EP0475032B1 - Vérin à fluide avec cylindre fendu - Google Patents

Vérin à fluide avec cylindre fendu Download PDF

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Publication number
EP0475032B1
EP0475032B1 EP91112328A EP91112328A EP0475032B1 EP 0475032 B1 EP0475032 B1 EP 0475032B1 EP 91112328 A EP91112328 A EP 91112328A EP 91112328 A EP91112328 A EP 91112328A EP 0475032 B1 EP0475032 B1 EP 0475032B1
Authority
EP
European Patent Office
Prior art keywords
slot
cylinder
transverse groove
output member
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
EP91112328A
Other languages
German (de)
English (en)
Other versions
EP0475032A1 (fr
Inventor
Heinz Podlesak
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
Application filed by Knorr Bremse AG filed Critical Knorr Bremse AG
Priority to AT91112328T priority Critical patent/ATE86365T1/de
Publication of EP0475032A1 publication Critical patent/EP0475032A1/fr
Application granted granted Critical
Publication of EP0475032B1 publication Critical patent/EP0475032B1/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
    • F15B15/082—Characterised by the construction of the motor unit the motor being of the slotted cylinder type

Definitions

  • the invention relates to a pressure medium cylinder with a longitudinally slotted cylinder tube which is closed at the end, in which a piston is displaceably guided in a sealed manner by means of two piston seals arranged near its ends, which in the area between the piston seals by means of a connecting means penetrating the slot and having a driver located in front of the slot on the outside of the cylinder tube is connected to a sealing tape arranged on the inside of the cylinder tube, which seals the slot outside of the section enclosed by the two piston seals, and possibly a cover tape covering the outside of the slot with the exception of the penetration area of the connecting means, with a force-transmitting member which is guided axially displaceably on the outside of the cylinder, that at least faces away from the driver and overlaps laterally, and with an axial force-transmitting slot outside located and symmetrical to a through the slot extending, the cylinder axis containing central plane coupling device between the driver and the power output member.
  • Such a pressure medium cylinder is known from EP-B-0 157 892.
  • a coupling device designed as a rotary bearing which coupling device has at least one, preferably at right angles to the cylinder axis and in the longitudinal slot center plane bearing axis about which the piston and the force output member can be rotated against each other to a limited extent.
  • the bearing point is designed as a cylindrical part which is firmly connected to the driver and is located outside the cylinder tube in front of the slot and the axis of which runs through the slot at right angles to the cylinder axis; the force output member has a corresponding recess in which the cylinder part engages.
  • these known or otherwise designed coupling devices which only enable rotary movements between the force output member and the piston, it is not possible to exclude clamps between the force output member guided in the cylinder tube and the force output member guided on the outside or otherwise, since there are always displacements in the transverse direction between the two to the cylinder and to the axis of rotation of these coupling devices are possible.
  • transverse displacements of the force output member relative to the cylinder tube as are possible due to guideways manufactured inaccurately with respect to the cylinder axis or due to adjustment errors on the guide members of the power output member, lead to clamping and increased wear on the guide members and tracks of the power output member and the piston or its cylinder guide.
  • the coupling device has a feather key which is arranged at right angles crossing the slot and which has a central section in a slot-facing transverse groove of the driver and with each end section in a groove-like , engages to the transverse groove recess of the power output member.
  • the feather key can engage in one of the openings receiving it - either in the transverse groove or in the recesses - with a slight press fit and in the other opening - the recesses or the transverse groove - with a sliding fit or play. Due to the light press fit, the feather key is held in its preassembled position during assembly work, making assembly work easier. By choosing the sliding seat or the size of its play, the quality and the extent of the relative mobility for the coupling of the force output member and driver can be determined.
  • the side walls of the transverse groove are at least slightly convexly curved or spherical, at least in the longitudinal direction, in such a way that the transverse groove has a central, narrow section and then widens on both sides towards its end regions, a high quality is obtained Relative rotation possibility between the power output member and the driver created around a central axis, perpendicular to the cylinder axis of rotation.
  • the pressure medium cylinder has a cylinder tube 1, which is closed at the end by cylinder cover 2, as can be seen from FIG.
  • the cylinder cover 2 simultaneously mediate the pressure medium feeds to the pressurizing chambers 4 and 5 located on both sides of a piston 3.
  • the cylinder tube 1 has an approximately square cross section, it is provided with an eccentrically arranged cylinder bore 6.
  • a plurality of mounting and guide grooves 7, which are of no further interest here, are incorporated.
  • the cylinder wall 8 of the cylinder tube 1 lying in the offset direction of the cylinder bore 6 is cut open by means of a slot 10 running parallel to the cylinder axis 9.
  • the piston 3 is axially relatively elongated, it has a piston seal 11 near each of its two ends to limit the pressurizing spaces 4 and 5, respectively.
