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EP3164610B1 - Piston et un positionneur equipé avec le piston - Google Patents

Piston et un positionneur equipé avec le piston Download PDF

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Publication number
EP3164610B1
EP3164610B1 EP14796715.2A EP14796715A EP3164610B1 EP 3164610 B1 EP3164610 B1 EP 3164610B1 EP 14796715 A EP14796715 A EP 14796715A EP 3164610 B1 EP3164610 B1 EP 3164610B1
Authority
EP
European Patent Office
Prior art keywords
piston
clamping
groove
strip
recess
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.)
Active
Application number
EP14796715.2A
Other languages
German (de)
English (en)
Other versions
EP3164610A1 (fr
Inventor
Jörg BESELER
Klaus Reichert
Daniela KLESMANN
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
Publication of EP3164610A1 publication Critical patent/EP3164610A1/fr
Application granted granted Critical
Publication of EP3164610B1 publication Critical patent/EP3164610B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/08—Characterised by the construction of the motor unit
    • F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
    • F15B15/1423—Component parts; Constructional details
    • F15B15/1447—Pistons; Piston to piston rod assemblies
    • 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
    • F15B15/28—Means for indicating the position, e.g. end of stroke
    • F15B15/2807—Position switches, i.e. means for sensing of discrete positions only, e.g. limit switches
    • 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
    • F15B15/28—Means for indicating the position, e.g. end of stroke
    • F15B15/2815—Position sensing, i.e. means for continuous measurement of position, e.g. LVDT
    • F15B15/2861—Position sensing, i.e. means for continuous measurement of position, e.g. LVDT using magnetic means
    • 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
    • F15B15/28—Means for indicating the position, e.g. end of stroke
    • F15B15/2892—Means for indicating the position, e.g. end of stroke characterised by the attachment means
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members

Definitions

  • the invention relates to a piston for a fluid operable adjusting device, in particular for a fluid-actuated linear actuator having a one-piece piston body in the region of its radial outer circumference coaxial to the longitudinal axis of the piston annular receiving groove with two mutually facing side groove flanks, in the one for position detection usable permanent magnet assembly is received, wherein the permanent magnet assembly consists of a bent into a ring structure elastic permanent magnetic magnetic tape.
  • the invention further relates to a fluid operable adjusting device, which is in particular a fluid-operated linear drive and which is provided with a housing in which a piston is arranged linearly displaceable.
  • An equipped with a piston of the aforementioned type actuator is known from DE 20 2005 005 508 U1 known and is designed for example as a linear drive or shock absorber.
  • the piston moves relative to a housing of the actuator, wherein the integrated into the piston permanent magnet assembly is available to allow by cooperating with external position detection means, a position detection of the piston.
  • the piston In order to produce the piston inexpensively, it contains a one-piece piston body with a peripheral receiving groove into which the permanent magnet assembly is inserted.
  • the latter consists of several arcuate Magnetic segments, which are used in the assembly of the piston from radially outside into the receiving groove.
  • the production and assembly of the magnet segments is relatively expensive.
  • the in the above DE 20 2005 005 508 U1 described piston is additionally equipped with a ring structure having a guide band, which is inserted into a formed on the outer circumference of the piston body annular retaining recess.
  • the guide band is formed as a hollow cylindrical guide ring, which is interrupted at one point of its circumference, so that it can be temporarily expanded due to its elasticity during assembly.
  • the radially outer surface of the guide band defines a guide surface which slidably engages the inner peripheral surface of the housing housing the piston so that the piston can perform a precisely guided linear movement relative to the housing.
  • a piston for a working cylinder which is equipped for position detection with an annular permanent magnet.
  • a multi-part construction of the piston body is provided.
  • the piston body consists of two mutually attached to form the receiving groove piston elements which are coated in the region of the receiving groove with an elastomeric material to clamp the permanent magnet and to fix it in a gentle manner.
