EP0442908B1 - Cylindre hydraulique avec dispositif amortisseur - Google Patents

Cylindre hydraulique avec dispositif amortisseur Download PDF

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Publication number
EP0442908B1
EP0442908B1 EP89912017A EP89912017A EP0442908B1 EP 0442908 B1 EP0442908 B1 EP 0442908B1 EP 89912017 A EP89912017 A EP 89912017A EP 89912017 A EP89912017 A EP 89912017A EP 0442908 B1 EP0442908 B1 EP 0442908B1
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EP
European Patent Office
Prior art keywords
cushioning
piston
fluid
cylinder
power
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
EP89912017A
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German (de)
English (en)
Other versions
EP0442908A1 (fr
Inventor
Sven-Erik Overstrom
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.)
OVERSTROM SVEN ERIK
Original Assignee
OVERSTROM SVEN ERIK
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Publication date
Application filed by OVERSTROM SVEN ERIK filed Critical OVERSTROM SVEN ERIK
Publication of EP0442908A1 publication Critical patent/EP0442908A1/fr
Application granted granted Critical
Publication of EP0442908B1 publication Critical patent/EP0442908B1/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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/076—Combined pneumatic-hydraulic systems with pneumatic drive or displacement and speed control or stopping by hydraulic braking
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/47—Flow control in one direction only
    • F15B2211/473—Flow control in one direction only without restriction in the reverse direction
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/755—Control of acceleration or deceleration of the output member
    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/80—Other types of control related to particular problems or conditions
    • F15B2211/885—Control specific to the type of fluid, e.g. specific to magnetorheological fluid
    • F15B2211/8855—Compressible fluids, e.g. specific to pneumatics

