EP3205892B1 - Unité linéaire actionnée par fluide - Google Patents

Unité linéaire actionnée par fluide Download PDF

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Publication number
EP3205892B1
EP3205892B1 EP16154923.3A EP16154923A EP3205892B1 EP 3205892 B1 EP3205892 B1 EP 3205892B1 EP 16154923 A EP16154923 A EP 16154923A EP 3205892 B1 EP3205892 B1 EP 3205892B1
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EP
European Patent Office
Prior art keywords
groove
section
damping
piston
fluid
Prior art date
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EP16154923.3A
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German (de)
English (en)
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EP3205892A1 (fr
Inventor
Bernd Bellingrodt
Joachim Kefer
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Festo SE and Co KG
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Festo SE and Co KG
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Priority to EP16154923.3A priority Critical patent/EP3205892B1/fr
Publication of EP3205892A1 publication Critical patent/EP3205892A1/fr
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Publication of EP3205892B1 publication Critical patent/EP3205892B1/fr
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    • 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
    • F15B15/222—Other details, e.g. assembly with regulating devices for accelerating or decelerating the stroke having a piston with a piston extension or piston recess which throttles the main fluid outlet as the piston approaches its end position

Definitions

  • the invention relates to a fluid-operated linear unit, with a linearly displaceably arranged in a working chamber of a housing piston and at least one Endlagendämpfungs adopted for cushioning of the piston, a movement-coupled to the piston shut-off body and an axially opposite the shut-off on a housing-fixed end wall with a control mouth in the Contain working chamber opening fluidic control channel, wherein on the end wall or on the shut-off a coaxial to the control mouth of the control channel sealing ring is arranged, which sealingly slides on a formed on the outer circumference of the shut-off or on the inner circumference of the control channel cylindrical sealing surface when the shut-off on approach of the piston a Kolbenendlage dips through the control port into the control channel, wherein inserted into the sealing surface an axially extending Dämpfungsnutan extract is, whose Nutan effet fürsquerrough varies over its axial length.
  • One from the EP 2 047 116 B1 known fluid operated linear unit of this type is designed as a pneumatic cylinder and has two Endlagendämpfungs noticeden, which provide a reduction in the impact intensity when the piston moves in its two Kolbenendlagen, usually by contact with an opposite housing-fixed end wall To be defined.
  • the end position damping device comprises in a variant of a projecting away from the piston shut-off body with a cylindrical sealing surface into which a Dämpfungsnutan extract is embedded, which is composed of a plurality of axially extending damping grooves.
  • the shut-off body dips into an opposite control channel, wherein it passes through a sealing ring which slidably rests against the sealing surface, that previously unhindered displaced by the control passage fluid only flow through the Dämpfungsnutan extract and consequently with a reduced flow rate can. This causes an effective cushioning at different piston speeds, without having to make adjustments by adjusting valves.
  • a cushioning device pneumatic cylinder which has a damping sleeve having at least one axially extending notch on its lateral surface.
  • This notch has different sized cross-sectional areas for adapting the attenuation intensity to the mass to be braked and / or accelerating. Specifically, this is a first cross-sectional area with a relatively constant, small cross-section, followed by further cross-sectional areas, which initially cause an enlargement of the cross section and then a gradual reduction of the cross section.
  • These cross sectional forms of Notches are varied depending on the mass to be braked and / or acceleration, so that different shapes are required for different applications, which involves a large manufacturing effort.
  • the invention has for its object to provide means for cushioning in a fluid-operated linear unit, which must make without changes within a large mass and speed spectrum very good damping properties.
  • the Dämpfungsnutan extract over several alternately successive and axially merging lengths with a minimum and a maximum Nutan glovessquerites has, so that the Nutan glovessquerrough the Dämpfungsnutanowski alternately decreases and increases in the longitudinal direction of the sealing surface wherein the Dämpfungsnutan extract has at least two axially spaced apart longitudinal sections each having a minimum Nutan glovessquerrough and at least two axially spaced apart longitudinal sections each having a maximum Nutan glovessquerrough.
  • the cylindrical sealing surface formed either on the shut-off body or on the inner circumference of the control channel has axially a front end region, from which the sealing ring slides axially over the sealing surface when the shut-off body dips into the control channel through the control mouth.
