EP0346716A1 - 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
EP0346716A1
EP0346716A1 EP89110115A EP89110115A EP0346716A1 EP 0346716 A1 EP0346716 A1 EP 0346716A1 EP 89110115 A EP89110115 A EP 89110115A EP 89110115 A EP89110115 A EP 89110115A EP 0346716 A1 EP0346716 A1 EP 0346716A1
Authority
EP
European Patent Office
Prior art keywords
piston rod
piston
bearing component
sealing
longitudinal
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
EP89110115A
Other languages
German (de)
English (en)
Other versions
EP0346716B1 (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 which can be pressurized with compressed air and has a piston rod which, at least in the length range which seals the associated cylinder cover by a seal against the escape of compressed air, has a cross section which deviates from the circular cross section and which has a piston rod that is non-rotatably connected to the cylinder enforced bearing component is assigned, which leads the piston rod longitudinally displaceable, but secured against rotation.
  • the piston rod of piston-cylinder units which can be pressurized with pressure medium, i.e. pneumatic or hydraulic cylinders, have a cylindrical shape, at least in the length section passing through the associated cylinder cover during the working stroke, which seals the gap between the piston rod and the passage opening in the cylinder cover against loss of pressure and discharge of the pressure medium by means of conventional ring seals - be it O-rings or lip sealing rings. 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.
  • pressure medium i.e. pneumatic or hydraulic cylinders
  • 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 Complex and the number of required components and the effort for their processing and assembly increases significantly compared to a simple piston-cylinder unit not secured against rotation.
  • the invention is based on the object to provide a piston-cylinder unit in which the outer dimensions of the piston-cylinder unit, at most slightly increasing, the piston rod against rotation self-guidance is integrated, the rotation lock no stiffness or loss of compressed air.
  • the piston rod in the area passing through the associated cylinder cover is formed over the largest part of the circumference by surface sections of circular cross section with the same circle radius, which are at uniform angular intervals from radially projecting or recessed, longitudinally running ball raceways educational Sections are interrupted that on the outside of the cylinder cover facing away from the piston is attached a bearing member penetrated by the piston rod, which in turn has ball raceways in alignment with the longitudinal ball raceways, with rows of on the in the space between the outer surface of the piston rod and the inner surface of the bearing member Ball raceways of the piston rod on the one hand and ball balls rolling on the other hand of the bearing component are arranged, and that in the connecting area between the cylinder cover and the bearing component in a circumferential receiving groove surrounding the piston rod at a radial distance, a lip sealing ring is provided with a passage opening that complements the cross-sectional shape of the piston rod , whose sealing lips are directed into the interior of the piston-cylinder unit.
  • the piston rod is therefore basically similar to a longitudinally displaceably guided shaft secured against rotation by a linear motion bearing with ball guides, but the problem of sealing the piston rod against the pressure built up by the pressure medium inside the piston-cylinder unit does not occur with such shafts a special lip sealing ring with the cross-sectional shape of the piston rod adapted opening is released.
  • the piston rod is provided with a number of equally spaced, radially protruding and extending in the working stroke longitudinal wedges, which are provided on both sides in the transition area to the adjoining circular cross-sectional surface section with the ball raceways, with the bearing component 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 raceways 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, the radial dimensions measured between the outer and the inner sealing lip in the areas associated with the longitudinal wedges of the piston rod less than a Is in the circumferentially intermediate areas.
  • 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 tion is closed all around and continuously on the outer surface of the piston rod sealing elastic sealing lip is provided, between the two sealing lips pointing in the same direction a circumferential pressure chamber is formed, open to the cylinder interior, the radial dimensions of which are measured between the outer and the inner sealing lip 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 for the piston rod 12.
  • a cylindrical bore 22 of the cylinder is a bore in two resizable 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 usual circular cross-sectional shape - the cross section recognizable in FIG. 2, in which the longitudinal wedges offset from one another by a basically circular basic cross section in each case by 120 ° in the circumferential direction 38 protrude radially, 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 centered in the cylinder cover 18 and is screwed to the cylinder cover to prevent rotation.
  • 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 somewhat emerges from the bearing component 46 at the end on the left in FIG. 1.
  • 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 mounted, by 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, matched bores in the fully extended end position of the piston rod 12.
  • the piston rod 12 is thus secured against rotation by the rows of balls which support the longitudinal wedges 38 laterally and are in turn supported 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 cage 58 made of plastic holds the bearing balls 42 so 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 retained in the bearing component 46 by the cage 58, so that there is no risk of the loss of individual bearing balls 42 when the piston-cylinder unit 10 is disassembled or assembled .
  • 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.
  • a strong pressure of the sealing lip 70 on the piston rod section 36 only takes place 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 piston as described above in connection with FIGS. 1 to 5.
  • 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 on the other are provided with the same reference numerals.
  • the two exemplary embodiments 10 and 10 ' largely coincide, the design adopted in the piston-cylinder unit 10 being fundamentally suitable for securing the piston rod against rotation against higher moments seeking to rotate it, and on the other hand in the design according to the piston-cylinder Unit 10 'of Lip sealing ring 60 'has a less complex and therefore simpler to manufacture.

