EP0346716B1 - Vérin à tige de piston immobilisée en rotation - Google Patents

Vérin à tige de piston immobilisée en rotation Download PDF

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Publication number
EP0346716B1
EP0346716B1 EP89110115A EP89110115A EP0346716B1 EP 0346716 B1 EP0346716 B1 EP 0346716B1 EP 89110115 A EP89110115 A EP 89110115A EP 89110115 A EP89110115 A EP 89110115A EP 0346716 B1 EP0346716 B1 EP 0346716B1
Authority
EP
European Patent Office
Prior art keywords
piston rod
piston
longitudinal
ball
bearing member
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
EP89110115A
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German (de)
English (en)
Other versions
EP0346716A1 (fr
Inventor
Peter Dipl.-Ing. Epp
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.)
Expert Maschinenbau GmbH
Original Assignee
Expert Maschinenbau 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 Expert Maschinenbau GmbH filed Critical Expert Maschinenbau GmbH
Priority to AT89110115T priority Critical patent/ATE80206T1/de
Publication of EP0346716A1 publication Critical patent/EP0346716A1/fr
Application granted granted Critical
Publication of EP0346716B1 publication Critical patent/EP0346716B1/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
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1414—Characterised by the construction of the motor unit of the straight-cylinder type with non-rotatable piston