  • the sealing ring is located in a region of the sealing surface, referred to as end position section, which is assigned to the rear end region of the sealing surface.
  • the shut-off body has reached the maximum possible immersion depth with respect to the control channel here.
  • At least one damping groove is formed in the sealing surface, which extends in the longitudinal direction of the sealing surface and which has a changing groove cross-section across its groove length.
  • the damping groove is thereby divided into a plurality of alternately successive and axially in particular continuously merging into each other length sections minimum and maximum groove cross-section.
  • Such a thing designed damping groove is called due to their changing groove cross section as a variable Dämpfungsnut.
  • the damping groove arrangement contains a plurality of variable damping grooves, these are expediently formed with the same length and arranged so that they extend over the same longitudinal section of the sealing surface.
  • the plurality of variable damping grooves are formed identically to each other so that they have the same changing cross-sectional shape over their length compared with each other.
  • variable damping grooves are preferably placed so that each length section of minimum cross-section of each variable damping groove relative to the longitudinal extent of the sealing surface at the same axial height with a longitudinal section of minimum cross-section of each other variable damping groove.
  • variable damping grooves are expediently open on the front side on the front side, the front side meaning that side which is associated with the front end region of the sealing surface.
  • each variable damping groove of the Dämpfungsnutan extract is formed so that it ends axially before the above-described end position portion of the sealing surface.
  • the variable damping grooves lose their effect, even before the piston has reached the piston end position.
  • the variable damping grooves are combined with at least one further damping groove of the damping groove arrangement, which is referred to as a constant damping groove, because it has a groove cross section which remains constant over its effective groove length.
  • This constant damping groove is placed so that it overlaps axially with each variable damping groove and also extends back to a region which lies axially to the end position portion of the sealing surface, so through the constant damping groove through a fluid transfer between the working chamber and the control channel also then it is still possible if the sealing ring has reached the end position portion and the variable damping grooves have become ineffective. In this way, up to the piston end position, a fluid transfer from the working chamber in the control channel possible, with only a very small Nutan kannsquerites is available on the very last part of the path of the piston movement, which ensures safe braking without rebound.
  • the Dämpfungsnutan extract is equipped with only a single constant Dämpfungsnut, which extends preferably linear over the entire axial length of the sealing surface away.
  • Each constant damping groove has expediently a V-shaped cross section.
  • the Dämpfungsnutan extract in one of the constant Dämpfungsnut diametrically opposite region of the sealing surface has a further Dämpfungsnut, which is designated for better distinction as a short Dämpfungsnut because their longitudinal extent limited only to the front end portion of the sealing surface. It ensures that the Nutan glovessquerites, that is, the total displaced from the working fluid from the Dämpfungsnutanowski provided Abströmquerrough at the beginning of the Endlagendämpfungsphase, which ensures a harmonious start of the damping process even with large masses and / or high speeds ,
  • variable damping grooves when the Dämpfungsnutan extract has a plurality of variable damping grooves, it is advantageous if the variable damping grooves have a triangular groove cross-section which is defined by two angularly and preferably at an angle of at least slightly more than 90 ° to each other arranged first and second groove flanks of which the first groove flank is formed flat and preferably extends in a Nutflank plane, the at least slightly oriented obliquely to a reference radial plane which is parallel to the central longitudinal axis of the cylindrical sealing surface and contains this central longitudinal axis.
  • the length sections of different groove cross-section result from the fact that the second groove flank has a zigzag-shaped or wavy longitudinal course and is composed of continuously merging valley and ridge sections.
  • the damping groove arrangement has a plurality of variable damping grooves designed in this way, several and preferably all variable damping grooves are arranged such that the groove flank planes of their first groove flanks extend parallel to one another.
  • Such a configuration favors a so-called tool-related production of Dämpfungsnutan angel means urformender manufacturing process, in particular by injection molding.
  • the variable damping grooves are arranged symmetrically on both sides of the reference radial plane.
  • a plurality of the variable damping grooves are formed in each of the two opposing sides of a further radial plane perpendicular to the reference radial plane, sealing surface sections of the sealing surface.
  • each variable damper groove has a right-angled V-contour in each region of its axial length.
  • the end position damping device can only be present in a simple manner if end position damping is desired in only one direction of movement of the piston. This is the case, for example, in a linear unit acting as a shock absorber.
