EP0089568B1 - Dispositif d'actionnement rotatif à fluide sous pression - Google Patents

Dispositif d'actionnement rotatif à fluide sous pression Download PDF

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Publication number
EP0089568B1
EP0089568B1 EP83102387A EP83102387A EP0089568B1 EP 0089568 B1 EP0089568 B1 EP 0089568B1 EP 83102387 A EP83102387 A EP 83102387A EP 83102387 A EP83102387 A EP 83102387A EP 0089568 B1 EP0089568 B1 EP 0089568B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
piston
guide
guides
pistons
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
Application number
EP83102387A
Other languages
German (de)
English (en)
Other versions
EP0089568A1 (fr
Inventor
Gerhardus Marinus Jozef Pierik
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.)
Cessione tebel Pneumatiek Bv
Original Assignee
P M I de Jong BV
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 P M I de Jong BV filed Critical P M I de Jong BV
Priority to AT83102387T priority Critical patent/ATE15402T1/de
Publication of EP0089568A1 publication Critical patent/EP0089568A1/fr
Application granted granted Critical
Publication of EP0089568B1 publication Critical patent/EP0089568B1/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
    • F15B15/02—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member
    • F15B15/06—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement
    • F15B15/065—Mechanical layout characterised by the means for converting the movement of the fluid-actuated element into movement of the finally-operated member for mechanically converting rectilinear movement into non- rectilinear movement the motor being of the rack-and-pinion type

Definitions

  • the invention relates to a pressure-actuated rotary drive or actuator according to the preamble of the main claim.
  • a device of this type is known from DE-B No. 2647385.
  • tilting moments occur during operation, which tend to cause the piston to tilt. This creates high frictional forces, which generate large surface pressures and thus severely impair the efficiency of the device and shorten the service life.
  • additional guides are provided in the known device which are laterally offset with respect to the drive guide, but whose effect is not satisfactory.
  • the object of the present invention is to increase the operational safety and the service life of the device and to improve its efficiency.
  • the guide provided with a toothed rack has, in its surface facing the cylinder wall, a groove which is arranged parallel and symmetrically to the cylinder axis and which receives the guide, which is offset by 180 ° around the longitudinal axis of the cylinder, in a form-fitting, sliding manner without a toothed rack of the other piston.
  • a cylinder is shown at 1 with two cylinder covers 2 and an inner line 3 and outer line 4 for the inflow and outflow of the medium.
  • two pistons 5 are arranged to be movable in the direction of the cylinder axis. They each have two guides 6 and 7, the guides 6 being provided with a toothed rack 8 which interact with a pinion of an actuating shaft 9.
  • the pistons 5 have circumferential sealing rings 10 and sliding rings 11 in the region of the piston crowns.
  • a sliding ring 12 is attached circumferentially to the cylinder inner wall, along which the guides 6 and the guides 7 slide together.
  • an additional channel 15 is provided which enlarges the remaining gap of the bore 3 and which runs parallel to the cylinder axis, so that the pressure medium during Inflow into the space formed between the piston crowns does not flow perpendicular to the direction of movement of the two, but rather in the direction of movement of the two pistons and thus supports the diverging movement.
  • bumps are attached to the outside of the piston crowns in order to fix springs which run coaxially to the cylinder axis and which are supported on the cylinder covers and return the pistons from the open position to the closed position that, for example, due to a leak with the pressure medium, pressure can no longer be built up.
  • the racks 8 are positively and non-positively fitted into the guides 6, so that they no longer leave their position without additional fasteners, even in alternating operation.
  • pins 16 can also be provided, which either glue or connect the toothed racks 8 to the guides 6 as dowel pins. If the toothed rack shape is less precisely matched to the shape of the guides 6, the toothed racks are held by means of screws, forces which want to lift the toothed racks out of the guides only have to be absorbed by the screws.
  • the guides 6 provided with a toothed rack 8 are provided in their surface facing the cylinder wall with a groove 23 oriented parallel and symmetrically to the cylinder axis, which guides the opposite guide 7 without toothed rack, offset by 180 ° about the longitudinal axis of the cylinder the other piston slidably receives.
  • each guide 6, apart from the groove 23, is equipped with symmetrically arranged guide surfaces 24 which are wide in the direction of the circumference of the cylinder inner wall and substantially exceed the width of the toothed racks.
  • the piston 5a is formed so that the seals 10a and g s 11 receiving guide surfaces 17 are aligned so that a far-reaching driving interengagement of auffactzubewegten piston is possible.
  • the cylinder cover 2 is then designed accordingly, so that there is still sufficient space for the air to enter.
  • FIG. 5 shows the embodiment of a device in which springs 20 per se belonging to the prior art are used. While in this embodiment the piston is designed, for example, in accordance with the embodiment in accordance with FIG. 1, but can also be designed in the same way in accordance with the embodiment in accordance with FIG to accomplish.
  • a damping device is additionally provided in a modification of the embodiment shown in FIGS. 1 to 5.
  • the cylinder space is penetrated by a web 25 which does not hinder the movements of the guides 6 and which serves to accommodate bores for the pressure medium supply and discharge lines and which at the same time represents the damper device on one side of the cylinder.
  • Bores 26 and 27 are provided both in the web 25 and in the cylinder cover 2.
  • the actual damping device 28 is installed in the piston 5 and, in the exemplary embodiment shown, is formed from two projections 29 and 30 projecting beyond the piston surfaces on both sides.
  • the plungers are dimensioned and arranged such that they are aligned with the bores 26 and 27 and can be guided into these bores 26 and 27, the bores having sealing rings, so that the plungers are tightly guided within the bores.
  • a throttle bore 31 is additionally provided and a bypass line 32, which is formed from a check valve, which in the illustrated embodiment consists of a ball 33 (FIG. 8), which is arranged in a ball cage which has a valve seat 34 .
  • the ball In the position shown in Fig. 8, the ball is in a position in which the bypass line is not closed, i. H. the ball does not rest on a valve seat, but, for example, on holding fingers, which allow the pressure medium to flow around it.
  • a bypass line 35 designed in the same way is provided in the cylinder cover 2 and a throttle bore 36 is also arranged in the cylinder cover 2, the two components 35 and 36 creating a connection between the cylinder space and the associated pressure medium supply and discharge line.
  • the ball of the check valve in the bypass line 35 bears against the valve seat, i. H. seals.
  • the pressure medium inlet and outlet lines can also be seen in the drawing, the line system, for example serving as a line, subsequently consisting of lines 401, 402 and 403, i.e. the compressed air supplied here leads to the rear of the plunger 30, lifts the valve ball 33 of the bypass line 32 from and can thereby apply pressure to the piston surface A of the piston 5.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Combined Devices Of Dampers And Springs (AREA)
  • Vehicle Body Suspensions (AREA)
  • Fluid-Damping Devices (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (10)

