EP1729015A1 - Dispositif entraîné par un fluide - Google Patents

Dispositif entraîné par un fluide Download PDF

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Publication number
EP1729015A1
EP1729015A1 EP05011977A EP05011977A EP1729015A1 EP 1729015 A1 EP1729015 A1 EP 1729015A1 EP 05011977 A EP05011977 A EP 05011977A EP 05011977 A EP05011977 A EP 05011977A EP 1729015 A1 EP1729015 A1 EP 1729015A1
Authority
EP
European Patent Office
Prior art keywords
plunger
fluid
working
piston
fluid device
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.)
Withdrawn
Application number
EP05011977A
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German (de)
English (en)
Inventor
Mark Dipl.-Ing.(FH) Hokenmaier
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.)
Festo SE and Co KG
Original Assignee
Festo SE and Co KG
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 Festo SE and Co KG filed Critical Festo SE and Co KG
Priority to EP05011977A priority Critical patent/EP1729015A1/fr
Publication of EP1729015A1 publication Critical patent/EP1729015A1/fr
Withdrawn legal-status Critical Current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
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/22—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke
    • F15B15/225—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke with valve stems operated by contact with the piston end face or with the cylinder wall

Definitions

  • the invention relates to a fluid device, in particular a fluid-actuated drive, with a housing containing a linearly displaceable working piston, which defines together with at least one axially opposite housing-side end wall a working chamber into which an outlet wall passing through discharge channel opens with a working piston axially facing outflow opening , wherein the working piston covers the outflow opening at approximately the stroke of approaching stroke movement before reaching its stroke end position and is braked in its further movement in a subsequent damping phase due to the building up in the working chamber back pressure.
  • a designed as a fluid-operated drive fluid device of this kind is from the DE 39 20 293 C2 known.
  • the fluid device is equipped with means that cause a cushioning of the piston.
  • the piston When the piston is displaced in the direction of an end wall, fluid is expelled from the volume-reducing working chamber through a housing-fixed outflow channel. Before reaching the stroke end position, the piston covers the associated outflow opening, so that the displaced pressure medium can only flow off throttled over a bypass channel. Due to the reduced flow rate, a back pressure builds up in the working chamber, which causes a slowing of the piston movement, so that the piston reaches the stroke end position with greatly reduced kinetic energy.
  • the discharge opening is closed during the damping phase by a spring-elastically suspended on the working piston cover.
  • the resilient suspension allows the working piston a relative movement with respect to the cover member carried by it, if this is prevented by its abutment against the end wall on its further movement.
  • a disadvantage of this design is the complex structure of the working piston and the condition caused by the covering in comparison to a conventional piston increased mass to be moved.
  • the piston movement in particular at high accelerations oscillations in the moving system can be caused, which impair the functionality and in particular can cause a non-reproducible beginning of the damping phase.
  • the discharge opening is located on the end face of a penetrated by the discharge plunger, which projects from the working wall in the working chamber from the end wall and in the damping phase counteracting him in the direction of the working piston acting restoring force relative to the end wall is pushed back.
  • the piston construction is considerably simplified.
  • the moving during the damping phase element is now a ram mounted on the housing, which is not moved outside the damping phase with the piston, so that the tendency to oscillate significantly reduced and the precision of the damping process is increased.
  • the beginning of the damping phase is characterized in that the incoming working piston closes the discharge opening, so that a back pressure reducing the piston speed can build up in the working chamber.
  • the plunger is pushed back solely by the thrust of the working piston or supported by the back pressure built up in the working chamber until the working piston has reached its desired Hubendlage.
  • the fluid device is in particular a fluid-operated drive, for example a pneumatic cylinder.
  • a shock absorber would also be possible.
  • EP 0 318 671 B1 already a pneumatic shock absorber, in which the moving piston cooperates with a housing side mounted plunger.
  • this plunger acts only as a valve member for venting the working chamber and also contains no discharge channel.
  • the restoring force acting on the plunger is expediently delivered by a spring device which, outside the damping phase, transforms the plunger into a basic position defined by the interaction with housing-mounted stop means biases.
  • the spring device could for example be a compressed air spring.
  • a bypass channel which bypasses the plunger-side outflow channel section and is equipped with a throttle restriction is present, through which the pressure medium displaced from the working chamber flows off during the damping phase.
  • the discharge opening remains closed from the beginning of the damping phase by the end face on the plunger piston. If it is a throttle point with adjustable throttling intensity, for example formed by an adjustable throttle screw, the desired damping characteristic can be specified application-specific variable.
  • the bypass channel may be a separate from the plunger separate channel, which runs in the end wall of the housing.