Definitions

  • This invention relates to a fluid-power cylinder provided with a cushioning device for cushioning the movements of the piston in the cylinder.
  • Fluid-power cylinders often require a cushioning device which retards the piston at one or both ends of its stroke within the cylinder.
  • a residual volume of fluid trapped in a cushioning compartment is allowed to escape from the cushioning compartment only through a restricted discharge passage in order to retard the movement of the piston during the final portion of its stroke.
  • a single cushioning piston is provided on one side of a power piston member which is reciprocable between opposite end positions in a power cylinder member.
  • the cushioning piston is received in a cushioning cylinder provided at one end of the power cylinder member so that fluid is trapped in a cushioning compartment defined by the cushioning cylinder.
  • a restricted discharge passage for the trapped fluid is formed by grooves or bores which communicate with the narrow annular gap between the cushioning piston and the wall of the cushioning cylinder.
  • a problem which is present in this and many other prior art cushioning devices is that the cushioning effect is dependent on the dimensional accuracy of components which move relative to one another and define the restricted discharge passage between them. Wear of these components also affects the cushioning effect which may therefore be gradually reduced in the course of time.
  • An object of this invention is to provide a fluid-power cylinder provided with a cushioning device which is improved in respect of the above-mentioned problems.
  • a fluid-power cylinder comprising a power cylinder member, a power piston member, which includes a power piston body reciprocable in the power cylinder member between opposed end positions and a piston rod secured to the power piston body and projecting from one end of the power cylinder member, and a device for cushioning the relative movements of the power cylinder member and the power piston member at the end positions, characterised by the following features:
  • the invention is embodied in a double-acting pneumatic cylinder provided with a hydraulic device for cushioning the stroke of the power piston member of the cylinder at both end positions or stroke ends.
  • Two separate cushioning cylinders are provided within a tubular piston rod of the power piston member and reciprocate therewith, and a dual cushioning piston is stationary with respect to the power cylinder member in which the power piston member is reciprocable.
  • the invention may be embodied in other types of fluid-power cylinders, e.g. cylinders in which the same kind of fluid is used both as working fluid and cushioning fluid.
  • the illustrated fluid-power cylinder comprises a power cylinder member generally designated by 11 and a power piston member 12 which is reciprocable in the power cylinder member. It also comprises a hydraulic cushioning device including a pair of cushioning cylinders 13, a dual cushioning piston 14 with an associated support tube 15 and a cushioning liquid reservoir 16.
  • Main components of the power cylinder member 11 are a cylindrical tube 20 of circular cross-section and front and rear end walls 21 and 22, respectively, which sealingly close the ends of the tube and are provided with connectors 23 and 24, respectively, through which the working fluid, namely compressed air, is supplied and discharged.
  • the rear end wall 22 is made integral with the cushioning liquid reservoir 16.
  • Mounted on the reservoir 16 are a pair of aligned pivot pins 25 by which the power cylinder member 11 may be pivotally mounted on a bracket (not shown).
  • the power piston member 12 comprises a power piston body 26 which sealingly engages the inner wall of the cylinder tube 20 and divides the cylinder space between the end walls into front and rear cylinder compartments 27 and 28, respectively, which communicate with respectively the front air connector 23 and the rear air connector 24, and a tubular piston rod 29, one end of which, the rear end, is secured to the power piston body and projects forwardly through a sliding seal in the front end wall 21 of the power cylinder member 11.
  • an eye bolt 30 Secured to the front end of the piston rod 29 is an eye bolt 30, through which the power piston member 12 may be connected to a part to be actuated, such as a door or the like.
  • the end positions of the reciprocating movements of the power piston member 12 in the power cylinder member 11 are defined by a pair of abutments which are provided on the cylinder end walls 23 and 24 and are adapted to be engaged by the power piston body 26.
  • the cushioning cylinders 13 of the cushioning device are formed by front and rear cylindrical sleeves which are secured in the hollow piston rod 29 adjacent respectively the front and the rear end thereof.
  • the adjacent ends of the two sleeves are internally bevelled or widened.
  • the sleeves 13 together with the front part of the piston rod 29 and the power piston body 26 the sleeves 13 define a pair of cushioning compartments 31A, 31B, which are open towards the interior 32 of the piston rod at their outer, adjacent ends but are otherwise closed.
  • the dual cushioning piston 14 is secured to the front end of the support tube 15 which in turn has its rear end secured to the cylinder end wall 22 and is in constant open communication with a cushioning liquid compartment 33 in the cushioning liquid reservoir 16.
  • the support tube 15 extends through a sliding seal 34 in the power piston body 26 and through the rear cushioning cylinder sleeve 13.
  • the cushioning piston 14 comprises a front piston section 14A and a rear piston section 14B.
  • the front cushioning piston section 14A is moved inwardly in the front cushioning cylinder compartment 31A to the vicinity of the inner end or bottom of the compartment.
  • the rear cushioning piston section 14B is moved inwardly in the rear cushioning cylinder compartment 31B to the vicinity of the inner end or bottom thereof.
  • the dual cushioning piston 14 comprises a dumbbell-shaped metal body, the enlarged end portions of which form the front and rear cushioning piston sections 14A, 14B and have a diameter slightly smaller than the inner diameter of the cushioning cylinder sleeves 13. The difference in diameters is sufficient to permit a substantially unrestricted liquid flow through the gap between each cushioning cylinder sleeve 13 and the associated cushioning piston section 14A, 14B received therein.
  • Each cushioning piston section 14A, 14B is provided with an external circumferential groove 35A, 35B, which accommodates a frusto-conical sealing ring 36A, 36B of relatively soft material.
  • the sealing rings are opposed such that their larger ends, which are adapted to engage sealingly the interior wall of the cushioning cylinder sleeves 13, are directed away from one another, i.e. towards the inner ends of the cushioning compartments.
  • a central axial passage 37 which is in constant open communication with the interior of the support tube 15 and thus with the cushioning liquid compartment 33. Inserted in the front end of this passage is a calibrated restrictor 38. By way of a transverse passage 39 the central portion of the passage 37 is in constant unrestricted communication with the space around the cushioning piston.
  • an axial passage 40 which is in constant unrestricted communication with the piston rod space 32 and is in constant but restricted communication with the space around the cushioning piston, the last-mentioned communication being by way of a calibrated restriction 41 located between the two sealing rings a small distance from the sealing ring 36B.
  • the piston rod space 32 and the spaces communicating with it are always filled with the cushioning liquid.
  • the front cushioning cylinder compartment 31A defined in front of the front cushioning piston section 14A expands.
  • the cushioning compartment 31A is successively filled with cushioning liquid which flows against very little resistance into the compartment past the sealing ring 36A because this sealing ring is pressed into its groove 35A.
  • the sealing ring 36A acts as a valve (one-way valve) which opens automatically to permit liquid flow into the front cushioning cylinder compartment 31A.
  • the rear cushioning piston section 14B When the power piston member 12 approaches its outer end position, the rear cushioning piston section 14B is received in the rear cushioning cylinder sleeve 13.
  • the rear sealing ring 36B because of its frusto-conical shape, is caused to engage sealingly the inner wall of the sleeve (one-way valve action).
  • the only path through which the cushioning liquid trapped in the rear cushioning cylinder compartment 31B can escape is therefore formed by the passage 40 containing the calibrated restriction 41. By virtue of its cross-sectional area, this restriction determines the rate at which the power piston member 12 continues its movement to the outer end position.
  • the calibrated restrictor 38 in the front cushioning piston section 14A determines the rate at which the final portion of this retraction takes place.
  • the cushioning device In use, there is no wear of those elements, namely the restrictors 38 and 41, of the cushioning device which determine the speed at which the power piston member 12 moves near the end positions, assuming that the forces acting on the power piston member 12 are given. These elements therefore do not undergo any change in respect of their predetermined cross-sectional flow area during the useful life of the cushioning device. Moreover, because it is also easy to design the restrictors with the desired cross-sectional flow area and to ensure that the cushioning liquid trapped in the cushioning cylinder compartments cannot escape except through the restrictors, the cushioning device can be designed to provide the desired cushioning effect. Moreover, it is easy to ensure that any wear that takes place does not cause the cushioning effect to change over the time in a way that is difficult to compensate. If the cushioning effect of the device should be reduced because of wear of the sealing rings of the cushioning pistons, the desired cushioning effect can readily be restored by replacement of the sealing rings.
  • calibrated restrictors are fixed, but it is of course within the scope of the invention to make them adjustable.
  • the cushioning liquid reservoir 16 the main body of which is made integral with the rear cylinder end wall 22, has a substantially circular cylindrical exterior shape and is sealingly closed at its rear end by means of a screw-threaded cover 42.
  • the two aligned pivot pins 25 are secured to a circular clamp 43 which is held in position about the cushioning liquid reservoir 16 by means of a bolt 44 which is passed through a pair of outwardly bent flanges 45 of the clamp.
  • the clamp 43 is secured axially in its position, and possibly also against rotation, on the cushioning liquid reservoir by a ridge 46 on the inner side of the clamp or by any other suitable projection which engages a corresponding groove or recess 47 on the outer side of the cushioning liquid reservoir 16.