1. Dispositif d'entraînement en rotation ou de réglage actionné par agent de pression, comportant,
a) un cylindre (1 ) et deux pistons (5) pouvant aller et venir dans celui-ci en sens opposé, dans une dépendance mutuelle rigide,
b) un arbre de réglage (9) avec pignon, s'étendant transversalement à l'axe du cylindre, qui est disposé symétriquement par rapport aux deux pistons (5) et à l'axe du cylindre,
c) deux guides (6, 7) disposés sur chacun des deux pistons (5), s'étendant parallèlement à l'axe du cylindre en partant du fond des pistons et s'appliquant par-dessus l'arbre de réglage (9), lesdits guides présentant leur côté extérieur des surfaces de guidage guidant le piston dans le cylindre (1 ) et étant placés à peu près à l'opposé l'un de l'autre relativement à l'axe longitudinal du cylindre, l'un des guides (6) présentant à son côté intérieur une crémaillère (8) (guide d'entraînement) qui coopère avec le pignon, caractérisé par le fait que les guides (6) munis d'une crémaillère (8) présentent chacun, dans leur surface tournée vers la paroi du cylindre, une gorge (23) disposée parallèlement à l'axe longitudinal du cylindre et symétriquement par rapport à cet axe et qui loge par encastrement avec glissement le guide opposé sans crémaillère (7) de l'autre piston, décalé de 180° autour de l'axe longitudinal du cylindre.
2. Dispositif selon la revendication 1, caractérisé par le fait que les guides (6) munis de la crémaillère (8) présentent, dans la direction de la circonférence de la paroi intérieure du cylindre, des surfaces de guidage larges (24), disposées symétriquement et dépassant notablement la largeur des crémaillères.
3. Dispositif selon l'une des revendications 1 ou 2, caractérisé par le fait que le guide (7) sans crémaillère est disposé de façon librement mobile dans l'espace formé par la gorge (23).
4. Dispositif selon l'une des revendications précédentes, dans lequel les crémaillères (8) sont adaptées par encastrement et sous l'action d'une force dans le guide (6) qui les porte, caractérisé par des goupilles (16) disposées dans des perforations alignées formées sur les crémaillères (8) et sur les guides (6).
5. Dispositif selon la revendication 4, caractérisé par le fait que les goupilles (16) sont collées.
6. Dispositif selon l'une des revendications précédentes, présentant une ouverture d'alimentation (3) destinée à l'agent de pression qui débouche dans le cylindre (1 ) entre les fonds de piston et un canal supplémentaire (15) se raccordant à cette ouverture d'alimentation (3), caractérisé par le fait que le canal supplémentaire (15) est formé d'une rainure parallèle à l'axe longitudinal du cylindre, située dans le côté intérieur de la paroi du cylindre, qui s'étend jusqu'au voisinage du fond de piston quand celui-ci se trouve complètement à l'intérieur dans sa position de point mort.
7. Dispositif selon la revendication 1, caractérisé par un dispositif d'amortissement (28) faisant saillie sur au moins un piston (5) au-dessus des deux surfaces de piston, pour amortir les mouvements finaux des pistons (5).
8. Dispositif selon la revendication 7, caractérisé par une traverse (25) ne gênant pas le mouvement des guides (6 et 7), par des perforations (26, 27) prévues l'une dans la traverse (25) et l'autre dans le couvercle de cylindre (2) adjoint au piston (5) muni du dispositif d'amortissement (28) et qui sont en communication avec les conduits d'amenée et d'évacuation d'agent de pression (401, 501 ) et par des poussoirs (29, 30) faisant saillie sur les deux côtés du piston (5), alignés sur les perforations et qui, dans les positions extrêmes, s'engagent de façon étanche dans les perforations (26,27).
9. Dispositif selon la revendication 8, caractérisé par des perforations d'étranglement (31, 36) reliant les cavités de cylindre, de part et d'autre de la surface de piston, aux conduits adjoints d'amenée et d'évacuation d'agent de pression.
10. Dispositif selon la revendication 9, caractérisé par des conduits de dérivation (32, 35) reliant les cavités de cylindre, de part et d'autre des surfaces de piston, aux conduits adjoints d'amenée et d'évacuation d'agent de pression et équipés de valves antiretour.
EP83102387A 1982-03-19 1983-03-11 Dispositif d'actionnement rotatif à fluide sous pression Expired EP0089568B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83102387T ATE15402T1 (de) 1982-03-19 1983-03-11 Druckmittelbetaetigte drehantriebsstellvorrichtung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3210050 1982-03-19
DE3210050 1982-03-19

