EP0519185B1 - Vérin commandé par un fluide sous pression - Google Patents

Vérin commandé par un fluide sous pression Download PDF

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Publication number
EP0519185B1
EP0519185B1 EP92107083A EP92107083A EP0519185B1 EP 0519185 B1 EP0519185 B1 EP 0519185B1 EP 92107083 A EP92107083 A EP 92107083A EP 92107083 A EP92107083 A EP 92107083A EP 0519185 B1 EP0519185 B1 EP 0519185B1
Authority
EP
European Patent Office
Prior art keywords
longitudinal
cylinder
flange plate
working cylinder
cylinder liner
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
EP92107083A
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German (de)
English (en)
Other versions
EP0519185B2 (fr
EP0519185A1 (fr
Inventor
Philippe Ducrettet
Christian . Tour
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
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Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0519185A1 publication Critical patent/EP0519185A1/fr
Application granted granted Critical
Publication of EP0519185B1 publication Critical patent/EP0519185B1/fr
Publication of EP0519185B2 publication Critical patent/EP0519185B2/fr
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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
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1428—Cylinders

Definitions

  • the invention relates to a pressure-operated cylinder according to the genus specified in the preamble of claim 1.
  • Such a pressure-actuated working cylinder is already known from DE 37 06 952 A1, in which a directional control valve controlling the working cylinder can be mounted on a flange plate which is arranged on two parallel, adjacent tie rods of this working cylinder.
  • the two tie rods penetrating the flange plate are made hollow from the four tie rods and used as pressure medium channels, via which the pressure medium controlled by the directional control valve is guided into the two pressure chambers on both sides of the piston.
  • the disadvantage of this working cylinder is that pressure medium channels are guided externally from the actual cylinder tube and transfer openings for the pressure medium from the hollow tie rod in the cover area must be provided, an additional receiving plate being required compared to the cylinder cover.
  • the working cylinder therefore requires a relatively large number of components and also results in a large number of sealing points, the transition points from the tie rods, which are loaded with high forces, into the cylinder cover being particularly critical.
  • the working cylinder is therefore relatively complex, with the risk of leakage being relatively large.
  • DE 29 18 294 C2 discloses a pressure-actuated working cylinder, in which the cylinder tube installed between two cylinder covers is designed as a profile tube with external channels, which can be used with the aid of additional components for different functions, such as pressure-carrying circulation channels or mounting channels.
  • the disadvantage of this cylinder is that the outer channels must have a longitudinal slot over their entire length, so that profiled components can be installed depending on the corresponding function. This leads to high construction costs and a risk of leakage. It is also unfavorable that when an external channel is used as the pressure medium channel, a seal or pressure medium connection has to be made via the front cylinder cover, which also increases the number of pressure medium-carrying components. For the rest, no information is given here on the attachment of a flange plate with directional control valve.
  • the pressure cylinder-actuated working cylinder according to the invention with the characterizing features of the main claim has the advantage that it allows a compact unit with integrated pressure medium channels, the risk of leakage pressure medium is particularly reduced.
  • the working cylinder needs fewer components, especially those with pressurization.
  • the working cylinder is easy to handle and versatile. It can be produced in a space-saving and thus inexpensive manner.
  • a construction according to claim 2 is particularly favorable, as a result of which a relatively simple and inexpensive profile tube can be used for the working cylinder. It is also advantageous if the working cylinder is designed according to claim 3, so that the longitudinal struts can also take over the function of tie rods if necessary. Furthermore, it is advantageous if the working cylinder is designed according to claims 4 and 9, as a result of which the flange plate can be guided and held properly. In addition, it is advantageous if, according to claim 5, the connections for inlet and return are formed directly on the flange plate. Further advantageous configurations result from the remaining claims, the description and the drawing.
  • FIG. 1 shows a perspective illustration of the working cylinder which can be actuated by pressure medium in a simplified manner
  • FIG. 2 shows a front view of the working cylinder according to FIG. 1, partly in longitudinal section
  • FIG. 3 shows a top view of the working cylinder according to FIG. 2
  • FIG. 4 shows a side view according to A in FIG. 2.
  • FIG. 1 shows a perspective, schematic illustration of a pressure cylinder that can be actuated by pressure medium, for the explanation of which reference is also made to FIGS. 2 to 4.
  • the working cylinder 10 has, as a housing, an essentially tubular cylinder liner 11, on the outside of which a flange plate 12 is attached, which in turn carries a flanged directional valve 13.
  • the cylinder liner 11 has a continuous guide bore 14 in which a piston 15 is guided so as to be axially displaceable.
  • a piston rod 16 is fastened to the piston 15 and is sealed in a first, front cylinder cover 17 is slidably guided and protrudes through the latter outwards.
  • the first cylinder cover 17 is inserted on the piston rod side into the guide bore 14 of the cylinder liner 11 and is axially fastened there and, together with the piston 15, delimits a first, front pressure chamber 18 installed and delimits a second pressure chamber 21 with the piston 15.
  • the tubular cylinder sleeve 11 has on its outer surface four longitudinal struts 22 to 25 running parallel to the longitudinal axis, of which the two longitudinal struts 22, 23 can be used as guide elements for the flange plate 12.
  • the longitudinal struts 22 to 25 are arranged on the outer circumference of the cylinder liner 11 evenly distributed, so that they are seen in cross section through the cylinder liner 11 on the corners of a square.