  • the linear unit one? fluid-actuated linear drive the end position damping device will regularly be present twice so that in both directions of movement of the piston cushioning is effected.
  • a fluid-actuated linear drive can be equipped with only a single end position damping device, if the application requires a cushioning in only one direction of movement of the piston.
  • the shut-off element which dips into the control channel during the end-position damping process is preferably piston-shaped or sleeve-shaped and designed in such a way that it protrudes axially from the piston to be braked.
  • the fluid-actuated linear unit 1 depicted in the drawing is a linear drive 1a, which can be actuated by means of fluid force and in particular pneumatically.
  • This linear drive 1a has a housing 3 and a
  • the fluid responsible for the required actuation force fluid is in particular compressed air, although another gas or a hydraulic medium would be used by fluid loading relative to the housing 3 linearly movable working unit.
  • the linear unit 1 is designed as a shock absorber.
  • the working unit 2 is mechanically moved by an external force acting on it.
  • working movement 4 The possible linear movement of the working unit 2 is hereinafter referred to as working movement 4 and is indicated by a double arrow.
  • the direction of movement of the working movement 4 coincides with the axial direction of the longitudinal axis 26 of the linear unit 1, which at the same time concerns the longitudinal axes of the housing 3 and the working unit 2.
  • an elongated working chamber 5 is formed, in which a piston 6 belonging to the working unit 2 is linearly displaceable in the axial direction of the longitudinal axis 26 in the working movement 4.
  • the working chamber 5 is divided by the piston 6 under sealing axially into a first sub-chamber 7 and a second sub-chamber 8.
  • the seal is effected by a sealing device 12 carried by the piston 6, which rests on a working chamber 5 peripherally delimiting and formed on the housing 3 piston sliding surface 13 slidably.
  • the housing 3 contains a housing tube 14 defining the piston running surface 13, as well as first and second end walls 15, 16 arranged on opposite end sides of the housing tube 14.
  • the working chamber 5 is limited end face.
  • the first end wall 15 defines the first sub-chamber 7, the second end wall 16, the second sub-chamber 8.
  • the working unit 2 includes a fixedly connected to the piston 6 power transmission member 18, which protrudes from the housing 3 and has a lying outside the housing 3 coupling portion 22, which is connectable in the exemplary linear drive 1a with a component to be moved.
  • the linear unit 1 as a shock absorber via the coupling section 22, the external force introduction.
  • the linear drive 1a may, for example, be a rodless linear drive, wherein the coupling section 22 is, for example, a driver which projects through a longitudinal slot of the housing 3.
  • the power transmission member 18 is designed as a piston rod 18 a, which extends coaxially to the longitudinal axis 26 and which passes through the first end wall 15 slidably sealed.
  • each control channel 23, 24 discharges via its own connection opening 27 to an outer surface of the housing 3.
  • a drive fluid can be fed into the two sub-chambers 7, 8 alternately and in opposite directions through the two connection openings 27 be discharged from these sub-chambers 7, 8, so that the piston 6 is acted upon by a fluidic actuation force, from which results in a linear drive 1a, the working movement 4 of the working unit 2.
  • the first control channel 23 is penetrated in the embodiment of the piston rod 18 a. Its flow cross-section made available for the passage of fluid is therefore ring-shaped, at least in the region of the associated control orifice 20.
  • shut-off body 28 away which belongs to the working unit 2 and extends coaxially in the direction of the opposite control port 20 back.
  • the working unit 2 between a voltage applied to the first end wall 15 first piston end position and one FIG. 1 apparent, on the second end wall 16 adjacent the second piston end position movable.
  • the piston rod 18a is retracted maximally into the housing 3 in the second piston end position.
  • the two piston end positions are preferably defined by the fact that the piston 6 abuts against an inner axial end face 25 of the respective end wall 15, 16 facing it.
  • the shut-off 28 are shorter than the possible between the two Kolbenendlagen work stroke of the unit 2. If the piston 6 one of the two Kolbenendlagen, therefore, the projecting towards the other Kolbenendlage shut-off 28 is completely within the associated sub-chamber 7, 8 and is off the opposite control channel 23, 24 pulled out.
