EP0602417B1 - Vérin de travail sans tige - Google Patents

Vérin de travail sans tige 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
Authority
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
Other languages
German (de)
English (en)
Other versions
EP0602417A1 (fr
Inventor
Gunther Dipl.-Ing. Strobel (Fh)
Manfred Moeck
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0602417A1 publication Critical patent/EP0602417A1/fr
Application granted granted Critical
Publication of EP0602417B1 publication Critical patent/EP0602417B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F15B15/20—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.

Landscapes

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

Claims (12)

  1. Vérin de travail sans tige, dont le piston sollicité par une pression entraîne une prise d'énergie (11, 11A) et qui comporte un système de freinage (14, 14A), qui freine, en mettant sous pression ou en déchargeant de pression un élément de freinage, la prise d'énergie afin de la positionner, le système de freinage (14, 14A) étant disposé sur la prise d'énergie (11, 11A),
    caractérisé en ce que
    le système de freinage (14, 14A) présente plusieurs pistons (19, 33) disposés dans des alésages (15 à 18, 31), dont les axes s'étendent perpendiculairement aux surfaces de freinage sur la paroi du boîtier (25) du vérin de travail et en ce qu'
    un plateau de freinage (23, 23A), séparé du piston à pression (19, 33) et guidé de façon particulière, est associé à au moins un tel piston (19, 33).
  2. Vérin de travail selon la revendication 1,
    caractérisé en ce que
    les pistons à pression (19) sont comprimés contre le plateau de freinage (23) en les alimentant au moyen d'un agent sous pression.
  3. Vérin de travail selon la revendication 1,
    caractérisé en ce que
    les pistons à pression (33) sont comprimés dans le sens du freinage par un ressort, en particulier un ressort à disques (43) et dans le sens de la purge par la pression d'un agent sous pression.
  4. Vérin de travail selon l'une des revendications 1 à 4,
    caractérisé en ce que
    les alésages (15 à 18, 31), qui reçoivent les pistons à pression, sont disposés dans une partie séparée (13, 14) du boîtier, qui est fixée sur la prise d'énergie (11).
  5. Vérin de travail selon les revendications 1, 3 et 4,
    caractérisé en ce que
    dans l'alésage (31) sont disposés deux pistons (32, 33), entre lesquels se trouve la chambre de pression (40) alimentée en agent sous pression,
    en ce que
    les deux pistons présentent un alésage central en alignement (34, 35), à travers lequel passe une tige filetée, et en ce que
    la face frontale libre de la tige filetée vient en contact avec le plateau (23A) et la tige filetée est guidée dans l'autre piston extérieur (33) dans un filetage et peut être fixée à l'aide d'un écrou (37).
  6. Vérin de travail selon l'une des revendications 1 à 5,
    caractérisé en ce qu'
    un plateau de freinage particulier (23, 23A) est associé à chaque piston à pression (19, 33).
  7. Vérin de travail selon l'une des revendications 1 à 6,
    caractérisé en ce que
    les parties du boîtier (12, 13) du système de freinage (14, 14A) sont disposées de façon symétrique par rapport à la prise d'énergie (11, 11A), de telle sorte que les pistons à pression se trouvent des deux côtés sensiblement en face l'un de l'autre
  8. Vérin de travail selon la revendication 7,
    caractérisé en ce qu'
    il présente un guidage (11C) séparé du piston de travail (11B) et
    en ce que
    le guidage (11C) et les axes des pistons à pression (19, 33) se trouvent sensiblement dans le même plan.
  9. Vérin de travail selon une ou plusieurs des revendications 1 à 8,
    caractérisé en ce que
    plusieurs alésages (15 à 18) avec des pistons à pression (19, 33) sont disposés sur un côté du système de freinage (14, 14A), pistons à pression qui en particulier sont de la même taille.
  10. Vérin de travail selon une ou plusieurs des revendications 1, 2, 4, 6 à 9,
    caractérisé en ce que
    les pistons à pression (19, 33) sont respectivement constitués sous la forme de plateaux circulaires, sur le bord extérieur desquels est disposé une bague d'étanchéité (20).
  11. Vérin de travail selon la revendication 10,
    caractérisé en ce qu'
    un plateau de freinage commun (23) est associé à plusieurs pistons à pression (19).
  12. Vérin de travail selon une ou plusieurs des revendications 4, 6 à 11,
    caractérisé en ce que
    la partie du boîtier (12, 13) présente un renfoncement ouvert d'un côté, qui présente à l'intérieur des alésages en forme de trous borgnes (15 à 18), qui guident les pistons à pression (19), renfoncement qui se transforme vers l'extérieur en un évidement (22) guidant le plateau de freinage (23).
EP93118855A 1992-12-18 1993-11-24 Vérin de travail sans tige Expired - Lifetime EP0602417B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4242971 1992-12-18
DE4242971A DE4242971A1 (de) 1992-12-18 1992-12-18 Kolbenstangenloser Arbeitszylinder

Publications (2)

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

Family

ID=6475772

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93118855A Expired - Lifetime EP0602417B1 (fr) 1992-12-18 1993-11-24 Vérin de travail sans tige

Country Status (2)

Country Link
EP (1) EP0602417B1 (fr)
DE (2) DE4242971A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3434369B2 (ja) * 1994-11-14 2003-08-04 Ｓｍｃ株式会社 ロッドレスシリンダ
DE19540502A1 (de) * 1995-10-31 1997-05-07 Festo Kg Fluidbetätiger kolbenstangenloser Linearantrieb

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3403830A1 (de) * 1983-04-12 1984-10-18 Knorr-Bremse GmbH, 8000 München Fluidgetriebener kolbenstangenloser arbeitszylinder
DE3514074A1 (de) * 1985-04-18 1986-10-23 Herion-Werke Kg, 7012 Fellbach Kolbenstangenloser zylinder
SE464534B (sv) * 1987-11-11 1991-05-06 Bo Granbom Bromsanordning vid en anordning foer linjaer roerelse

Also Published As

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

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