  • the longitudinal struts 22 to 25 are each integrally formed in the manner of profile rails on the outer surface of the cylinder liner 11, so that the cylinder liner 11 can be easily produced from a profile tube.
  • the outer surface of the cylinder liner 11 is seen in cross section essentially as an octagon, in which the vertically and horizontally lying four longitudinal surfaces 26 are continuous and flat, while the longitudinal struts 22 to 25 are integrally formed on the four obliquely lying longitudinal surfaces 27.
  • Each of these longitudinal struts 22 to 25 forms an approximately semicircular guide surface 28 towards the outside, each of which merges into the oblique longitudinal surface 27 via two guide surfaces 29, 31 running approximately parallel to one another.
  • Each of the longitudinal struts 22 to 25, which extend over the entire length of the cylinder liner 11, has a continuous longitudinal bore 32.
  • the two axial end regions of each longitudinal bore 32 have blind bore-like threaded bores 33, 34 which are introduced into them at the end face and run in the axial direction.
  • sealing plugs 35 are screwed into the threaded bores 33 and 34, respectively, from the relevant end faces, so that the longitudinal bore 32 in the first longitudinal strut 22 forms a first pressure medium channel 36.
  • This first pressure medium channel 36 is connected to the second pressure chamber 21 via a first oblique bore 37 arranged in the cylinder liner 11.
  • a second pressure medium channel 38 is formed in the second longitudinal strut 23, which is connected to the first, front pressure chamber 18 via a second oblique bore 39, which lies in the region of the first cylinder cover 17.
  • the two oblique bores 37, 39 can be easily produced in the profiled cylinder liner 11 and form so-called transition openings to the two pressure chambers on both sides of the piston 15.
  • the flange plate 12 has on its underside two mounting grooves 41, 42 which are open on one side and whose shape is precisely adapted to the outer contour of the longitudinal struts 21, 22, so that the flange plate 12 is perfectly and axially displaceable is guided on the longitudinal struts 21, 22.
  • the flange plate 12 is pushed from an end face of the cylinder liner 11 onto the longitudinal struts 22, 23 and locked in a predetermined position by locking screws 43.
  • the center planes of the two mounting grooves 41, 42 run perpendicular to one another, so that the flange plate 12 engages behind the longitudinal struts 22, 23 and is therefore held captively in the radial direction on the cylinder liner 11.
  • the flange plate 12 In the locked position, the flange plate 12 has such a position that the first pressure medium channel 36 in the longitudinal strut 22 has a first motor connection 46 in a flange surface 47 via a first transition opening 44 (FIG. 2) and transverse channels 45 running in the flange plate 12.
  • a pump pressure connection 52 located in the flange surface 47 between the two motor connections 46, 48 is connected to an inlet connection 53, which is formed in a rear end face 54 of the flange plate 12.
  • an angle connection 55 is additionally screwed into this inlet connection 53, which is not shown in FIG. 1 for the sake of simplicity.
  • two return connections 56, 57 are arranged in the flange surface 47, of which, for the sake of simplicity, only the connection from the return connection 56 to an outlet connection 58 located in the side wall of the flange plate 12 is shown in FIG.
  • the two transfer openings 44, 51 between the flange plate 12 and the two longitudinal struts 22, 23 on the cylinder liner 11 are sealed by suitable seals, so that no pressure medium can leak to the outside at the transition of the pressure medium channels from the flange plate 12 into the cylinder liner 11.
  • FIG. 1 the course of the pressure medium flow is indicated in a simplified form with arrows, as it results when the directional valve 13 is switched accordingly and when the piston rod 16 extends.
  • a pressure medium which is used to actuate the working cylinder 10, is introduced at the inlet connection 53 into the flange plate 12, where it arrives at the inlet connection 52 in the flange surface 47.
  • the pressure now flows in the directional control valve 13 itself medium from the pump pressure connection 52 to the first motor connection 46 into the flange surface 47, whereupon it flows through the flange plate 12 through the transverse channels 45 and the first transition opening 44 into the first pressure medium channel 36 in the first longitudinal strut 22.
  • the 5/2-way valve 13 If the piston rod 16 on the working cylinder 10 is to be retracted, the 5/2-way valve 13 is switched over.
  • the directional control valve 13 then controls pressure medium from the pump pressure connection 52 to the second motor connection 48 and thus into the first, front pressure chamber 18, whereupon the piston 15, which is pressurized on the front side, retracts the piston rod 16.
  • pressure medium from the second pressure chamber 21 is in turn controlled via the first motor connection 46 to the return connection 56 and can thus escape via the exhaust air caps 59.
  • all pressurized channels are thus within a few components, including in particular the directional control valve 13, the flange plate 12 and the cylinder liner 11.
  • the risk of leakage pressure medium escaping is thus kept extremely low.
  • the flange plate 12 is guided in a perfect and captive manner on the cylinder bushing 11 and can be adapted in its axial position to the particular circumstances by merely drilling the two transition openings 44 and 51 on the two longitudinal struts 22 and 23, respectively.
  • the cylinder liner 11 can be produced in a simple and inexpensive manner from a profiled tube, the two pressure medium channels 36 and 38 being able to be installed in any way in two adjacent longitudinal struts 22 to 25.
  • the oblique bores 37 and 39 can be easily manufactured in the profile tube in terms of production technology.
  • the flange plate 12 with directional valve 13 can be removed without having to remove the cylinder covers 17, 19 from the cylinder liner 11.
  • the working cylinder 10 is therefore versatile and can be manufactured inexpensively.
  • the longitudinal struts 22 to 25 as integrated components of the cylinder liner 11 perform a variety of functions; They not only serve to guide and hold the flange plate 12, but also form pressure medium-carrying channels for controlling the working cylinder 10. Furthermore, they can also be used for the function of tie rods if required, if other types of cover are used instead of the cylinder cover shown.
  • the working cylinder is not limited to use as a pneumatic cylinder, but can also be operated with hydraulic pressure medium.