  • the linear unit 1 is equipped with an end-position damping device 32, which causes the speed of the piston 6 and thus of the working unit 2 during a designated as damping phase stroke phase is greatly reduced shortly before reaching the Kolbenendlage to unwanted impact on the housing 3 avoid.
  • the damping effect is based on the structure of a force acting on the working unit 2 fluidic counterforce.
  • Each of the two end-position damping devices 32 includes one of the two shut-off bodies 28 and a sealing ring 33 arranged coaxially in the area of the control orifice 20 of the opposite control channel 23, 24.
  • the peripheral outer periphery of the shut-off body 28 forms a cylindrical sealing surface 35 which is sealed by the associated sealing ring 33 is when the shut-off body 28 in the above-mentioned damping phase through the sealing ring 33 passes into the respective control channel 23, 24 dives.
  • the sealing ring 33 is expediently made of a material with rubber-elastic properties, at least in the region in contact with the peripheral sealing surface 35 of the shut-off body 28.
  • the cylindrical sealing surface 35 has axially a front end portion 44 which faces the sealing ring 33 in the state of the shut-off body 28 which is not immersed in the sealing ring 33. Further, the sealing surface 35 has a respect to the front end portion 44 axially closer to the piston 6 lying rear end portion 46.
  • the contact area between the sealing ring 33 and the sealing surface 35 is limited to a longitudinal section of the sealing surface 35 in the rear end region 46, referred to as end-position section 45. This end-section 45 expediently adjoins the piston 6 axially directly.
  • the shut-off body 28 is sleeve-shaped in both end-position damping devices 32 and is seated coaxially on the piston rod 18a passing through it. Not further illustrated fastening measures provide for an axially immovable fixation with respect to the piston 6.
  • the shut-off body 28 may also be formed of solid material and a piston-shaped overall.
  • the shut-off body 28 may also be an integral part of the piston rod 18a.
  • the linear unit 1 is equipped with only one end-position damping device 32, so that only in one direction of movement of the working unit 2 takes place a cushioning.
  • shut-off body 28 at the front end portion 44 of the sealing surface 35 is suitably rounded or conically tapered, which applies to the embodiment.
  • the sealing surface 35 includes as an integral part of a recessed sunken into the sealing surface 35 Dämpfungsnutan extract 36 which extends in the longitudinal direction of the sealing surface 35.
  • the cylindrical sealing surface 35 has a longitudinal axis 37 which coincides with the longitudinal axis 26 and whose axial direction defines the longitudinal direction of the sealing surface 35.
  • the sealing surface 35 also has a circumferential direction 38 indicated by a double arrow, which is the direction around the longitudinal axis 37.
  • the Dämpfungsnutan extract 36 is composed of a plurality of embedded in the sealing surface 35 groove-like depressions, which are referred to as damping grooves 47 due to their functionality. These are preferably differently designed types of damping grooves 47, among which there is preferably at least one variable damping groove 47a and at least one constant damping groove 47b. Furthermore, there is optionally a damping groove 47, designated as a short damping groove 47c, whose presence is restricted exclusively to the front end region 44 of the sealing surface 35 and whose longitudinal extent is limited to this front end region 44.
  • Each damping groove 47 has a groove cross-section which lies in a plane perpendicular to the longitudinal axis 37.
  • the sum of the groove cross sections of all the damping grooves 47 lying in this way defines the entire cross section of the damping groove arrangement 36, which is referred to as the groove arrangement cross section.
  • the outflow cross-section available to the drive fluid displaced from the respective sub-chamber 7 or 8 is determined by that groove arrangement cross-section which is measured at the longitudinal position of the sealing face 35 at which the sealing ring 33 is located.
  • the sealing ring 33 abuts only on the sealing surface 35, while it only bridges the damping grooves 47 and not or only slightly immersed in the damping grooves 47. Consequently, the displaced working fluid can flow only throttled during the damping phase, so that a pressure build-up takes place in the assigned sub-chamber 7, 8, which exerts a braking force opposite the direction of movement of the working unit 2 on the piston 6 and thereby slows down the working movement 4 until it stops.
  • a special feature of the Dämpfungsnutan extract 36 is that their Nutan kannsquerrough across the axial length of the sealing surface 35 changes away.