Definitions

  • the invention relates to a piston-cylinder unit that can be pressurized with pressure, with a piston rod which, at least in the length range which seals the associated cylinder cover by a seal against the escape of pressure medium, has a cross-section deviating from a circular cross-section, through which a piston-connected piston rod passes
  • Bearing component is assigned, which guides the piston rod in a longitudinally displaceable manner, the piston rod in the area passing through the associated cylinder cover being formed over the largest part of the circumference by surface sections of circular cross section with the same circular radius, which are interrupted at equal angular intervals by sections forming longitudinal raceways , and on the cylinder cover the bearing component penetrated by the piston rod is fastened, which in turn is in alignment with the longitudinally running ball raceways points, and in the space between the outer surface of the piston rod and the inner surface of the bearing component rows of bearing balls rolling on the ball raceways of the piston rod on the one hand and the ball raceways of the bearing component on the other are arranged, and wherein in the cylinder cover in
  • the piston rod of piston-cylinder units that can be pressurized with pressure medium that is to say pneumatics or hydraulic cylinders, generally have a cylindrical shape, at least in the length section penetrating the associated cylinder cover during the working stroke, which has the seal of the between the piston rod and the Passage opening in the cylinder cover required gap against pressure loss and leakage of the pressure medium by means of conventional ring seals - be it O-rings or lip seals. Due to the cylindrical shape of the piston rod, the end of the piston rod emerging from the cylinder is not secured against rotation, especially since the cylinder firmly connected to the piston rod has a concentric circular boundary, which is also not secured against rotation in the circumferential direction within the cylinder.
  • piston-cylinder units are used in constructions in which they have to advance and retract components which have to be held during the stroke in an orientation which is exactly secured against rotation relative to the longitudinal central axis of the piston-cylinder unit, additional guides must be provided , which secure the piston rod against rotation. Regardless of whether there are guides provided in series or parallel to the piston rod and connected to it, the overall length or width of the piston-cylinder unit increases considerably. In addition, the structure of the piston-cylinder unit becomes more complex and the number of required components and the effort for their processing and assembly increases significantly compared to a simple piston-cylinder unit which is not secured against rotation.
  • the invention has for its object to provide a piston-cylinder unit in which an external dimension of the piston-cylinder unit which at most slightly increases, and which protects the piston rod against rotation, is integrated, the anti-rotation device ensuring no sluggishness or loss of compressed air.
  • the bearing component is arranged in a rotationally fixed manner on the outside of the cylinder cover facing away from the piston, that the ball raceways are shaped in a circular concave cross section, and that the sealing ring is arranged in the connecting region between the cylinder cover (18) and the bearing component (46) and as Lip sealing ring is formed, the sealing lips are directed inside the piston-cylinder unit.
  • the piston rod is fundamentally similar to a longitudinally displaceable shaft that is secured against rotation by a linear movement bearing with ball guides, but the problem of sealing the piston rod, which does not occur with such shafts, against the pressure built up by the pressure medium inside the piston-cylinder unit by means of a special lip Sealing ring with the cross-sectional shape of the piston rod adapted passage opening is released.
  • the piston rod is provided with a number of equally spaced, radially protruding longitudinal wedges running in the working stroke direction, which are each provided with the ball raceways on both sides in the transition area to the adjoining, cross-sectionally circular surface section, the bearing component being in alignment to the longitudinal wedges is provided with longitudinal grooves in which the ball raceways of the bearing component are provided.
  • This configuration with a linear motion bearing that has become known as the "Ball Spline" appropriate anti-rotation lock has proven itself.
  • the configuration can also be such that the piston rod is provided with a number of equally spaced, radially recessed, longitudinal grooves forming the ball raceways, to which the longitudinal grooves forming the ball raceways are associated with a corresponding angular displacement in the inner surface of the bearing component.