Publications (2)

Publication Number Publication Date
EP0089568A1 EP0089568A1 (fr) 1983-09-28
EP0089568B1 true EP0089568B1 (fr) 1985-09-04

Family

ID=6158697

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83102387A Expired EP0089568B1 (fr) 1982-03-19 1983-03-11 Dispositif d'actionnement rotatif à fluide sous pression

Country Status (6)

Country Link
EP (1) EP0089568B1 (fr)
AT (1) ATE15402T1 (fr)
DE (1) DE3360703D1 (fr)
HK (1) HK27586A (fr)
MY (1) MY8600424A (fr)
SG (1) SG95885G (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3443302A1 (de) * 1984-08-22 1986-03-06 Christian 5140 Erkelenz Kubanek Stroemungsmittelbetaetigter schwenkantrieb
JP6332688B2 (ja) * 2014-09-02 2018-05-30 Smc株式会社 ロータリアクチュエータ
DE102019204446A1 (de) * 2019-03-29 2020-10-01 Festo Se & Co. Kg Fluidbetätigte Drehantriebsvorrichtung
CN113062894B (zh) * 2021-03-16 2022-07-15 中煤科工集团重庆研究院有限公司 一种用于狭窄空间的摆动马达

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1229848B (de) * 1963-01-14 1966-12-01 Sihn Kg Wilhelm Jun Vorrichtung zur hydraulisch abgebremsten pneumatischen Bewegung von Maschinenteilen
US3246581A (en) * 1963-10-23 1966-04-19 Flo Tork Inc Air actuator
FR1461217A (fr) * 1965-04-23 1966-12-10 Mathews Engineering Company Lt Appareil moteurs rotatifs actionnés par un fluide sous pression
NL174580C (nl) * 1975-10-21 1984-07-02 El O Matic Bv Inrichting voor een zwenkbeweging veroorzakende aandrijving.
GB1548683A (en) * 1976-10-06 1979-07-18 Norbo Pneumatics Ltd Pneumatic actuators
US4281588A (en) * 1979-06-18 1981-08-04 Sprague Devices, Inc. Reciprocating piston fluid powered motor

Also Published As

Publication number Publication date
EP0089568A1 (fr) 1983-09-28
SG95885G (en) 1987-09-18
ATE15402T1 (de) 1985-09-15
DE3360703D1 (en) 1985-10-10
HK27586A (en) 1986-04-25
MY8600424A (en) 1986-12-31

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