  • the design is such that the Nutan glovessquerrough starting at the front end portion 44 tends to decrease to the rear end portion 46, which in the diagram of FIG. 6 is illustrated by a leveled cross-sectional profile line 48.
  • the cross-sectional reduction is overall not continuous, but is characterized by a mountain and Valley course, in which alternate lengths of minimum Nutan glovessquerites and lengths sections with maximum Nutan glovessquerrough.
  • the cross-sectional areas of the maximum Nutan glovessquerexcellente tend towards the rear end portion 46 of the sealing surface 35, which is preferably true for the minimum Nutan glovessquerroughe.
  • the length sections of the damping groove arrangement 36 having a minimum groove arrangement cross-section are identified by reference numeral 52 and are also referred to below as minimum length sections 52 for the sake of simplicity.
  • the maximum Nutan glovessquerites having longitudinal sections of the Dämpfungsnutan extract 36 identified by reference numeral 53 and hereinafter referred to simplification as maximum length sections 53.
  • the minimum length sections 52 and maximum length sections 53 are arranged axially one after the other and expediently merge into one another continuously.
  • the Dämpfungsnutan extract 36 has at least two and preferably more than two axially spaced-apart minimum longitudinal sections 52 and also additionally at least two and preferably more than two axially spaced-apart maximum length sections 53rd
  • variable damping grooves 47a a plurality are present, all of which expediently have their front starting point in the front end region 44 of the sealing surface 35, wherein they are preferably open on the front side of the front side.
  • the variable damping grooves 47a preferably extend at the front side of the shut-off body 28 as far as the front axial end face 54 facing away from the piston 6.
  • variable damping grooves 47a expediently before the Endlagenabites 45. This ensures that at the latest in the Kolbenendlage no drive fluid is more able to pass through the sealing ring 33 through one of the variable damping grooves 47a and from the working chamber 5 in the associated control channel 23, 24 to transfer.
  • variable attenuation groove array 47a Compared to a single variable damper groove 47a, the variable attenuation groove array 47a has the advantage that the slot-like groove openings located in the area of the seal surface 35 are relatively narrow, counteracting a tendency of the seal ring 33 to dive into the variable damper grooves 47a due to its elasticity.
  • the respective released flow cross-section is distributed here to all of the plurality of variable damping grooves 47a.
  • variable damping grooves 47 a are each individually configured so that each variable damping groove 47 a in their Longitudinal direction is divided into a plurality of alternately successive and continuously merging into longitudinal sections 55 minimum groove cross-section and length sections 56 maximum groove cross-section.
  • the variable damping grooves 47a are placed so that each minimum length portion 52 of the Dämpfungsnutan instruct 36 by lying at the same axial height portions 55 minimum groove cross-section and all maximum length sections 53 of the Dämpfungsnutan angel 36 lying at the same axial height sections 56 maximum groove cross-section of all variable damping grooves 47a are defined.
  • the Dämpfungsnutan Aunt 36 includes in addition to the variable damping grooves 47a at least one, and preferably exactly one constant damping groove 47b, which extends linearly in the axial direction of the longitudinal axis 37 and over its groove length has a constant groove cross-section. Unlike the variable damping grooves 47a, this constant damping groove 47b extends beyond the end layer section 45 of the sealing surface 35 and only ends axially after this end layer section 45. It extends as an example up to the piston 6.
  • This embodiment has the advantage that the constant damping groove 47b in each phase of the damping stroke and up to and including reaching the piston end position for a fluid transfer between the working chamber 5 and the associated control channel 23, 24 is available. This ensures that the piston end position is still reliably reached at a very low speed even when the variable damping grooves 47a have already emerged from the sealing ring 33.
  • the constant damping groove 47b is expediently open on the front side at the front end region 44 of the sealing surface 35. It extends parallel to the plurality of variable damping grooves 47a, which, however, projects beyond it at the rear, in order to also axially penetrate the end position section 45. Particularly advantageous is a V-shaped cross-sectional shape of the constant damping groove 47b has been found.
  • variable damping grooves 47a have a triangular groove cross section, wherein two sides of the triangle are defined by two angularly arranged first and second groove flanks 57, 58, while the third side of the triangle is formed by the slot-like groove opening in the region of the sealing surface 35.