  • the piston 3 is provided with a web-like connecting means 12 which extends through the slot 10 and firmly connects the piston 3 to a driver 13 located in front of the slot 10 on the outside of the cylinder tube.
  • the driver 13 is facing away from the slot and overlapped laterally by a bow-like force output member 14, which is guided axially displaceably on both sides of the slot 10 by means of guide arrangements of no further interest on the outside of the cylinder tube 1.
  • indirect guidance can also be provided on special guide rails connected to the cylinder tube.
  • the slot 10 is pressure medium-tight on the inside of the cylinder tube in the area of the pressurization spaces 4 and 5 by a sealing tape 15 covered; in the area of the piston 3 between its piston seals 11, the sealing tape 15 is lifted from the slot 10 and guided through a guide channel 16 of the piston 3 in such a way that the slot 10 is free for the connection means 12 to pass through.
  • the slot 10 is covered outside the area of the piston 3 by a shroud 17, which is also lifted from the slot 10 in the area of the piston 3 and is guided through a space 18 located between the driver 13 and the force output member 14, such that the connecting means 12 can pass through the slot 10 and can be fixedly connected to the driver 13, can optionally be made in one piece with it.
  • magnetic tapes 19 can be inserted into the cylinder tube 1 on both sides of the slot 10, which magnetically hold the shroud 17 made of suitable material outside the area of the piston 3. 1 and 2, neither the sealing tape 15 nor the shroud 17 are shown to simplify the illustrations.
  • the pressure medium cylinder corresponds to a conventional slot cylinder, as is known, for example, from EP-B-0 113 790 or 0 157 892 mentioned at the beginning.
  • the driver 13 For coupling the driver 13 to the force output member 14, the driver 13 has a transverse groove 20 approximately in the middle of its longitudinal extent on its side facing away from the slot, to each of which a groove-like recess 21 in the force output member 14 adjoins the transverse groove 20.
  • the two recesses 21 are also open on the cylinder tube side.
  • a straight key 22 is inserted into the transverse groove 20 such that it engages with its end sections in the recesses 21: the key 22 thus runs transversely to the slot 10, crossing it at a right angle.
  • the section of the parallel key 22 engaging in the transverse groove 20 is longer, preferably approximately twice as long as each of the end sections of the parallel key engaging in one of the recesses 21 22.
  • the parallel key 22 it is expedient to design the parallel key 22 with a larger height seen perpendicular to the longitudinal direction of the slot than the thickness seen in the longitudinal direction of the slot. Finally, it is expedient to make the end faces of the parallel key 22 semi-cylindrical in order to round a cylinder axis perpendicular to the longitudinal direction of the slot.
  • the key 22 with the transverse groove 20 and the recesses 21 having coupling device between the driver 13 and the force output member 14 can be designed such that the key 22 engages with play both in the transverse groove 20 and the recesses 21. In this embodiment, however, there is considerable play in the longitudinal direction between the driver 13 and the power output member 14, which may be undesirable. In addition, the assembly can be difficult: When the power output member 14 is placed on the cylinder tube 1 and the driver 13, which can be done, for example, with the lateral guide legs 23 of the power output member 14 removed, the feather key 22 previously loosely inserted in the transverse groove 20 or the recesses 21 change their position. Even if the piston 3, the feather key 22 and the force output member 14 are assembled outside the cylinder tube 1 for mounting the pressure medium cylinder and then axially pushed into or onto the latter, the loose feather key 22 can cause difficulties.
  • the longitudinal play between the driver 13 and the force output member 14 is reduced, as a result of which the longitudinal force transmission between the piston 3 and the power output member 14 can be done more precisely, and at the same time an unwanted change in position of the parallel key 22 is excluded during assembly operations.
  • the side walls of the transverse groove 20 are slightly convex in the longitudinal direction or convex, such that the transverse groove 20 has a central, narrow section and then expand on both sides towards their end areas.
  • the feather key 22 is expediently held in the above-mentioned middle, narrow section and in the recesses 21 parallel to the cylinder axis 9 with a sliding or slight press fit, so that the coupling device is at least almost free of play in this direction.
  • the side walls of the transverse groove 20 are also convexly curved in their transverse direction, at least in their central longitudinal extension region, there is a further possibility of rotation about an axis of rotation which is perpendicular to the aforementioned.
  • the force output member 14 can carry out displacements transversely as well as perpendicular to the longitudinal direction of the slot 10 relative to the driver 13, and rotations about a parallel to the cylinder axis 9 Axis of rotation possible. Furthermore, within the scope of the games on the parallel key 22, rotations of the force output member 14 relative to the driver 13 are possible about axes of rotation which run perpendicular to the cylinder axis 9 or cross the latter.
  • the parallel key 22 can also be rotated relative to the transverse groove 22 during these rotations, although it can be designed as a play-free coupling device in the direction of force transmission between the piston 3 and the force output member 14.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Tires In General (AREA)