  • This simplified exemplary embodiment is particularly suitable in cases in which there are comparatively small moments acting in the circumferential direction and trying to twist the piston rod.
  • a cage which holds the bearing balls in the bearing component is assigned to the rows of bearing balls rolling on the ball raceways and the rows of bearing balls which are returned in the return longitudinal grooves and which is opposite the ball raceways of the piston rod lying areas each have a slot through which the bearing balls can only partially pass through, while it is closed in the area of the return longitudinal grooves in each case towards the piston rod.
  • the lip sealing ring provided according to the invention is preferably designed such that it has a circularly delimited outer diameter which is larger than the diameter measured over the end face of the longitudinal wedges of the piston rod, and at the edge of which one on the cylindrical inner surface the receiving groove-sealing circumferential elastic sealing lip is provided, and that along the cross-sectional shape of the piston rod complementarily shaped inner passage opening, a further all-round closed and continuously sealing elastic sealing lip is provided on the outer surface of the piston rod, with a circumferential sealing lip between the two pointing in the same direction , pressure chamber open towards the inside of the cylinder is formed, whose radial dimensions measured between the outer and the inner sealing lip in the area assigned to the longitudinal wedges of the piston rod hen are less than in the regions lying between them in the circumferential direction.
  • the lip sealing ring is designed in such a way that it has a circularly limited outer diameter which is larger than the maximum diameter of the piston rod, and at the edge of which one on the cylindrical one
  • the inner surface of the receiving groove is provided with a circumferential elastic sealing lip, and along the inner passage opening which is complementarily shaped in accordance with the cross-sectional shape of the piston rod
  • Another closed all around and continuously on the outer surface of the piston rod sealing elastic sealing lip is provided, whereby a circumferential pressure chamber is formed between the two sealing lips pointing in the same direction, the radial dimensions of which are measured between the outer and the inner sealing lip in the the areas assigned to the longitudinal grooves of the piston rod are larger than in the areas lying between them in the circumferential direction.
  • the piston-cylinder unit shown in FIG. 1, designated in its entirety by 10, is a double-acting pneumatic cylinder with end position damping that can be acted upon with compressed air as the working medium, which corresponds to known pneumatic cylinders of this type in terms of its basic structure, so that its structure is not described in detail to this extent must be, especially since the protection according to the invention against rotation of its piston rod 12 can also be realized in the same way in other types, for example single-acting and undamped pneumatic cylinders, as well as in piston-cylinder units which can be acted upon by a hydraulic fluid as the working medium.
  • the piston-cylinder unit 10 thus has the actual cylinder 20, which is closed at one end by a closed cylinder cover 14 and at the other end by a cylinder cover 18 provided with a circular through-opening 16 in cross section for the piston rod 12.
  • a cylindrical bore 22 of the cylinder is a bore in two size-adjustable working spaces 24, 24 'dividing and on the inner wall delimiting sealing piston 26 slidably mounted.
  • the piston 26, which is assembled from a plurality of parts not described in detail, is penetrated centrally by the reduced-diameter cylindrical inner end 28 of the piston rod 12 and held at the end of the piston rod by a sleeve 30 screwed onto the free end.
  • the piston rod 12 has, in the region 36 adjoining the reduced-diameter cylindrical end section 28 - deviating from the customary circular cross-sectional shape - the cross-section recognizable in FIG 38 radially step forward, forming 40 ball raceways for rows of bearing balls 42 (FIG. 1) in transition regions rounded into the circular cross-sectional wave area, of which one row lies on each side of each longitudinal wedge.
  • each row of balls runs in a longitudinal groove 44 in a surrounding bearing component 46, which is held centered in the cylinder cover 18 and is screwed to the cylinder cover and secured against rotation. This screwing takes place - in the case shown - with fastening screws 48, Only one of which is shown in FIG.
  • FIG. 1 and which at the same time also serve to fasten the piston-cylinder unit 10 as a whole in a through bore 50 in a mounting plate 52 forming part of a larger construction, only one of which is shown in FIG. 1 - dash-dotted hatched - partial area is shown.
  • Fig. 1 the piston rod 12 is shown in the fully retracted position in the piston-cylinder unit 10, in which the working space 24 has its maximum and the working space 24 'its minimum size.