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)
  • Braking Arrangements (AREA)

Abstract

Le cylindre hydraulique décrit, qui comprend un élément à cylindre moteur (11) et un élément à piston moteur (12) pouvant effectuer un mouvement de va-et-vient dans ledit élément à cylindre entre des positions terminales, est pourvu d'un dispositif servant à amortir les mouvements relatifs de l'élément à piston moteur et de l'élément à cylindre moteur à proximité des positions terminales. Le dispositif amortisseur comprend un cylindre amortisseur (13) pouvant se déplacer conjointement avec l'élément à piston moteur (12) et un piston amortisseur (14), lequel est fixe par rapport à l'élément à cylindre moteur (11) et peut être reçu dans le cylindre amortisseur par rapport auquel il effectue un mouvement axial, de façon à définir un compartiment de cylindre amortisseur (31A, 32B) présentant un passage de décharge restreint (37/38, 40/41). Un joint d'étanchéité (36A, 36B) situé sur le piston amortisseur (14) fait office de soupape unidirectionnelle empêchant l'écoulement du fluide amortisseur entre le piston amortisseur (14) et le cylindre amortisseur (13), lorsque le piston amortisseur effectue un mouvement vers l'intérieur dans le compartiment de cylindre amortisseur (31A, 31B), et réduit ainsi le volume du compartiment, tout en permettant un écoulement du fluide sensiblement non restreint lorsque le piston amortisseur effectue un mouvement vers l'extérieur.

Claims (7)