Landscapes

  • 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)
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 true EP0346716A1 (fr) 1989-12-20
EP0346716B1 EP0346716B1 (fr) 1992-09-02

Family

ID=6356586

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 (6)

* Cited by examiner, † Cited by third party
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
DE4430373A1 (de) * 1993-08-26 1995-03-02 Templeton Kenly & Co Hydraulischer Nasenlastenheber
EP0965779A2 (fr) 1998-06-20 1999-12-22 Festo AG & Co Anneau d'étanchéité
EP0896159A3 (fr) * 1997-08-04 2000-09-27 Waircom M.B.S. S.p.A. Cylindre pneumatique à tige de piston non rotative
US7127982B2 (en) 2005-03-04 2006-10-31 Festo Corporation Linear drive with non-rotating piston

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE29507688U1 (de) * 1995-05-10 1995-07-20 Festo Kg, 73734 Esslingen Fluidbetätigter Arbeitszylinder
DE29517615U1 (de) * 1995-11-07 1995-12-21 Festo Kg, 73734 Esslingen Fluidbetätigter Arbeitszylinder
DE29721432U1 (de) * 1997-12-04 1998-02-26 Festo AG & Co, 73734 Esslingen Fluidbetätigter Arbeitszylinder
JP2001295809A (ja) * 2000-04-11 2001-10-26 Smc Corp ガイド付きシリンダ
EP2199624B1 (fr) 2008-12-17 2012-06-06 FESTO AG & Co. KG Actionneur linéaire fluidique avec unité de guidage
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

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1171749A (fr) * 1956-04-18 1959-01-29 Bendix Aviat Corp Perfectionnements aux vérins
FR2035439A5 (fr) * 1969-02-15 1970-12-18 Neumeister Otto
US3994539A (en) * 1975-07-22 1976-11-30 Robomation Corporation Self-contained activated slide apparatus and methods of constructing and utilizing same
DE3444048A1 (de) * 1983-12-01 1985-07-18 Eberhard 7207 Aldingen Schmid Pneumatik- oder hydraulikzylinder mit konzentrischer kolbenstange

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1171749A (fr) * 1956-04-18 1959-01-29 Bendix Aviat Corp Perfectionnements aux vérins
FR2035439A5 (fr) * 1969-02-15 1970-12-18 Neumeister Otto
US3994539A (en) * 1975-07-22 1976-11-30 Robomation Corporation Self-contained activated slide apparatus and methods of constructing and utilizing same
US3994539B1 (fr) * 1975-07-22 1987-02-10
DE3444048A1 (de) * 1983-12-01 1985-07-18 Eberhard 7207 Aldingen Schmid Pneumatik- oder hydraulikzylinder mit konzentrischer kolbenstange

Cited By (9)

* Cited by examiner, † Cited by third party
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
DE4430373A1 (de) * 1993-08-26 1995-03-02 Templeton Kenly & Co Hydraulischer Nasenlastenheber
GB2283283A (en) * 1993-08-26 1995-05-03 Templeton Kenly & Co Inc Hydraulic toe jack
US5524868A (en) * 1993-08-26 1996-06-11 Templeton, Kenly & Co., Inc. Hydraulic toe jack
GB2283283B (en) * 1993-08-26 1998-04-08 Templeton Kenly & Co Inc Hydraulic toe jack
EP0896159A3 (fr) * 1997-08-04 2000-09-27 Waircom M.B.S. S.p.A. Cylindre pneumatique à tige de piston non rotative
EP0965779A2 (fr) 1998-06-20 1999-12-22 Festo AG & Co Anneau d'étanchéité
US7127982B2 (en) 2005-03-04 2006-10-31 Festo Corporation Linear drive with non-rotating piston

Also Published As

Publication number Publication date
DE3820337A1 (de) 1989-12-21
ES2034502T3 (es) 1993-04-01
DE8915484U1 (de) 1991-04-18
EP0346716B1 (fr) 1992-09-02
DE58902188D1 (de) 1992-10-08
ATE80206T1 (de) 1992-09-15

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