  • the EP 0 307 569 A2 describes a piston-cylinder unit whose piston has a one-piece piston body, on the peripherally a broken at one point of its circumference guide belt is placed.
  • the guide band has elastic properties and is in one on the outer circumference the piston body formed annular groove spring-like snapped.
  • the piston body has at a position of its outer periphery via a recess in which a permanent magnet piece is inserted, which is covered by the guide band.
  • a fluid operable adjusting device which has a piston with a one-piece piston body, wherein in the piston body in the region of its radial outer circumference an annular receiving groove is formed, in which an annular permanent magnet is received.
  • the invention has for its object to provide measures that allow a cost-effective equipment of a piston with a usable for position detection permanent magnet assembly.
  • the magnetic tape has two in the circumferential direction of the receiving groove facing Bandendabschnitte and whose width is less than the distance between the two groove flanks of the receiving groove, each of the two Bandendabroughe by clamping in one of two in the circumferential direction of the receiving groove adjacent clamping zones of the receiving groove is held, in which the piston body has at least one under local narrowing of the receiving groove with respect to a groove flanks projecting and pressing on the side surface of the magnetic tape clamping projection.
  • the invention is further achieved in an operable with fluid actuator of the type mentioned in that it is equipped with a trained in the aforementioned sense piston.
  • an elastically bendable, over permanent magnetic properties possessing magnetic tape is used, which is placed around the piston body for mounting on the piston body and thereby inserted into the receiving groove.
  • the magnetic tape is positioned so that its two mutually facing Bandendabterrorisme come to rest in a clamping region of the piston body, in which the receiving groove has two adjacent clamping zones in the circumferential direction of the receiving groove.
  • Each of the two band end sections is placed in one of the two clamping zones.
  • Each clamping zone is characterized in that at least one of the two groove flanks of the receiving groove is provided with a clamping projection which projects beyond the associated groove flank.
  • the width of the receiving groove in the region of each clamping projection is less than the clear distance between the two mutually facing groove flanks, which is greater than the width of the magnetic tape. Consequently, the magnetic tape can be easily inserted into the receiving groove by lying around or bending around the piston body in the areas outside of the clamping area, while the two Bandendabitese are pushed into the receiving groove with slight pressure during insertion into the respective associated clamping zone.
  • the magnetic tape is applied laterally and clamped in the receiving groove. If the magnetic tape is fixed in this way in the receiving groove, the band end sections can no longer be unfolded, so that the piston can then be easily inserted into the housing of an associated adjusting device.
  • the piston body is equipped with a plurality of clamping projections acting on the respectively assigned band end section.
  • each clamping zone at least two and in particular exactly two in the circumferential direction of the receiving groove at a distance adjacent to each other arranged clamping projections are provided, which are assigned to different groove flanks.
  • the clamping projection spaced in the circumferential direction of the receiving groove in this respect is located on the opposite groove flank. It is very advantageous if none of these clamping projections opposite to the respective other groove edge associated clamping projection. In the region of each clamping projection, therefore, the assigned band end section is respectively clamped between on the one hand one of the clamping projections and on the other hand the opposite groove flank.
  • the alternate arrangement of the clamping projections on the two groove flanks has the consequence that the band end portion quasi swings through the clamping zone or has a slightly wavy longitudinal course.
  • Such a design of the clamping zone is extremely insensitive to tolerances and ensures a secure clamping each Bandendabiteses even with a large tolerance range, which can make the production costs very low.
  • the projected clear distance, measured in the longitudinal direction of the piston, between the two projections which are spaced apart in the circumferential direction of the receiving groove is smaller than the width of the magnetic tape. Nevertheless, since the clamping projections are spaced from one another, the band end section can be relatively easily threaded or pushed into the receiving groove from radially outward.
  • the clear distance between each clamping projection and the opposite groove flank of the receiving groove is equal to or greater than the width of the magnetic tape.