Claims (7)

  1. Cylindre à milieu sous pression, avec un tube de cylindre (1) fendu longitudinalement, fermé à l'une de ses extrémités, et dans lequel est guidé un piston (3) avec étanchéité assurée par deux garnitures d'étanchéité (11) prévues aux voisinages des extrémités du piston qui, dans la région située entre lesdites garnitures (11), est relié, à l'aide d'un élément de liaison (12) passant par la fente (10), rigidement à un élément d'entraînement (13) situé devant la fente (10) et à l'extérieur du tube de cylindre, ainsi qu'avec une bande d'étanchéité (15), située du côté intérieur du tube de cylindre et recouvrant de façon étanche au milieu sous pression, la fente (10) en dehors de la section qui est délimitée par les deux garnitures, et éventuellement un ruban de couverture (17) qui recouvre, du côté extérieur la fente (10), à l'exception de la zone de passage de l'élément de liaison (12), et avec un élément menant (14) guidé indirectement ou directement dans le sens axial sur le côté extérieur du cylindre et chevauchant l'élément d'entrainement (13) au moins par ses deux côtés et du côté éloigné de la fente, ainsi qu'avec un dispositif d'accouplement entre l'élément d'entraînement (13) et l'élément menant (14), qui transmet des forces axiales, qui est situé du côté extérieur de la fente et qui est symétrique par rapport à un plan médian (24) qui contient l'axe (9) du cylindre, caractérisé par le fait que le dispositif d'accouplement comporte un ressort d'ajustage (22) qui est disposé de manière à croiser à angle droit la fente (10) et qui pénètre, par une section médiane, dans une gorge transversale (20) de l'élement d'entraînement (13), éloignée de la fente, et, par chaque section d'extrémité, dans une ouverture (22) de l'élément menant (14), formée à la manière d'une gorge et alignée sur la gorge transversale (20).
  2. Cylindre à milieu sous pression selon la revendication 1, caractérisé par le fait que les deux ouvertures (21) de l'élément menant (14) sont dégagés du côté du tube de cylindre.
  3. Cylindre à milieu sous pression selon la revendication 1 ou 2, caractérisé par le fait que le ressort d'ajustage (22) pénètre dans l'une des ouvertures horizontale -soit la gorge (20) ou les ouvertures (21)- qui le reçoit, avec un léger ajustage serré, et pénètre dans l'autre ouverture correspondante -qui sont les ouvertures (21) ou la gorge transversale (20)- horizontale avec un ajustement appuyé ou avec jeu.
  4. Cylindre à milieu sous pression selon une ou plusieurs des revendications précédentes, caractérisé par le fait que les parois latérales de la gorge transversale (20) présentent, au moins dans la direction longitudinale, une courbure légèrement convexe ou bombée, de manière que la gorge transversale (20) possède une section médiane étroite et s'élargit des deux côtés, en partant de ladite section médiane vers les zones d'extrémités.
  5. Cylindre à milieu sous pression selon une ou plusieurs des revendications précédentes, caractérisé par le fait que le ressort d'ajustage (22) présente, dans la direction longitudinale de la fente, une hauteur plus grande par rapport à l'épaisseur mesurée dans la direction longitudinale de la fente.
  6. Cylindre à milieu sous pression selon la revendication 5, caractérisé par le fait que le ressort d'ajustage (22) présente des côtés frontaux arrondis en demi-cylindre autour d'axes du cylindre, qui sont perpendiculaires à la direction longitudinale de la fente.
  7. Cylindre à milieu sous pression selon une ou plusieurs des revendications précédentes, caractérisé par le fait que la section médiane du ressort d'ajustage (22), qui pénètre dans la gorge transversale (20) est plus longue, éventuellement deux fois aussi longue que chaque section d'extrémité qui pénètre dans une des ouvertures (21).
EP91112328A 1990-08-03 1991-07-23 Vérin à fluide avec cylindre fendu Expired - Lifetime EP0475032B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT91112328T ATE86365T1 (de) 1990-08-03 1991-07-23 Druckmittelzylinder mit laengsgeschlitztem zylinderrohr.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4024717 1990-08-03
DE4024717A DE4024717A1 (de) 1990-08-03 1990-08-03 Druckmittelzylinder mit laengsgeschlitztem zylinderrohr