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

Claims (11)

1. Vérin (10) commandé par un fluide sous pression, dans lequel :
- une douille tubulaire (11), contenant un piston (15) coulissant axialement, est fermée à ses deux extrémités par des couvercles (17, 19), dont au moins un est traversé par la tige (16) du piston.
- le long de la douille, à l'extérieur et parallèlement à son axe longitudinal, plusieurs éléments de guidage (22, 25) sont répartis régulièrement à sa périphérie, deux d'entre eux (22, 23) voisins, servant de support à un plateau de bridage (12) pouvant coulisser en direction longitudinale et recevoir un distributeur servant à commander le vérin.
- les deux éléments de guidage supportant le plateau de bridage sont creux et percés d'ouverture de passage (37, 39, 44, 51) au niveau du plateau de bridage et des couvercles du vérin, de sorte que le fluide sous pression peut être envoyé, par la soupape de commande dans l'une ou l'autre des deux chambres de pression (18, 21) encadrant le piston,
caractérisé en ce que les éléments de guidage s'étendant le long de la douille (11), parallèlement à l'axe longitudinal, font partie de la douille et sont constitués par des nervures longitudinales (22,23) présentant des surfaces externes de guidage (28, 29, 31) maintenant de manière imperdable le plateau de bridage glissé dessus, les ouvertures de passage (39, 37) reliant les deux nervures (22, 23) aux deux chambre de pression (18, 21) se situant dans la douille (11) du vérin.
2. Vérin selon la revendication 1, caractérisé en ce que la douille (11) est une pièce extrudée en forme de tube profilé qui porte à l'extérieur quatre nervures longitudinales (22, 23, 24, 25) qui vues en coupe transversale, sont situées aux coins d'un rectangle, de préférence aux coins d'un carré, et présentent chacune un alésage longitudinal interne continu (32);
3. Vérin selon la revendication 2, caractérisé en ce que les alésages (32) situés à l'intérieur des nervures (22 à 25) présentent à partir des faces frontales de la douille (11), des extrémités munies d'alésages filetés (33, 34).
4. Vérin selon une des revendications 1 à 3, caractérisé en ce que les rainures de maintien (41,42) associées aux nervures (22, 23) sont ouvertes sur un côté du plateau de bridage (12) et sont conçues pour que le plateau (12) est maintenu, radialement imperdable sur la douille (11).
5. Vérin selon une des revendications 1 à 4, caractérisé en ce que les raccords d'amenée (53) et de retour (58) du fluide sous pression sont prévus sur le plateau de bridage (12).
6. Vérin selon une des revendications 2 à 5, caractérisé en ce que la douille de vérin (11) a une forme extérieure qui dessine, en coupe transversale, un octogone sensiblement régulier, les nervures longitudinales (22 à 25) se plaçant chacune au milieu de quatre faces longitudinales (27) opposées deux par deux.
7. Vérin selon une ou plusieurs des revendications précédentes, caractérisé en ce qu'un dispositif de sécurité (43) empêchant le coulissement axial le long des nervures (22, 23) est monté sur le plateau de bridage (12).
8. Vérin selon une des revendications 1 à 7, caractérisé en ce que le couvercle de vérin (17, 19) est bloqué axialement dans la douille de vérin (11).
9. Vérin selon une des revendications 1 à 8, caractérisé en ce que la nervure longitudinale (22 à 25) du profilé tubulaire présente une surface de guidage (28), sensiblement semi-circulaire en coupe transversale, prolongée par deux surfaces de guidage sensiblement parallèles (29, 31), aboutissant à une face longitudinale (27) de la douille de vérin (11).
10. Vérin selon la revendication 8, caractérisé en ce que les deux couvercles de vérin (17, 19) sont montés dans un alésage (14) de guidage contenant le piston (15).
11. Vérin selon la revendication 8 ou 10, caractérisé en ce que le diamètre extérieur maximal du couvercle (17, 19) correspond au diamètre de l'alésage de guidage (14).
EP92107083A 1991-06-19 1992-04-25 Vérin commandé par un fluide sous pression Expired - Lifetime EP0519185B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4120170A DE4120170A1 (de) 1991-06-19 1991-06-19 Druckmittelbetaetigbarer arbeitszylinder
DE4120170 1991-06-19