  • the distance measured in the circumferential direction of the receiving groove between the clamping projections arranged on different groove flanks is at least as large as the width of the magnetic tape, but at most twice the width of the magnetic tape. In this way one obtains a particularly reliable clamping effect.
  • the clamping projections can be designed arbitrarily and can be structured, for example, knob-shaped. It is considered particularly expedient if the clamping projections are each formed rib-shaped with an elongated shape and each extending starting from the region of the groove base in the direction of the radial groove opening of the receiving groove.
  • clamping projections are chamfered at their end facing the radial groove opening end to the associated groove flank. In this way, the clamped Bandendabites can very comfortably push into the receiving groove.
  • the magnetic strip is preferably a strand body bent to the desired ring shape, the two strip end sections of which either rest loosely against one another or are arranged at a small distance from one another.
  • the magnetic tape consists of a strand-shaped band body made of an elastically deformable plastic material, which is provided with permanent magnet means.
  • the permanent magnet means are preferably ferromagnetic particles which are integrated in the band body and magnetized as required.
  • the one-piece piston body is preferably made of a rigid material. This then applies correspondingly for the one-piece component of the piston body performing clamping projections.
  • the piston body made of metal, ceramic, glass or a hard plastic material.
  • the piston body not only has a single clamping area provided with two adjacent clamping zones, but has two such clamping areas which are assigned to diametrically opposite peripheral areas of the piston body. In this way, there is a greater variability in the insertion of the magnetic tape in the receiving groove.
  • the piston is equipped with a guide strip suitable for the linear guidance of the piston in a housing of an actuating device.
  • the guide band is like the magnetic tape arranged coaxially to the piston body.
  • the guide band is expediently located in an annular holding recess formed in the piston body, which concentrically encloses the annular receiving groove and which has a greater axial width than the receiving groove.
  • the receiving groove opens with its radially outer groove opening in the recess bottom of the holding recess.
  • annular structured guide tape encloses the magnetic tape radially outside and covers the magnetic tape expediently.
  • the guide band is particularly easy to mount on the piston body when it is inserted into a coaxial to the longitudinal axis of the piston annular retaining recess and is thereby held in the radial direction with respect to the longitudinal axis of the piston positively in the retaining recess.
  • the guide band has a ring structure in the assembled state, but overall is a finite, over two opposite Bandendab songse disposal strand body, which can be put around the piston body for mounting in the retaining recess simply.
  • the two mutually facing recess flanks of the holding recess have in cross-section each an undercut profiling, wherein they each have a radial distance from the recess bottom of the retaining recess in the direction of the opposite recess flank projecting annular retaining projection.
  • the two holding projections are able to engage in a form-fitting manner with the facing side edge of the guide strip pressed into the holding recess and thereby hold the guide strip in a form-fitting manner in the radial direction of the piston.
  • the guide band has elastically deformable properties, so that the holding projections can press under local deformation of the guide band and to form a positive engagement in the respective associated side edge of the guide band.
  • the guide band expediently has a rectangular cross-section.
  • FIG. 1 shows in longitudinal section a fluid operable adjusting device 1 in one embodiment as a fluid-operated linear actuator 1a.
  • a fluid operable adjusting device 1 in one embodiment as a fluid-operated linear actuator 1a.
  • the scope of the invention is not limited to linear drives, but extends to all other types of usable in connection with fluid applications actuators, such as for use in shock absorbers.
  • the adjusting device 1 has a housing 2 which defines a housing chamber 3 extending in a linear manner and preferably having a circular cross-section, in which a piston 4 is arranged to be linearly displaceable back and forth.
  • the longitudinal axis 5 of the piston 4 extends in the direction of movement of the piston 4 and preferably coincides with the longitudinal axis 6 of the housing chamber 3.
  • the housing chamber 3 is closed at both end sides by a respective end wall 7a, 7b of the housing 2.
  • the peripheral, radially outer boundary of the housing chamber 3 takes over a one-piece or multi-part tubular body 8 extending between the two end walls 7a, 7b, the inner surface of which defines a cylindrical piston running surface 9.