  • the length of the section 36 of the piston rod 12 provided with the longitudinal wedges 38 is selected such that it still extends through the bearing component 46 and at the end on the left in FIG. 1 something emerges from the bearing component 46.
  • a cylindrical piston rod section 54 on which one of the piston rod 12 depending on the loading of the working spaces 24, 24 'with compressed air to be moved back and forth - not shown - component can be assembled from that it is assumed that it must not change its relative rotational position with respect to the longitudinal central axis of the piston-cylinder unit 10 because, for example, it may have projecting pins which have to engage in the corresponding, suitable bores in the fully extended end position of the piston rod 12.
  • the rotation of the piston rod 12 is thus ensured by the rows of balls supporting the longitudinal wedges 38 laterally and supported in turn in the longitudinal grooves 44 in the bearing component 46.
  • the bearing balls 42 roll on the associated raceways of the section 36 and the bearing component 46 and thus also change their position in the longitudinal direction.
  • a suitably designed plastic cage 58 holds the bearing balls 42 in such a way that in the area of the longitudinal grooves 44 they can partially pass through a slot provided there to the ball races on the piston rod section 36 while opposing the deeper return longitudinal grooves 56 the piston rod closes. Even when the piston rod 12 is completely pulled out of the bearing component 46, the bearing balls 42 are thus held back by the cage 58 in the bearing component 46, so that there is no risk of loss of individual bearing balls when dismantling or assembling the piston-cylinder unit 10 42 exists.
  • the anti-rotation device of the piston rod 12 corresponds to the linear motion bearings supplied by the company THK Europe GmbH, Dusseldorf under the name “Ball Spline”, which therefore enable a shaft to be moved centrally in a bearing component and secured against rotation, but none Allow axial sealing against gaseous or liquid pressure medium.
  • the lip seal 60 which is shown separately in FIGS. 3 and 4, is arranged in a circumferential receiving groove 62 (FIGS. 1 and 5) which is cylindrical on the groove base and which is on the one hand in the cylinder cover 18 and on the other hand seals on the outer surface of the piston rod section 36.
  • the lip sealing ring has an outer circular and an inner radial section 64 which is delimited in accordance with the cross-sectional shape of the piston rod section 36 on the side opposite the working space 24 of the piston-cylinder unit by a metallic support disk 66 in the receiving groove.
  • the support disk is held clamped between a radial surface of the cylinder cover 18 and the bearing component 46.
  • a circumferential sealing lip 68 which is attached to the outer circumference of the radial section 64 and points in the direction of the working space 24, rests under prestress on the circumferential or bottom surface of the receiving groove 62 and a sealing lip 70 following the outline shape of the inner boundary rests on the piston rod section 36.
  • the lip sealing ring 60 made of elastomeric plastic thus forms a circumferential pressure chamber 72 open in the direction of the working chamber 24, in which the pressure prevailing in the pressure chamber 24 builds up and additionally presses the sealing lips 68, 70 against the assigned sealing surfaces.
  • the sealing lip 70 is only strongly pressed against the piston rod section 36 when the working space 24 is pressurized with compressed air, i.e. when the piston rod is withdrawn inside the piston-cylinder unit.
  • the relative movement between the section 36 and the sealing lip 70 is then directed in the direction of the free end of the sealing lip, whereby its wear is only relatively small, provided the surface of the piston rod section 36 is designed with sufficient smoothness.
  • FIGS. 6 to 10 show a piston-cylinder unit compared to the piston-cylinder unit described above in connection with FIGS. 1 to 5 10 modified piston-cylinder unit 10 'shown, which, however, only in relation to the - from the circular cross-section - cross-sectional shape of the cylinder cover 18 passing length range of the piston rod 12 and the resulting different arrangement of the ball raceways on the piston rod and a correspondingly changed shape of the lip seal ring differs from the piston-cylinder unit 10.
  • modifications mentioned are described below, while it is sufficient to refer to the previous description of the piston-cylinder unit 10, especially since functionally identical parts of the two exemplary embodiments in the drawing figures 1 to 5 on the one hand and 6 to 10 are otherwise provided with the same reference numerals.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Fluid-Damping Devices (AREA)
  • Apparatus For Radiation Diagnosis (AREA)
  • Compressor (AREA)

