisha Vérin sans tige
JPH05106611A (ja) * 1991-10-14 1993-04-27 Smc Corp ロツドレスシリンダ
JPH05126111A (ja) * 1991-11-01 1993-05-21 Smc Corp ロツドレスシリンダ
US5311810A (en) * 1991-11-01 1994-05-17 Smc Kabushiki Kaisha Rodless cylinder
US5279207A (en) * 1991-11-11 1994-01-18 Smc Kabushiki Kaisha Rodless cylinder
EP0662566A1 (fr) * 1994-01-11 1995-07-12 Maschimpex Handels- und Consulting AG Entraînement linéaire
EP0662567A2 (fr) * 1994-01-11 1995-07-12 Invest Tech AG Actionneur linéaire sans tige
US5467686A (en) * 1994-01-11 1995-11-21 Invest Tech Ag Linear drive without a piston rod
US5517901A (en) * 1994-01-11 1996-05-21 Machimpex Handels- Und Consulting Ag Linear drive having profile elements provided on flanks in a longitudinal slot of a guide tube
EP0662567A3 (fr) * 1994-01-11 1997-07-09 Invest Tech Ag Actionneur linéaire sans tige.
US6336393B1 (en) 1998-07-01 2002-01-08 Parker-Hannifin Corporation Rodless pneumatic cylinder

Also Published As

Publication number Publication date
EP0177850A1 (fr) 1986-04-16
DE3374707D1 (en) 1988-01-07
DE3363754D1 (en) 1986-07-03
EP0177850B1 (fr) 1987-11-25
EP0104364B1 (fr) 1986-05-28

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