  • the end walls 7a, 7b are expediently designed as a housing cover which is separate relative to the tubular body 8 and connected to the tubular body 8 by fastening means. However, it is also possible to form at least one of the end walls 7a, 7b in one piece with the tubular body 8.
  • the radial outer contour of the piston 4 is adapted to the inner contour of the housing chamber 3, so that it slides along the piston running surface 9 during its linear movement.
  • the piston 4 is provided at its radially outer circumference with a preferably cylindrical guide surface 10 which slidably rests against the piston running surface 9, so that the piston 4 undergoes a linear guide with respect to the housing 2 during its linear movement by the interaction between the guide surface 10 and the piston running surface 9 ,
  • the housing chamber 3 is divided axially into two working spaces 12 a, 12 b, in each case one outside the cutting plane of the FIG. 1 lying fluid channel opens, so that a controlled fluid admission of the two working spaces 12a, 12b is possible.
  • the piston 4 can be driven to a linear movement relative to the housing 2 in the axial direction of the longitudinal axis 6.
  • the fluid used for the operation of the adjusting device 1 is preferably compressed air.
  • the use of another gaseous medium or a hydraulic medium is possible.
  • the linear movement of the piston 4 can be tapped outside of the housing 2 on a force-tapping part 14 coupled in a motion-coupled manner to the piston 4.
  • the latter is in the embodiment of a piston rod 15, which passes through at least one of the end walls 7b slidable under sealing and which is fixed with its lying within the housing chamber section 3 on the piston 4.
  • the piston 4 and the piston rod 5 thus form a moving unit.
  • the linear actuator 1a is a rodless linear drive, in which the piston 4, for example, magnetically with an outside of the Housing 2 slidably mounted Kraftabgriffsteil is motion coupled.
  • the piston 4 has a preferably disk-shaped piston body 16.
  • the piston body 16 has a piston body radial plane 16 a that is perpendicular to the longitudinal axis 5 of the piston 4.
  • About the piston body 16 of the piston 4 is fixed to the piston rod 15 in the embodiment.
  • the piston body 16 is circular-disk-shaped and is penetrated by a central fastening hole 17, with which it is plugged onto the piston rod 15.
  • the piston body 16 is expediently a one-piece component. It is preferably made of a rigid material and is made in the embodiment of metal, in particular die-cast aluminum. As alternative materials for the piston body 16, for example, ceramic, glass or hard plastic may be mentioned, with composite materials are also possible.
  • the piston body 16 carries in the region of its outer periphery to the longitudinal axis 5 concentric sealing means 18, which rest in the built-in adjusting device 1 state of the piston 4 on the piston running surface 9 slidably. They prevent a fluid transfer between the two working spaces 12a, 12b.
  • the sealing means 18 consist of two sealing rings 18a, 18b which are fixed to the piston body 16 at an axial distance from each other.
  • each sealing ring 18a, 18b held in a radially outwardly open mounting groove 19a, 19b, which are formed in the piston body 16 at its radially outer periphery.
  • Each attachment groove 19a, 19b is arranged coaxially with the longitudinal axis 5.
  • the guide surface 10 is expediently formed by the radially outwardly oriented outer circumferential surface of a guide band 22 having a ring structure which is fixed to the piston body 16 in the region of the radial outer circumference.
  • the piston body 16 has in the region of its radial outer circumference via a coaxial to the longitudinal axis 5 annular retaining recess 23 into which the guide belt 22 dips radially and in which the guide belt 22 is held.
  • the piston 4 is equipped with a permanent magnet assembly 24 which is usable for detecting the position of the piston 4.
  • the permanent magnet assembly 24 is fixed in place on the piston 4 and makes its linear movement with.
  • position detection means responsive to the magnetic field of the permanent magnet assembly 24 can be in operation of the actuator 1, the current axial position of the permanent magnet assembly 24 supporting Determine piston 4.