Claims (7)

  1. Ensemble à piston et cylindre (10;10′), susceptible d'être sollicité par un fluide sous pression, comportant une tige de piston (12), qui présente, au moins dans la zone longitudinale qui traverse le couvercle de cylindre (18) associé, de façon étanche au moyen d'un joint d'étanchéité empêchant toute sortie de fluide sous pression, une section transversale qui diffère de la section transversale circulaire et à laquelle est associée un élément de construction de palier (18), relié au cylindre (20) et traversé par la tige de piston (12), qui guide la tige de piston (12) dans un déplacement longitudinal, cette dernière étant formée, dans la zone (36;36") qui traverse le couvercle de cylindre (18) associé, sur la plus grande partie de la périphérie, de parties de surface à sections transversales en forme d'arc de cercle de même rayon, interrompues à intervalles angulaires réguliers par des sections qui forment des pistes de roulement à billes (40;39) qui s'étendent en direction longitudinale et l'élément de construction de palier (46) traversé par la tige de piston (12) étant fixé sur le couvercle de cylindre (18)) et présente, de son côté, des pistes de roulement à billes (44) alignées par rapport aux pistes de roulement à billes (40,39) longitudinales, et des séries de billes de palier (42), qui roulent d'une part sur les pistes de roulement à billes (40;39) de la tige de piston et d'autre part sur les pistes de roulement à billes (44) de l'élément de construction de palier (46) et sont disposées dans l'espace intermédiaire existant entre la surface extérieure de la tige de piston (12) et la surface intérieure de l'élément de construction de palier (46), et où une bague d'étanchéité (60) qui présente une ouverture de passage correspondante, complémentaire de la forme de section transversale de la tige de piston (12), est prévue dans le couvercle de cylindre (18), dans une gorge de réception (62) circulaire qui entoure la tige de piston à distance radiale, caractérisé en ce que l'élément de construction de palier (46) est disposé bloqué en rotation sur la face extérieure, éloignée du piston, du couvercle de cylindre (18), que les pistes de roulement à billes (40;39) sont d'une forme concave à section transversale en arc de cercle et que la bague d'étanchéité est disposée dans la zone de liaison entre le couvercle de cylindre (18) et l'élément de construction de palier (46) et réalisée sous forme d'une bague d'étanchéité à lèvres (60), dont les lèvres d'étanchéité (68;70;70′) sont orientées vers l'intérieur de l'ensemble à piston et cylindre (10;10′).
  2. Ensemble à piston et cylindre selon la revendication 1, caractérisé en ce que la tige de piston (12) est pourvue d'un certain nombre de nervures longitudinales (38), distribuées à intervalles angulaires réguliers, qui font saillie radialement et s'étendent dans la direction de la course motrice, pourvues chacune, des deux côtés, dans la zone de transition vers la section de surface à section transversale en forme d'arc de cercle, de pistes de roulement à billes (40), et que l'élément de construction de palier (46) est pourvu de rainures longitudinales, en alignement avec les nervures longitudinales, dans lesquelles sont réalisées les pistes de roulement à billes (44) de l'élément de construction de palier.
  3. Ensemble à piston et cylindre selon la revendication 1, caractérisé en ce que la tige de piston (12) est pourvue d'un certain nombre de rainures longitudinales, distribuées à intervalles angulaires réguliers, creusées radialement, formant les pistes de roulement à billes (39), auxquelles sont associées des rainures longitudinales distribuées, suivant un espacement angulaire correspondant, dans la surface intérieure de l'élément de construction de palier (46) et formant ses pistes de roulement à billes (44).
  4. Ensemble à piston et cylindre selon l'une des revendications 1 à 3, caractérisé en ce que des rainures longitudinales de retour (56) plus profondes, décalées en direction circonférentielle par rapport aux pistes de roulement à billes sont prévues dans la surface intérieure de l'élément de construction de palier (46) et reliées, à leurs deux extrémités, aux extrémités voisines de la piste de roulement à billes (44) chaque fois associée, de sorte que les billes de palier (42) qui arrivent à une extrémité de la piste de roulement à billes correspondante ménagée dans l'élément de construction de palier (46), à l'occasion d'une course effectuée par la tige de piston (12), sont véhiculées dans les rainures longitudinales de retour (56) lors de la progression du mouvement de la tige de piston et retournées, par l'intermédiaire de ces dernières, dans le sens inverse du sens de la course de la tige de piston.
  5. Ensemble à piston et cylindre selon la revendication 4, caractérisé en ce qu'aux séries de billes de palier (42), qui roulent sur les pistes de roulement à billes (40;44;39) et aux séries de billes de palier (42), qui sont ramenées dans les rainures longitudinales de retour (56) est associée une cage (58), qui maintient les billes de palier dans l'élément de construction de palier (46) et présente, dans chaque zone opposée aux pistes de roulement à billes de la tige de piston (12) une fente, à travers laquelle les billes de palier (42) ne peuvent passer que partiellement, tandis qu'elle,est chaque fois fermée, dans la zone des rainures longitudinales de retour (56), vis-à-vis de la tige de piston (12).
  6. Ensemble à piston et cylindre selon la revendication 2, caractérisé en ce que la bague d'étanchéité à lèvres (60) présente un diamètre extérieur circulaire réduit, supérieur au diamètre mesuré sur les surfaces frontales des nervures longitudinales de la tige de piston (12) et sur son bord étant prévue une lèvre d'étanchéité (68) élastique circulaire assurant l'étanchéité de la'surface intérieure cylindrique de la gorge de réception (62), et que, le long de l'ouverture de passage intérieure, à forme correspondante complémentaire de la forme de la section transversale de la tige de piston (12), est prévue une autre lèvre d'étanchéité (70) élastique, fermée sur son pourtour et assurant une étanchéité ininterrompue sur la surface extérieure de la tige de piston, où entre les deux lèvres d'étanchéité (68,70) tournées dans le même sens, est formée une enceinte de pression (72) circulaire, ouverte vers l'intérieur du cylindre, dont les dimensions radiales, mesurées entre les lèvres d'étanchéité extérieure et intérieure (68;70) sont moindres, dans les zones associées aux nervures longitudinales (38) de la tige de 'piston, que celles dans les zones intercalaires en direction circonférentielle.
  7. Ensemble à piston et cylindre selon la revendication 3, caractérisé en ce que la bague d'étanchéité à lèvres (60′) présente un diamètre extérieur circulaire réduit, supérieur au diamètre maximal de la tige de piston (12), et sur son bord étant prévue une lèvre d'étanchéité (68) élastique circulaire assurant l'étanchéité de la surface intérieure cylindrique de la gorge de réception (62), et que, le long de l'ouverture de passage intérieure, à forme correspondante complémentaire de la forme de la section transversale de la tige de piston (12), est prévue une autre lèvre d'étanchéité (70′) élastique, fermée sur son pourtour et assurant une étanchéité ininterrompue sur la surface extérieure de la tige de piston, où entre les deux lèvres d'étanchéité (68,70′) tournées dans le même sens, est formée une enceinte de pression (72) circulaire, ouverte vers l'intérieur du cylindre, dont les dimensions radiales, mesurées entre les lèvres d'étanchéité extérieure et intérieure sont supérieures, dans les zones associées aux gorges longitudinales (39) de la tige de piston (12), à celles dans les zones intercalaires en direction circonférentielle.
EP89110115A 1988-06-15 1989-06-05 Vérin à tige de piston immobilisée en rotation Expired - Lifetime EP0346716B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89110115T ATE80206T1 (de) 1988-06-15 1989-06-05 Kolben-zylinder-einheit mit gegen verdrehung gesicherter kolbenstange.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3820337A DE3820337A1 (de) 1988-06-15 1988-06-15 Kolben-zylinder-einheit mit gegen verdrehung gesicherter kolbenstange
DE3820337 1988-06-15