  • the two groove flanks 57, 58 are, viewed in cross section at right angles to the longitudinal axis 37, arranged at an obtuse angle to each other, which is expediently only slightly larger than 90 °. This is true for any location along the length of a respective variable damping groove 47a.
  • the first groove flank 57 runs in the axial direction of the longitudinal axis 37 purely linearly in a plane designated as groove flank plane 62.
  • This groove flank plane 62 is preferably aligned slightly inclined to a reference radial plane 63, which contains the central longitudinal axis 37 of the sealing surface 35.
  • the groove flank plane 62 of the first groove flank 57 of each variable damping groove 47a is arranged in this manner, which applies to the illustrated embodiment.
  • the inclination of the groove flank 62 with respect to the reference radial plane 63 is not apparent due to its insignificance in the drawing.
  • the groove flank plane 62 is inclined such that its distance from the reference radial plane 63 increases as it approaches an additional radial plane 66 mentioned below.
  • the second groove flank 58 has a non-linear, zigzag-shaped or wave-shaped in the longitudinal direction of the sealing surface 35 Longitudinal course with continuously merging valley sections 65 and comb sections 64.
  • the comb sections 64 define the longitudinal sections 55 of minimal groove cross-section and the valley sections 65 define the longitudinal sections 56 of maximum groove cross-section.
  • the second groove flank 58 in the exemplary embodiment in each case has a linear, planar extension, so that a zigzag-shaped longitudinal course results. But these lengths can also be at least partially curved so that a wave-shaped longitudinal course results.
  • the edge with which the first groove flank 57 merges into the sealing surface 35 preferably has a linear extension. This differs from the longitudinal course of the existing between the second groove edge 58 and the sealing surface 35 transition edge, which runs according to the longitudinal course of the second groove flank 58 zig-zag or wavy.
  • the damping grooves 47 are distributed in the circumferential direction 38 at a distance from each other in the sealing surface 35.
  • the variable damping grooves 47a are preferably subdivided into two sealing surface sections which each occupy 180 ° of the circumference of the sealing surface 35 and which for better distinction as first sealing surface section 35a and second sealing surface section 35b are designated.
  • the two sealing surface sections 35a, 35b lie on opposite sides of a further radial plane 66 which is perpendicular to the reference radial plane 63 and has already been mentioned above, which in turn also includes the longitudinal axis 37 of the sealing surface 35.
  • four variable damping grooves 47a in the two sealing surface sections 35a, 35b each two of these four variable damping grooves 47 a on opposite sides of the reference radial plane 63.
  • first groove flanks 57 point away from the reference radial plane 63
  • second groove flanks 58 each point away from the further radial plane 66.
  • the damping groove assembly 36 can be very easily produced by primary forming by means of a forming tool having two divided halves in the other radial plane 66 tool halves.
  • the Entformungscardi is oriented at right angles to the further radial plane 66.
  • the preferred single constant damping groove 47b is expediently arranged lying in the first sealing surface section 35a and on the reference radial plane 63.
  • the short damping groove 47c already mentioned above is preferably located in the second sealing surface section 35b and there likewise on the reference radial plane 63. It is thus located in a peripheral region of the sealing surface 35 which is placed diametrically to the circumferential region containing the constant damping groove 47b.