  • the latter allows a path-dependent variation of the attenuation intensity very simply by designing the outer contour of the plunger so that the cross-section of the gap-like Gap varies depending on the axial position of the plunger.
  • a gradually decreasing cross-section when pushing back the plunger can be provided, with the needs corresponding, for example, to a linear or progressive characteristic curve.
  • damping measures is located on the movable plunger at least one during the damping phase of the pressure prevailing in the working chamber fluid pressure opposite to the direction of action of the restoring force acted upon fluid loading surface.
  • This configuration can be used in particular to obtain a pressure-controlled damping.
  • the discharge channel expediently provides the only Abström réellekeit for the trapped in the working chamber pressure medium.
  • On an additional bypass duct with throttle point is advantageously dispensed with.
  • the plunger expediently has a plunger piston, enlarged in cross-section, for defining the fluid loading surface.
  • the plunger piston may be wholly or partially formed by an annular seal. These may simultaneously act as a check valve member to increase the flow area when an inversion of the piston movement is to be caused by an opposite fluid flow.
  • fluid-operated drives in the form of linear drives.
  • inventive concept would also be applicable to rotary actuators.
  • it is pneumatic drives, although an operation with hydraulic media would be possible.
  • the fluid device has a housing 1, which delimits an elongated interior 2, in which a working piston 3 is arranged linearly displaceable.
  • the working piston 3 is provided with an annular seal assembly 4 which is slidably sealingly abutting the peripheral peripheral surface of the inner space 2, so that the latter is divided under sealing into a first and second working chamber 5, 6.
  • the peripheral boundary of the inner space 2 takes over a pipe section 7 of the housing 1.
  • a pipe section 7 of the housing 1 At both end faces of each first or second end wall 8, 9 is arranged, the respectively associated first and second working chamber 5, 6 on the working piston 3 opposite axial side concludes.
  • Each working chamber 5, 6 communicates with a wall of the housing 1 passing through the first and second control channel 12, 13, the other ends to the outer surface of the housing 1 and fed via the fluidic pressure medium of choice or can be discharged to the working piston 3 in the to shift one or the other direction.
  • the movement of the working piston 3 can be tapped outside of the housing 1 on a motion-coupled to the power piston 3 driven part 14 which is in the embodiment a fixed to the piston 3 piston rod which passes through the first end wall 8 under seal and guided sliding.
  • the working piston 3 can be moved between two stroke end positions, in which it rests against the axial inner surface of the respective associated end wall 8, 9 facing it.
  • the first stroke end position, in which the working piston 3 rests against the second end wall 9, is apparent from FIG.
  • the opposite second stroke end position is illustrated in FIG.
  • the drive is equipped with damping means 16, which cause a cushioning when the working piston 3 moves to the second stroke end position.
  • damping means 16 are associated with the first end wall 8 and combined with the first control channel 12.
  • no fluidic cushioning is provided in the embodiment and contains the second end wall 9 therefore no comparable damping means.
  • a corresponding equipment would readily be possible, the design would then correspond to that of the damping means 16, so that can be dispensed with a separate description at this point.
  • the two control channels 12, 13 combine in each case the function of an inflow of pressure medium into the associated working chamber 5, 6 enabling inflow channel 12a and 13a and the outflow of the displaced by the moving working piston 3 pressure medium outflow channel 12b, 13b. Since the functionality as a discharge channel is particularly important for the cushioning, the description of the damping means 16 initially takes place mainly from the point of view of the functionality of a discharge channel 12b.
  • the first working chamber 5 facing the first end wall 8 includes in extension of the first working chamber 5 and laterally offset from the piston rod 14 is an axially In it are the rear end portion of a plunger 18 which projects axially into the first working chamber 5 and thereby projects the working piston 3.
  • the plunger 18 is linearly adjustable relative to the first end wall 8 in a direction parallel to the direction of movement of the working piston 3 direction of movement back and forth.
  • the piston movement 22 and the plunger movement 23 is illustrated by a double arrow.
  • the receiving chamber 17 is divided from the adjacent first working chamber 5 by a partition wall 24 formed as an integral part of the first end wall 8, which has an opening 25 which is penetrated by the plunger 8 slidably.
  • the opening 25 extends along at least part of the circumference of the plunger 18 and can cause a displacement guide in this way.
  • the outflow channel 12b has a plunger 18 preferably coaxial over its entire length passing through the plunger-side outflow channel 26. This opens at the working piston 3 facing the front end of the plunger 18 with a discharge opening 27 into the first working chamber 5.
  • the plunger-side discharge channel section 26 communicates with a region of the receiving chamber 17 which is in constant communication with a further housing-side outflow channel section 28, which can be connected to a pressure sink, for example to the atmospheric environment or to a tank.