  • the position detection means comprise, for example, one or more sensors, for example Hall sensors, and / or they belong to a displacement measuring system.
  • the permanent magnet arrangement 24 expediently has an annular structure and is arranged coaxially to the longitudinal axis 5 on the piston body 16.
  • the permanent magnet arrangement 24 is received in an annular receiving groove 25 of the piston body 16 formed in the region of the radial outer circumference of the piston body 16.
  • This receiving groove 25 has a radially outwardly oriented, extending around the piston body 16 around extending slot-shaped groove opening 26 which is narrower in the axial direction of the piston 4 than the retaining recess 23.
  • the receiving groove 25 is surrounded by the holding recess 23 radially outside, wherein it opens with its groove opening 26 in the recess bottom 27 of the retaining recess 23.
  • the recess base 27 is the radial base of the retaining recess 23.
  • the radially oriented groove opening 26 of the receiving groove 25 opens into the holding recess 23 in the axially central region.
  • annular recessed base portion 27a, 27b which is preferably contoured cylindrical.
  • the arranged in the holding recess 23 guide belt 22 covers the slot opening 26 and consequently also arranged in the receiving groove 25 permanent magnet assembly 24th
  • the retaining recess 23 for the guide band 22 has two in the axial direction of the longitudinal axis 5 of the piston 4 spaced apart and facing each other side recess flanks 28a, 28b. Each of these depression flanks 28 adjoins the depression bottom 27, with each depression flank being exemplified 28a, 28b merges into one of the two recess base sections 27a, 27b.
  • the holding recess 23 is open at the recess bottom 27 opposite radial side, ie radially outward.
  • the receiving groove 25 for the permanent magnet arrangement 24 has a groove base 32, radially outwardly facing groove base surface, which lies opposite the groove opening 26 radially outward.
  • the diameter of the groove bottom 32 is smaller than the diameter of the recess bottom 27.
  • the receiving groove 25 has two in the axial direction of the longitudinal axis 5 spaced apart and at the same time facing each other lateral groove flanks 33a, 33b, which are hereinafter referred to better distinction as the first groove flank 33a and second groove flank 33b.
  • the two groove flanks 33a, 33b go in the embodiment radially inward into the recess bottom 27 of the retaining recess 23 via.
  • the clear distance between the two groove flanks 33a, 33b is smaller than the clear distance between the two recess flanks 28a, 28b.
  • the receiving groove 25 preferably has an at least substantially rectangular cross-section.
  • the guide band 22 has a ring structure in the state fixed in the holding recess 23. However, the ring structure is not completely self-contained, but has an interruption 34.
  • the guide band 22 is a strand body of finite length, which has two mutually opposite Bandendabête 22a, 22b.
  • the guide band is made as a linear extruded body, which is then bent, during assembly on the piston body 16, to the annular shape.
  • the guide band 22 has elastically deformable properties.
  • the guide band 22 When assembled, the guide band 22 is wound around the piston body 16 coaxially and inserted into the holding recess 23, with its two band end portions 22a, 22b facing each other in the circumferential direction 23a of the holding recess 23.
  • the circumferential direction 23a of the holding recess 23 is the direction about the longitudinal axis 5 and is indicated in Figure 3 by a double arrow.
  • the facing each other in the circumferential direction of the holding recess 23 faces of the guide belt 22 are preferably chamfered across the entire width of the guide belt 22 away.
  • the mutually facing beveled end faces of the two Bandendabitese 22a, 22b are preferably parallel to each other.
  • the permanent magnet assembly 24 preferably consists of an elastic permanent magnetic magnetic tape 35 bent into a ring structure.
  • the magnetic tape 35 is expediently of finite length and has two mutually opposite band end portions 35a, 35b.
  • the magnetic tape 35 is made as a linear strand body, which is bent to the ring structure when it is mounted in the receiving groove 25.
  • the magnetic tape 35 is thus bent around in its mounting on the piston body 16 expediently with simultaneous radial insertion into the receiving groove 25 to the piston body 16.