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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)

Claims (15)

  1. Unité linéaire actionnée par fluide, avec un piston (6) agencé de manière mobile linéairement dans une chambre de travail (5) d'un boîtier (3) et avec au moins un dispositif d'amortissement de position finale (32) pour l'amortissement de position finale du piston (6) qui contiennent un corps de blocage (28) couplé en mouvement avec le piston (6) et un canal de commande (23, 24) fluidique débouchant axialement à l'opposé du corps de blocage (28) sur une paroi terminale (15, 16) fixée au boîtier avec une embouchure de commande (20) dans la chambre de travail (5), dans laquelle un anneau étanche (33) coaxial à l'embouchure de commande (20) du canal de commande (23, 24) est agencé sur la paroi terminale (15, 16) ou sur le corps de blocage (28), lequel glisse de manière étanche sur une surface étanche (35) cylindrique réalisée sur la périphérie extérieure du corps de blocage (28) ou sur la périphérie intérieure du canal de commande (23, 24) lorsque le corps de blocage (28) pénètre lors de l'approche du piston (6) d'une position terminale de piston au travers de l'embouchure de commande (20) dans le canal de commande (23, 24), dans laquelle un agencement de rainure d'amortissement (36) s'étendant axialement est intégré dans la surface étanche (35), dont la section transversale d'agencement de rainure se modifie au-delà de sa longueur axiale, caractérisée en ce que l'agencement de rainure d'amortissement (36) dispose de plusieurs sections de longueur (52, 53) se suivant alternativement et passant axialement l'une dans l'autre avec une section d'agencement de rainure minimale et une section d'agencement de rainure maximale de sorte que la section transversale d'agencement de rainure de l'agencement de rainure d'amortissement (36) diminue et augmente en alternance dans le sens longitudinal (37) de la surface étanche (35), dans laquelle l'agencement de rainure d'amortissement (36) présente au moins deux sections longitudinales (52) espacées axialement l'une de l'autre avec respectivement une section transversale d'agencement de rainure minimale et au moins deux sections longitudinales (53) espacées axialement l'une de l'autre avec respectivement une section transversale d'agencement de rainure maximale.
  2. Unité linéaire actionnée par fluide selon la revendication 1, caractérisée en ce que la surface étanche (35) présente une zone d'extrémité (44) avant tournée vers l'anneau étanche (33) et une zone d'extrémité (46) arrière opposée axialement à celle-ci, dans laquelle la zone d'extrémité (46) arrière définit une section de position finale (45), contre laquelle l'anneau étanche (33) repose de manière étanche lorsque le piston (6) a atteint la position finale de piston.
  3. Unité linéaire actionnée par fluide selon la revendication 1 ou 2, caractérisée en ce que l'agencement de rainure d'amortissement (36) contient au moins une rainure d'amortissement (47a) variable présentant une section transversale de rainure se modifiant au-delà de sa longueur de rainure qui dispose de plusieurs sections de longueur (52, 53) se suivant en alternance et passant axialement l'une dans l'autre avec une section transversale de rainure minimale et maximale.
  4. Unité linéaire actionnée par fluide selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'agencement de rainure d'amortissement (36) contient plusieurs rainures d'amortissement (47a) variables dans leur section transversale de rainure, lesquelles sont réparties dans le sens périphérique sur la périphérie de la surface étanche (35) et lesquelles disposent respectivement de plusieurs sections de longueur (55, 56) se suivant en alternance dans le sens longitudinal et passant axialement l'une dans l'autre avec une section transversale de rainure minimale et une section transversale de rainure maximale.
  5. Unité linéaire actionnée par fluide selon la revendication 4, caractérisée en ce que les rainures d'amortissement (47a) variables présentent entre elles la même longueur.
  6. Unité linéaire actionnée par fluide selon la revendication 4 ou 5, caractérisée en ce que plusieurs ou toutes les rainures d'amortissement variables (47a) sont placées de sorte que leurs sections de longueur (52) avec une section transversale de rainure minimale et leurs sections de longueur (53) avec une section transversale de rainure maximale se trouvent au moins sensiblement à la même hauteur axiale.
  7. Unité linéaire actionnée par fluide selon l'une quelconque des revendications 3 à 6 en liaison avec la revendication 2, caractérisée en ce que chaque rainure d'amortissement variable (47a) se termine axialement avant la section de position finale (45) de telle manière que chaque rainure d'amortissement variable (47a) perde son action avant que le piston (6) ne soit arrivé dans la position finale de piston.
  8. Unité linéaire actionnée par fluide selon l'une quelconque des revendications 3 à 7, caractérisée en ce qu'au moins une ou chaque rainure d'amortissement variable (47a) présente une section transversale de rainure triangulaire et présente deux premiers et seconds flancs de rainure (57, 58) agencés angulairement l'un à l'autre, dans laquelle le premier flanc de rainure (57) s'étend dans un plan de flanc de rainure (62) qui est orienté au moins légèrement incliné vers un plan radial de référence (63) contenant l'axe longitudinal (37) central de la surface étanche (35) cylindrique, alors que le second flanc de rainure (58) présente une étendue longitudinale en forme de zigzag ou d'onde et dispose de sections de creux et crêtes (65, 64) passant en permanence l'une dans l'autre par lesquelles les sections longitudinales (52, 53) avec une section transversale de rainure minimale et maximale sont définies.