  • a further housing-side outflow channel section 28 opens to the outer surface of the housing 1 and is connected in the operation of the fluid device to a control valve device, via which either a connection to a pressure source or a pressure sink can be made.
  • Connection means 32 of the housing side Abströmkanalabiteses 28 allow the direct attachment of the control valve device or the connection of a leading to the control valve means fluid line.
  • a mechanical spring device 33 which acts on the plunger 18 in its extension direction 34, ie in the direction of the working piston 3 and which is supported on a housing-fixed support surface 35.
  • the spring device 33 is, in particular, a compression spring, preferably a helical compression spring coaxial with the plunger 18.
  • the spring device 33 engages the back of the plunger 18 and is aligned in extension to this.
  • the plunger 18 In the state not acted upon by the working piston 3, the plunger 18 is biased by the spring device 33 under prestress into a basic position extended as far as possible into the first working chamber 5. This is apparent from Figures 2, 3 and 6.
  • the basic position is defined by in the stroke of the plunger 18 projecting housing-mounted stop means 36 against which the plunger 18 rests in the basic position.
  • the stop means 36 are formed by the partition wall 24, against which the plunger 18 located in the basic position rests with a radial projection 37.
  • the spring device 33 exerts on the plunger 18 constantly oriented in the extension direction 34 restoring force F R.
  • This is expediently variably adjustable.
  • a simultaneously serving as a rear wall for the receiving chamber 17 adjusting member 38 is provided, which is rotatable and thereby axially adjustable in an internally threaded portion 42 of the receiving chamber 17 is screwed in and on which the support surface 35 is located.
  • the cover 44 may be part of a piston-resistant rubber-elastic body 46.
  • the covering surface 44 is expediently designed as an annular surface concentric with the piston longitudinal axis, with a radius corresponding to the distance of the outlet opening 27 from the piston longitudinal axis.
  • the damping means 16 are designed to obtain a pressure-controlled damping phase.
  • the plunger 18 in the region of its rear side within the receiving chamber 17 has a designated as a plunger piston portion 47 in comparison to the opening 25 passing through tubular plunger portion larger outside diameter.
  • the plunger piston 47 divides the receiving chamber 17 into an independent outer receiving chamber section 48 connected to the housing-side outflow channel section 28 and the spring device 33 at an independent inner receiving chamber section 49.
  • the inner receiving chamber section 49 is constantly in contact with the adjacent first working chamber 5 in connection, which happens in the embodiment via a partition wall 24 passing through opening 52.
  • the opening 52 may be formed as in the embodiment of a radial extension of the penetrated by the plunger 18 opening 25.
  • the end face of the plunger piston 47 delimiting the axially inner receiving chamber section 49 forms a fluid loading surface 53, which is constantly acted upon by the opening 52 through the prevailing in the first working chamber 5 fluid pressure.
  • This fluid application has an effect on the instantaneous plunger position during the damping phase, because a fluidic actuating force Fs counteracting the restoring force F R results from the fluid loading surface 53 in conjunction with the fluid pressure acting against it against the extension direction 34.
  • the height of the fluidic force Fs depends on the height of the currently prevailing in the first working chamber 5, due to the obstruction of the outflow building back pressure and increases with increasing approach of the working piston 3 to the second stroke end position.
  • the plunger 18 displaces, without being pushed directly by the working piston 3, relative to the latter against the extension direction 34 and consequently lifts away from the working piston 3 to a certain extent.
  • the outflow opening 27 is released, which has an immediate pressure reduction in the first working chamber 5 via the outflow channel 12b result, so that the working piston 3 closes the outflow opening 27 again due to the thereby again decreasing force Fs.
  • the setting of the counter-pressure to be adjusted can be changed in the embodiment by varying the bias of the spring device 33.
  • the adjusting member must be screwed more or less far into the receiving chamber 17.
  • pressure medium is fed from the outside into the first control channel 12, so that it no longer functions as a discharge channel 12b but as an inflow channel 12a.
  • the pressure medium flows in this case via the housing-side outflow channel section 28 into the outer receiving chamber section 48 and from there into the plunger-side outflow channel section 26, so that it acts on the covering surface 44 of the working piston 3 with a positioning force.
  • check valve means 54 are provided which allow the pressure medium to flow into the first working chamber 5, bypassing the ram-side outflow channel section.
  • the check valve means 54 in the embodiment of the plunger piston 47 at least partially consists of a coaxially on the outer periphery of the plunger 18 arranged annular seal 55 which has an elastically deformable sealing lip which abuts in radially inwardly bendable manner on the peripheral surface of the receiving chamber 17.
  • the seal 55 has a conical shape with an obliquely outwardly widening cross section in the extension direction 34 so that it is bent inwardly when the pressure prevailing in the outer receiving chamber section 48 is greater than the pressure prevailing in the inner receiving chamber section 49.
  • annular seal 55 If there is a reverse pressure difference at the annular seal 55, the sealing lip is pressed against the inner circumference of the receiving chamber 17 reinforced and prevents a fluid transfer into the outer receiving chamber 48.