  • This type of assembly suitably corresponds to that of the guide band 22nd
  • the magnetic tape 35 has elastically deformable properties.
  • it consists of a strand-shaped band body made of an elastically deformable plastic material, which is provided with permanent magnet means, which are responsible for the permanent magnetic properties of the magnetic tape 35.
  • the permanent magnet means are, for example, ferromagnetic particles which are embedded in the strand-shaped band body in fine distribution during the production of the magnetic tape and subsequently magnetized.
  • the circumferential direction 25a of the receiving groove 25 is the direction around the longitudinal axis 5 and is in FIG. 3 indicated by a double arrow. Between the two Bandendabitesen 35a, 35b is an interruption 36 of the ring structure of the magnetic tape 35, which manifests itself in particular in a small gap, so that the two Bandendabchae 35a, 35b in the circumferential direction 25a of the receiving groove 25 are opposed with a small distance.
  • the circumferential direction 25a of the receiving groove 25 is the direction around the longitudinal axis 5 of the piston 4 around.
  • the magnetic tape 35 has two longitudinal side surfaces 39a, 39b which, in the state mounted in the receiving groove 25, respectively face one of the groove flanks 33a, 33b.
  • the guide band 22 in the inserted into the retaining recess 23 due to its elastic properties has the tendency to open in the region of the two Bandendabitese 22a, 22b and from the retaining recess 23, the guide belt 22 is held together by the piston body 16 solely because of suitable fixing measures, so that it retains its ring structure in which it is fixed in the retaining recess 23 over its entire length.
  • the piston body 16 is formed in the region of the receiving groove 25 so that it holds the inserted into the receiving groove 25 magnetic tape 35 so that it is based on its elasticity expansion tendency on his full length away in the receiving groove 25 is arranged and in the region of the two Bandendabête 35a, 35b does not open.
  • the presently described effect is achieved in the guide band 22 in that the two recess flanks 28a, 28b of the holding recess 23 in cross-section each have an undercut profiling, so that each recess flank 28a, 28b form-fitting with the respectively facing side edge 37a, 37b of the two in the axial direction the longitudinal axis 5 oriented side edges 37a, 37b of the guide belt 22 is engaged.
  • the form-fit acts in a radial direction with respect to the longitudinal axis 5, so that the guide band 22 is held in the retaining recess 23 over its entire length by the profiled recess flanks 28a, 28b. It is expediently a releasable positive engagement to allow replacement of the guide band in case of need.
  • the undercut profiling of the recess flanks 28a, 28b manifests itself per recess flank 28a, 28b, in particular in a holding projection 38a, 38b projecting in the direction of the respectively opposite recess flank 28b, 28a is arranged concentrically to the longitudinal axis 5 of the piston 4 and extends continuously in the circumferential direction of the retaining recess 23.
  • Each of the two holding projections 38a, 38b is arranged with a radial distance with respect to the recess base 27 of the holding recess 23 with respect to the longitudinal axis 5, so that in the area of a respective recess flank 28a, 28b located radially between a respective holding projection 38a, 38b and the recess base 27 annular self-contained holding recess 43a, 43b results, in which the guide strip 22 can engage and which is also arranged concentrically to the longitudinal axis 5 of the piston 4.
  • the guide belt 22 preferably has a rectangular cross-section in the initial state not yet inserted into the holding recess 23.
  • the width of the guide belt 22 is slightly larger in this initial state than the measured in the axial direction of the longitudinal axis 5 clear distance between the opposing retaining projections 38a, 38b. In this way it is achieved that the holding projections 38a, 38b are pressed in the inserted into the holding recess 23 state of the guide belt 22 under local deformation of the guide belt 22 in the respective associated side edge 37a, 37b.
  • the displaced by the impressing material of the guide strip 22 engages in the retaining recesses 43 a, 43 b.
  • the guide strip is acted upon with radial force with respect to the longitudinal axis 5, so that it is pressed in between the two holding projections 38a, 38b and clamped therein.