  9. Unité linéaire actionnée par fluide selon la revendication 8, caractérisée en ce que les plans de flanc de rainure (62) des premiers flancs de rainure (57) de plusieurs ou toutes les rainures d'amortissement (47a) variables disposant d'une section transversale triangulaire s'étendent parallèlement l'un à l'autre.
  10. Unité linéaire actionnée par fluide selon la revendication 8 ou 9, caractérisée en ce que respectivement plusieurs des rainures d'amortissement (47a) variables disposant d'une section transversale de rainure triangulaire sont réalisées dans les deux sections de surface étanche (35a, 35b) se trouvant sur des côtés opposés d'un autre plan radial (66) perpendiculaire au plan radial de référence (63) de la surface étanche (35) en répartition symétrique au plan radial de référence (63).
  11. Unité linéaire actionnée par fluide selon l'une quelconque des revendications 3 à 10 en liaison avec la revendication 2, caractérisée en ce que l'agencement de rainure d'amortissement (36) contient outre l'au moins une rainure d'amortissement (47a) variable au moins une rainure d'amortissement (47b) constante présentant une section transversale de rainure constante au-delà de sa longueur de rainure active, s'étendant aussi axialement qui se chevauche axialement avec au moins une ou chaque rainure d'amortissement (47a) variable et qui est ouverte côté arrière vers une zone qui se trouve axialement après la section de position finale (45) de la surface étanche (35) de telle manière que l'au moins une rainure d'amortissement (47b) constante permette un passage de fluide entre la chambre de travail (5) et le canal de commande (23, 24) jusqu'à atteindre la position finale de piston, dans laquelle la rainure d'amortissement constante (47b) est ouverte côté avant de manière appropriée sur la zone d'extrémité avant (44) de la surface étanche (35).
  12. Unité linéaire actionnée par fluide selon la revendication 11, caractérisée en ce que l'agencement de rainure d'amortissement (36) présente une courte rainure d'amortissement (47c) réalisée dans une zone opposée diamétralement à la rainure d'amortissement (47b) constante de la surface étanche (35), dont l'étendue longitudinale est délimitée sur la zone d'extrémité (44) avant de la surface étanche (35).
  13. Unité linéaire actionnée par fluide selon l'une quelconque des revendications 1 à 12, caractérisée en ce que le dispositif d'amortissement de position finale (32) est présent deux fois afin de susciter son amortissement de position finale pour les deux sens de mouvement possibles du piston (6).
  14. Unité linéaire actionnée par fluide selon l'une quelconque des revendications 1 à 13, caractérisée en ce que le corps de blocage (28) est réalisé en forme de piston ou de douille et dépasse axialement du piston (6).
  15. Unité linéaire actionnée par fluide selon l'une quelconque des revendications 1 à 14, caractérisée par une configuration en tant qu'unité linéaire pneumatique actionnée avec de l'air comprimé et/ou par une configuration en tant qu'entraînement linéaire pour lequel le piston (6) peut être déplacé par alimentation de fluide en direction de sa position finale de piston.
EP16154923.3A 2016-02-09 2016-02-09 Unité linéaire actionnée par fluide Not-in-force EP3205892B1 (fr)

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CN108223487A (zh) * 2017-12-16 2018-06-29 小冶精通（天津）液压机械有限公司 一种液压油缸
GB2587193A (en) * 2019-09-13 2021-03-24 Airbus Operations Ltd Aircraft landing gear system
CN111977547B (zh) * 2020-08-31 2022-01-14 徐州硕辰液压工程机械有限公司 一种具有缓冲功能的液压装置
CN112901647B (zh) * 2021-03-11 2022-03-01 维沃移动通信有限公司 转轴装置和电子设备

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US4064788A (en) * 1976-07-29 1977-12-27 Parker-Hannifin Corporation Cushioning means for hydraulic cylinder
DE19836422C2 (de) * 1998-08-12 2002-10-24 Mannesmann Rexroth Ag Druckmittelbetätigter Arbeitszylinder
WO2008083717A1 (fr) * 2007-01-12 2008-07-17 Festo Ag & Co. Kg Unité linéaire actionnée par fluide, notamment entraînement linéaire

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