  • the annular seal 55 also contributes to the definition of the Fluidbeetzyerungs character 53 and forms a part of the plunger 47th
  • the pressure-regulating characteristic can be avoided in the exemplary embodiment of FIGS. 1 to 5 by preventing the build-up of an excessively high counter-pressure in the first working chamber 5. This is done by means of an optional, indicated in phantom in Figures 3 and 5 only by dash-dotted lines 56, the connection between the first working chamber 5 and the housing-side outflow channel 28 or the outer receiving chamber 48 produces bypassing the plunger-side Abströmkanalabiteses.
  • a throttling point 57 which is switched into the course of the bypass channel 56 or formed by a correspondingly small cross section of the bypass channel 56 limits the flow rate possible through the bypass channel 56 to a value which is lower than the outflow rate possible with the outflow channel 12b released, so that from the start of the damping phase, the flow rate still remains Pressure medium from the first working chamber 5 is displaced, but this to a much lesser extent, so that in turn builds up a back pressure in the first working chamber 5, which reduces the piston speed.
  • the restoring force of the spring device 33 is chosen in this Vatiante so that the building up force Fs at no time is able to lift the plunger 18 from the working piston 3.
  • the throttle body is formed adjustable in their throttling intensity, the damping characteristic can be easily adapted to the particular application.
  • the throttle point can be defined for example by an adjustable throttle screw.
  • the first working chamber 5 is completely closed off at shut-off from the working piston 3 discharge opening 27 and without further connection to a pressure sink.
  • the outflow of the pressure medium takes place here exclusively through the periodically released outflow opening 27th
  • FIG. 6 shows a variant in which the plunger 18 directly itself to define the bypass channel 56th contributes.
  • the plunger 18 projects into the receiving chamber 17, without subdividing them as in the other embodiments under sealing in two receiving chamber sections.
  • the receiving chamber 17 as a whole communicates with the housing-side outflow channel section 28 on the one hand, and with the ram-side outflow channel section 26 in the manner already described, on the other hand.
  • a bypass channel 56 is a gap-like gap 56 a between the outer periphery of the plunger 18 and the penetrated by the plunger 18 partition 24. Apart from the gap-like gap 56 a is no connection between the receiving chamber 17 and the Thus, in particular, the opening 52 present in the other exemplary embodiments is missing. With the exception of the region of the gap-like interspace 56a, the plunger 18 penetrates the opening 25 in a sealed or at least tight fit.
  • the plunger 18 in the exemplary embodiment is provided on the outer circumference locally with a longitudinal recess 59 defined, for example, by a groove or a flattening, which defines the gap-like intermediate space 56a with the opposite peripheral surface section of the opening 25. If during the damping phase, the discharge opening 27 is closed by the working piston 3, the pressure medium can only throttled over the gap-like gap 56 a in the receiving chamber 17 and from there to the pressure sink flow, resulting in the first working chamber 5 already described back pressure and consequently the deceleration of the Working piston 3 causes.
  • the longitudinal recess 59 may be designed such that the cross section of the gap-like intermediate space 56 a is constant irrespective of the axial position of the plunger 18. However, it is also possible to realize a flow-dependent flow cross-section that varies depending on the stroke. For this purpose, in the manner indicated by dash-dotted lines, the longitudinal recess 59 can be designed, for example, with a cross-section which changes in the longitudinal direction, e.g. with changing depth. In particular, it is then possible to realize an attenuation intensity which increases as the working piston 3 approaches the second stroke end position.
  • check valve means 54 may be present, which, bypassing the ram-side outflow channel section 26, a fluid admission allow the first working chamber 5, when the first control channel 12 pressure medium is fed.
  • the check valve means 54 can in this case be turned on in a separate overflow channel 58 which runs in the first end wall 8 and which opens at one end into the first working chamber 5 and at the other end into the housing-side outflow channel section 28 or directly into the receiving chamber 17.
  • the check valve means 45 allow fluid flow only in the direction of the first working chamber 5 and lock in the opposite direction. They may be of conventional construction, for example by means of a valve ball pressed against a valve seat by a spring.
  • check valve means 54 Such a separate implementation of the check valve means 54 would also be possible or alternatively in the design of Figures 1 to 5. There could then be dispensed in particular to the non-return function of the annular seal 55.
  • the damping principle according to the invention can be used not only in active fluid devices such as fluid-actuated drives, but also in passive fluid devices such as shock absorbers, in which the piston is not displaced by fluid force but by external application of force.
  • the output member 14 would then act as a drive part, for example, as to be acted upon by a braked external part bumper.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Damping Devices (AREA)
EP05011977A 2005-06-03 2005-06-03 Dispositif entraîné par un fluide Withdrawn EP1729015A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP05011977A EP1729015A1 (fr) 2005-06-03 2005-06-03 Dispositif entraîné par un fluide