  • the magnetic tape 35 is advantageously a clamping principle is used, in which the magnetic tape 35 is not clamped over its entire length away by the piston body 16, but only in some areas, and in particular at its two Bandendabêten 35a, 35b.
  • the clamping fixation of the two band end sections 35a, 35b takes place independently of one another.
  • the two band end portions 35a, 35b are not fixed to each other, but only on the piston body 16th
  • the piston body 16 has at least one point of its peripheral outer circumference via a clamping region 44, on which the piston body 16 is formed so that it can hold the two Bandendabête 35a, 35b independently clamped in the receiving groove 25.
  • the piston body 16 in the clamping region 44 has two clamping zones 45a, 45b, which are adjacent to one another in the circumferential direction 25a of the receiving groove 25 and which is designed to positively hold one of the band end sections 35a, 35b in each case.
  • the magnetic tape 35 expediently has a constant width "B" over its entire length. This width B is in the axial direction of the longitudinal axis 5 of the piston 4 and between the both side surfaces 39a, 39b measured.
  • the magnetic tape 35 desirably has a rectangular cross-sectional shape.
  • the width B of the magnetic tape 35 is less than the clear distance A1 between the two groove flanks 33a, 33b of the receiving groove 25. Consequently, the magnetic tape 35 is in those areas of the receiving groove 25 in which portions of the groove flanks 33a, 33b opposite, with a small Game tainted in the receiving groove 25 recorded.
  • the piston body 16 has at least one clamping projection 46a, 47a protruding with respect to one of the two groove flanks 33a, 33b in the direction of the opposite groove flank 33b, 33a; 46b, 47b, which causes a local narrowing of the receiving groove 25.
  • the local constriction ensures that the magnetic tape 35 is clamped in one or more places in the region of its two band end sections 35a, 35b in the receiving groove 25 and can not open.
  • the constriction areas which can also be referred to as bottlenecks, are marked by arrows at 48.
  • each clamping zone 45a, 45b only a single clamping projection whose distance to the opposite groove flank is slightly smaller than the width B of the magnetic tape 35, so that the clamping essentially results from the fact that the single clamping projection in the facing side surface 39a , 39b of the magnetic tape 35 is pressed.
  • each clamping zone 45a, 45b it is also possible in each clamping zone 45a, 45b to arrange a plurality of clamping projections in the circumferential direction 25a of the receiving groove 25 at a distance from each other. For example can this multiple clamping projections on only one and thereby be formed on the same groove flank 33a, 33b.
  • clamping zones 45a, 45b it is also possible, in one or both clamping zones 45a, 45b, to provide two clamping projections opposite to one another in the axial direction of the longitudinal axis 5 of the piston 4 on the two groove flanks 33a, 33b, which project towards each other and a constriction 48 for clamping the associated band end section 35a, Define 35b. In this case, only one or more pairs of such opposing clamping projections may be present per clamping zone 45a, 45b.
  • the piston body 16 in each of the two clamping zones 45a, 45b has a plurality of clamping projections 46a, 47a spaced apart from one another in the circumferential direction 25a of the receiving groove 25; 46b, 47b, that is, via a plurality of clamping projections, which are arranged offset in the circumferential direction of the receiving groove 25 to each other.
  • the clamping projections 46a, 47a; 46b, 47b in the respective clamping zone 45a, 45b are not each on the same groove flank 33a, 33b, but are arranged on different groove flanks 33a, 33b.
  • a first clamping projection 46a, 46b is integrally formed on the first groove flank 33a and a second clamping projection 47a, 47b spaced therefrom in the circumferential direction 25a of the receiving groove 25 on the second groove flank 33b.
  • a respective clamping projection 46a, 47a; 46b, 47b opposite region of the respective other groove flank 33a, 33b is preferably no clamping projection, where the respective groove flank 33a, 33b is designed as a clamping projection.