Publications (3)

Publication Number Publication Date
EP0519185A1 EP0519185A1 (fr) 1992-12-23
EP0519185B1 true EP0519185B1 (fr) 1994-10-19
EP0519185B2 EP0519185B2 (fr) 1999-08-11

Family

ID=6434253

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92107083A Expired - Lifetime EP0519185B2 (fr) 1991-06-19 1992-04-25 Vérin commandé par un fluide sous pression

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EP (1) EP0519185B2 (fr)
DE (2) DE4120170A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2710372B1 (fr) * 1993-09-22 1995-11-17 Alain Bourgeois Dispositif de commande hydraulique d'un vérin à double effet.
JP3131570B2 (ja) * 1996-10-14 2001-02-05 エスエムシー株式会社 ロータリーアクチュエータ
DE10043647B4 (de) * 2000-09-05 2004-02-05 Robert Bosch Gmbh Druckmittelbetätigbare Stelleinheit
DE10112637A1 (de) * 2001-03-14 2002-09-19 Continental Teves Ag & Co Ohg Aus einem Strang abgeschnittenes Rohteil f. einen Hauptzylinder sowie hieraus gefertigter Hauptzylinder
US11009048B1 (en) 2020-09-09 2021-05-18 Robert Bosch Gmbh Boom lift system

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3060901A (en) * 1960-05-31 1962-10-30 Ling Temco Vought Inc Hydraulic actuator with integrally housed valve
US3571883A (en) * 1968-04-19 1971-03-23 Westinghouse Air Brake Co Method of making a fluid operated cylinder device
DE3246970A1 (de) * 1982-12-18 1984-06-20 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Druckmittelbetaetigbarer arbeitszylinder
DE8315785U1 (de) * 1983-05-28 1986-06-26 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Druckmittelbetätigte Kolben-Zylinder-Einheit mit Magnetschuh als Verdrehsicherung
DE3436946C2 (de) * 1984-10-09 1994-06-09 Mannesmann Ag Linearantrieb
FR2573490B1 (fr) * 1984-11-19 1988-08-26 Telemecanique Electrique Verin ayant un canal de transfert integre dans le cylindre
AT386656B (de) * 1986-04-01 1988-09-26 Hoerbiger Pneumatic Gmbh Druckmittelbetaetigbarer arbeitszylinder
ES2045272T3 (es) * 1989-03-03 1994-01-16 Festo Kg Cilindro para una unidad de cilindro-piston.

Also Published As

Publication number Publication date
DE59200647D1 (de) 1994-11-24
EP0519185B2 (fr) 1999-08-11
EP0519185A1 (fr) 1992-12-23
DE4120170A1 (de) 1992-12-24

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