  1. Cylindre hydraulique comprenant
       un cylindre moteur (11)
       un piston moteur (12), qui comprend un corps de piston moteur (25) allant et venant dans le cylindre moteur entre des positions d'extrémité opposées et une tige de piston (29) fixée au corps de piston moteur et se projetant depuis une extrémité du cylindre moteur, et
       un dispositif pour amortir les mouvements du piston moteur (12) et du cylindre moteur (11) l'un par rapport à l'autre aux positions d'extrémité,
       caractérisé en ce que
       le dispositif amortisseur comprend
    (a) pour chaque position d'extrémité un piston amortisseur (14A, 14B) sur le cylindre moteur (11) et un cylindre amortisseur (13) sur le piston moteur (12), le cylindre amortisseur (13) définissant un compartiment amortisseur (31A, 31B) comportant une extrémité interne fermée et une extrémité externe ouverte dans lequel le piston amortisseur peut être reçu lorsqu'il approche de la position d'extrémité, et
    (b) un réservoir de fluide amortisseur (16) en communication de fluide constante avec les deux compartiments amortisseurs (31A, 31B), un passage d'évacuation restreint (37/38, 40/41) constituant le seul passage d'échappement du fluide amortisseur du compartiment amortisseur associé au réservoir de fluide amortisseur lorsque le piston amortisseur est reçu dans le cylindre amortisseur,
    - la tige de piston (29) du piston moteur (12) est creuse, son intérieur étant en communication libre constante avec le réservoir de fluide amortisseur (16),
    - les cylindres amortisseurs (13) sont situés au sein de la tige de piston du piston moteur (12) et espacés axialement, les extrémités de cylindres adjacents étant ouvertes pour définir les extrémités externes ouvertes des compartiments amortisseurs (31A, 31B),
    - chaque piston amortisseur (14A, 14B) est doté extérieurement d'un joint étanche (36A, 36B)au fluide adapté à engager de manière étanche la paroi interne du cylindre amortisseur associé (13) lorsque le piston amortisseur se déplace dans le cylindre amortisseur vers l'extrémité interne du compartiment amortisseur (31A, 31B) et à permettre un écoulement de fluide sensiblement libre entre le piston amortisseur et la paroi interne du cylindre amortisseur lorsque le piston amortisseur se déplace dans le cylindre amortisseur vers l'extrémité externe du compartiment amortisseur, et
    - le passage d'évacuation (37/38, 40/41) est un passage qui est ménagé dans le piston amortisseur et contourne le joint étanche au fluide (36A, 36B).
  2. Cylindre hydraulique selon la revendication 1, caractérisé en ce que le passage d'évacuation (37/38, 40/41) comprend un dispositif de restriction d'écoulement calibré (38, 41).
  3. Cylindre hydraulique selon la revendication 2, caractérisé en ce que le dispositif de restriction d'écoulement (38) est situé sur un élément de restriction d'écoulement monté avec possibilité de remplacement sur le piston amortisseur (14A).
  4. Cylindre hydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le joint étanche au fluide (36A, 36B) peut être engagé avec la paroi interne du cylindre amortisseur (13) sous l'effet de la pression de fluide agissant axialement sur le joint étanche au fluide et dirigée vers l'extrémité interne du compartiment amortisseur (31A, 31B), et peut être déplacé loin de cette paroi sous l'effet de la pression de fluide agissant axialement sur le joint étanche au fluide vers l'extrémité externe du compartiment amortisseur.
  5. Cylindre hydraulique selon la revendication 4, caractérisé en ce que le joint étanche au fluide (36A, 36B) est un joint annulaire tronconique en un matériau élastique, l'extrémité la plus grande du joint annulaire donnant sur l'extrémité interne du compartiment amortisseur (31A, 31B).
  6. Cylindre hydraulique selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le réservoir de fluide amortisseur (16) constitue une extension axiale sensiblement cylindrique de l'autre extrémité du cylindre moteur (11).
  7. Cylindre hydraulique selon la revendication 6, caractérisé en ce que la majeure partie du réservoir de fluide amortisseur (16) est d'un seul tenant avec une paroi d'extrémité (22) du cylindre moteur (11).
EP89912017A 1988-11-08 1989-11-02 Cylindre hydraulique avec dispositif amortisseur Expired - Lifetime EP0442908B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
SE8804035 1988-11-08
SE8804035A SE465529B (sv) 1988-11-08 1988-11-08 Tryckluftcylinder med anordning foer aendlaegesdaempning
PCT/SE1989/000624 WO1990005245A1 (fr) 1988-11-08 1989-11-02 Cylindre hydraulique avec dispositif amortisseur

Publications (2)

Publication Number Publication Date
EP0442908A1 EP0442908A1 (fr) 1991-08-28
EP0442908B1 true EP0442908B1 (fr) 1994-04-20

Family

ID=20373885

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89912017A Expired - Lifetime EP0442908B1 (fr) 1988-11-08 1989-11-02 Cylindre hydraulique avec dispositif amortisseur

Country Status (5)

Country Link
EP (1) EP0442908B1 (fr)
CA (1) CA2002278A1 (fr)
DE (1) DE68914848T2 (fr)
SE (1) SE465529B (fr)
WO (1) WO1990005245A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE0102331D0 (sv) 2001-06-29 2001-06-29 Biacore Ab Flow cell method

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE347046B (fr) * 1969-11-07 1972-07-24 Monsun Tison Ab

Also Published As

Publication number Publication date
SE465529B (sv) 1991-09-23
CA2002278A1 (fr) 1990-05-08
SE8804035L (sv) 1990-05-09
SE8804035D0 (sv) 1988-11-08
DE68914848T2 (de) 1994-11-03
DE68914848D1 (de) 1994-05-26
WO1990005245A1 (fr) 1990-05-17
EP0442908A1 (fr) 1991-08-28

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