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05011977A EP1729015A1 (fr) 2005-06-03 2005-06-03 Dispositif entraîné par un fluide

Publications (1)

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EP1729015A1 true EP1729015A1 (fr) 2006-12-06

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2142738A4 (fr) * 2007-04-10 2013-01-09 Wabtec Holding Corp Système d'amortissement pour cylindre pneumatique de moteur différentiel
CN115163603A (zh) * 2022-05-16 2022-10-11 马鞍山市天成液压机械制造有限公司 一种带内置线性位移传感器的近程保压高压重型液压缸

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2332520A (en) * 1942-05-18 1943-10-26 Victor F Lucht Variable buffer
US4700611A (en) * 1983-09-17 1987-10-20 Shoketsu Kinzoku Kogyo Kabushiki Kaisha Pneumatic cylinder motor with end-of-travel cushioning mechanism
DE3644662A1 (de) * 1986-12-30 1988-07-14 Josef Goellner Hydraulischer endlagenstossdaempfer
DE3920293C2 (fr) 1989-06-21 1992-10-29 Festo Kg, 7300 Esslingen, De
EP0318671B1 (fr) 1987-12-01 1994-03-02 Festo KG Amortisseur pneumatique de chocs
US5784947A (en) * 1992-06-22 1998-07-28 Bayne Machine Works, Inc. Residential refuse collection cart lifter with universal features
DE10158123A1 (de) 2001-11-27 2003-06-12 Rexroth Mecman Gmbh Endlagengedämpfter Druckmittelzylinder
EP1447571A1 (fr) 2003-02-12 2004-08-18 Rexroth Mecman GmbH Cylindre à amortissement de fin de course réglable

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2332520A (en) * 1942-05-18 1943-10-26 Victor F Lucht Variable buffer
US4700611A (en) * 1983-09-17 1987-10-20 Shoketsu Kinzoku Kogyo Kabushiki Kaisha Pneumatic cylinder motor with end-of-travel cushioning mechanism
DE3644662A1 (de) * 1986-12-30 1988-07-14 Josef Goellner Hydraulischer endlagenstossdaempfer
EP0318671B1 (fr) 1987-12-01 1994-03-02 Festo KG Amortisseur pneumatique de chocs
DE3920293C2 (fr) 1989-06-21 1992-10-29 Festo Kg, 7300 Esslingen, De
US5784947A (en) * 1992-06-22 1998-07-28 Bayne Machine Works, Inc. Residential refuse collection cart lifter with universal features
DE10158123A1 (de) 2001-11-27 2003-06-12 Rexroth Mecman Gmbh Endlagengedämpfter Druckmittelzylinder
EP1447571A1 (fr) 2003-02-12 2004-08-18 Rexroth Mecman GmbH Cylindre à amortissement de fin de course réglable

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2142738A4 (fr) * 2007-04-10 2013-01-09 Wabtec Holding Corp Système d'amortissement pour cylindre pneumatique de moteur différentiel
US8528459B2 (en) 2007-04-10 2013-09-10 Wabtec Holding Corp. Cushioning system for pneumatic cylinder of differential engine
AU2008236987B2 (en) * 2007-04-10 2013-10-10 Wabtec Holding Corp. Cushioning system for pneumatic cylinder of differential engine
CN115163603A (zh) * 2022-05-16 2022-10-11 马鞍山市天成液压机械制造有限公司 一种带内置线性位移传感器的近程保压高压重型液压缸

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