Publications (2)

Publication Number Publication Date
EP0346716A1 EP0346716A1 (fr) 1989-12-20
EP0346716B1 true EP0346716B1 (fr) 1992-09-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP89110115A Expired - Lifetime EP0346716B1 (fr) 1988-06-15 1989-06-05 Vérin à tige de piston immobilisée en rotation

Country Status (4)

Country Link
EP (1) EP0346716B1 (fr)
AT (1) ATE80206T1 (fr)
DE (3) DE3820337A1 (fr)
ES (1) ES2034502T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29721432U1 (de) * 1997-12-04 1998-02-26 Festo AG & Co, 73734 Esslingen Fluidbetätigter Arbeitszylinder
US5761985A (en) * 1995-11-07 1998-06-09 Festo Kg Fluid power cylinder
EP2199624A1 (fr) 2008-12-17 2010-06-23 Festo AG & Co. KG Actionneur linéaire fluidique avec unité de guidage

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Publication number Priority date Publication date Assignee Title
GB2243873A (en) * 1990-03-22 1991-11-13 Christopher J English Support including an hydraulic ram is for use in continuous casting
DE9212073U1 (de) * 1992-09-08 1992-11-12 Expert Maschinenbau Gmbh, 64653 Lorsch Vorschubeinheit
US5524868A (en) * 1993-08-26 1996-06-11 Templeton, Kenly & Co., Inc. Hydraulic toe jack
DE29507688U1 (de) * 1995-05-10 1995-07-20 Festo Kg, 73734 Esslingen Fluidbetätigter Arbeitszylinder
IT237848Y1 (it) * 1997-08-04 2000-09-29 Waircom M B S S P A Cilindrico pneumatico con albero non rotante
DE29811098U1 (de) 1998-06-20 1998-09-24 Festo AG & Co, 73734 Esslingen Dichtungsring
JP2001295809A (ja) * 2000-04-11 2001-10-26 Smc Corp ガイド付きシリンダ
US7127982B2 (en) 2005-03-04 2006-10-31 Festo Corporation Linear drive with non-rotating piston
CN103438045B (zh) * 2013-08-28 2016-05-04 浙江亿日气动科技有限公司 带阀真空气缸

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FR1171749A (fr) * 1956-04-18 1959-01-29 Bendix Aviat Corp Perfectionnements aux vérins
DE1907689C2 (de) * 1969-02-15 1971-02-18 Otto Neumeister Ein- oder mehrstufiger Hydraulikzylinder mit Verdrehsicherung
DE2521364A1 (de) * 1975-05-14 1976-11-25 Festo Maschf Stoll G Kolben-zylinder-kombination mit einem hin und her bewegbaren und hierbei unverdrehbar gelagerten arbeitskolben
US3994539A (en) * 1975-07-22 1976-11-30 Robomation Corporation Self-contained activated slide apparatus and methods of constructing and utilizing same
CH678217A5 (en) * 1983-12-01 1991-08-15 Eberhard Schmid Pneumatic or hydraulic cylinder with concentric piston rod
DE3435964A1 (de) * 1984-09-29 1986-04-10 Teja 7814 Breisach Winterhalter Zylinder mit verdrehungsgesicherter kolbenstange
DE3513214A1 (de) * 1985-04-12 1986-10-16 Licencia Találmányokat Ertékesítö Vállalat, Budapest Arbeitszylinder mit kugelfuehrung
DE8703310U1 (de) * 1987-03-05 1988-06-30 Robert Bosch Gmbh, 7000 Stuttgart Arbeitszylinder

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5761985A (en) * 1995-11-07 1998-06-09 Festo Kg Fluid power cylinder
DE19639548C2 (de) * 1995-11-07 2001-12-13 Festo Ag & Co Fluidbetätigter Arbeitszylinder
DE29721432U1 (de) * 1997-12-04 1998-02-26 Festo AG & Co, 73734 Esslingen Fluidbetätigter Arbeitszylinder
EP2199624A1 (fr) 2008-12-17 2010-06-23 Festo AG & Co. KG Actionneur linéaire fluidique avec unité de guidage

Also Published As

Publication number Publication date
ATE80206T1 (de) 1992-09-15
DE58902188D1 (de) 1992-10-08
ES2034502T3 (es) 1993-04-01
DE8915484U1 (de) 1991-04-18
EP0346716A1 (fr) 1989-12-20
DE3820337A1 (de) 1989-12-21

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