Publications (2)

Publication Number Publication Date
EP0475032A1 EP0475032A1 (fr) 1992-03-18
EP0475032B1 true EP0475032B1 (fr) 1993-03-03

Family

ID=6411619

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91112328A Expired - Lifetime EP0475032B1 (fr) 1990-08-03 1991-07-23 Vérin à fluide avec cylindre fendu

Country Status (4)

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EP (1) EP0475032B1 (fr)
JP (1) JPH05133408A (fr)
AT (1) ATE86365T1 (fr)
DE (2) DE4024717A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4137789C2 (de) * 1991-11-16 1994-01-20 Festo Kg Linearantrieb
DE4334681C2 (de) * 1993-10-12 1995-09-28 Norgren Martonair Gmbh Bewegungseinheit zur Erzeugung einer Linearbewegung
DE4413512A1 (de) * 1994-04-19 1995-10-26 Hygrama Ag Kolbenstangenloser Druckmittelzylinder
DE29508663U1 (de) * 1995-05-24 1995-08-17 Festo Kg, 73734 Esslingen Kupplungseinrichtung für Linearantriebe
JP3011084B2 (ja) * 1995-12-27 2000-02-21 豊和工業株式会社 直線作動機

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0113790B1 (fr) * 1983-01-14 1987-03-11 PROMA Produkt- und Marketing Gesellschaft m.b.H. Cylindre sous pression avec un tube cylindrique fendu longitudinalement et fermé aux extrémités
EP0157892B1 (fr) * 1984-04-10 1987-06-24 Reinhard Lipinski Transporteur linéaire
EP0294350A1 (fr) * 1987-06-03 1988-12-07 Linjär Transportteknik I Stockholm Ab Moteur linéaire

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4998459A (en) * 1989-09-22 1991-03-12 Blatt John A Rodless fluid actuated motor with improved sealing characteristics

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0113790B1 (fr) * 1983-01-14 1987-03-11 PROMA Produkt- und Marketing Gesellschaft m.b.H. Cylindre sous pression avec un tube cylindrique fendu longitudinalement et fermé aux extrémités
EP0157892B1 (fr) * 1984-04-10 1987-06-24 Reinhard Lipinski Transporteur linéaire
EP0294350A1 (fr) * 1987-06-03 1988-12-07 Linjär Transportteknik I Stockholm Ab Moteur linéaire

Also Published As

Publication number Publication date
DE4024717A1 (de) 1992-02-06
ATE86365T1 (de) 1993-03-15
EP0475032A1 (fr) 1992-03-18
DE59100053D1 (de) 1993-04-08
JPH05133408A (ja) 1993-05-28

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