  • each band end portion 35a, 35b pressed into a pinching zone 45a, 45b winds with a slight wavy line in the circumferential direction 25a of the receiving groove 25 through the respective pinching zone 45a, 45b and is thereby effectively clamped.
  • this type of clamping it is not necessary that the between each clamping projection 46a, 47a; 46b, 47b and the opposite groove flank 33a, 33b measured clear distance A2 is smaller than the width B of the magnetic tape 35.
  • This clear distance A2 is suitably the same size as the width B magnetic tape 35 or even in this regard may be slightly larger.
  • the clamping effect results mainly from the fact that the magnetic tape 35 is meander-like deformed in each clamping zone 45a, 45b, that in particular in the clamping projections 46a, 47a; 46b, 47b adjacent areas with the groove flanks 33a, 33b is clamped.
  • the clamping effect is essentially based on the fact that the band end portions 35a, 35b in the clamping portions 45a, 45b are forced by the alternately on different groove flanks 33a, 33b clamping projections in a meandering or wavy or at least bent longitudinal shape and due to the elasticity of the magnetic tape 35 the Have a tendency to deform back into their linear initial shape, so that they clamp in the receiving groove 25 transversely to its circumferential direction 25a.
  • each clamping zone 45a, 45b the distance A4 measured in the circumferential direction of the receiving groove between the clamping projections 46a, 47a arranged on different groove flanks 33a, 33b; 46b, 47b so that it is at least as large as the width B of the magnetic tape and at most twice the width B of the magnetic tape.
  • a further clamping region 44a of the described structure at at least one point spaced apart in the circumferential direction of the piston body 16 from the clamping region 44.
  • This further clamping region 44a may then alternatively to the described clamping region 44 be used for fixing the two band portions 35a, 35b, when the magnetic tape 35 is inserted with a corresponding position in the receiving groove 25.
  • even more such clamping areas along the circumference of the piston body 16 may be distributed, but you will keep the number of clamping areas as low as possible, as they generally complicate the insertion of the magnetic tape 35 due to the achieved clamping effect.
  • the clamping projections 46a, 47a; 46b, 47b can basically be designed arbitrarily. It is important that they cause a local narrowing in the course of the receiving groove 25.
  • each clamping projection 46a, 47a; 46b, 47b according to Figures 2 and 3 is formed rib-shaped with elongated shape and extending from the region of the groove bottom 32 of the receiving groove 25 in the direction of the radial groove opening 26 of the receiving groove 25 respectively.
  • the clamping projections 46a, 47a; 46b, 47b have at their radial slot opening 26 facing end portion a radially outward and to the associated groove flank 33a, 33b extending chamfer 49.
  • the chamfers 49 form oblique guide surfaces which guide the respective band end section 35a, 35b into the receiving groove 25 in a targeted manner when the same is subjected to a pressing force during assembly from the radially outside.

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

Claims (16)

  1. Piston pour un dispositif de réglage pouvant fonctionner avec un fluide, en particulier pour un entraînement linéaire actionné par un fluide, comprenant un corps de piston (16) d'un seul tenant, qui présente, dans la zone de sa périphérie extérieure radiale, une rainure de réception (25) de forme annulaire coaxiale par rapport à l'axe longitudinal (5) du piston (4), pourvue de deux flancs de rainure (33a, 33b) latéraux tournés l'un vers l'autre, dans laquelle un ensemble d'aimants permanents (24) pouvant être utilisé aux fins de la détection de position est reçu, dans lequel l'ensemble d'aimants permanents (24) est constitué d'une bande magnétique (35) à aimantation permanente élastique liée en une structure annulaire, caractérisé en ce que la bande magnétique (35) présente deux sections de bande (35a, 35b) tournées l'une vers l'autre dans la direction périphérique de la rainure de réception (25) et dont la largeur est inférieure à la distance entre les deux flancs de rainure (33a, 33b) de la rainure de réception (25), dans lequel chacune des deux sections de bande (35a, 35b) est maintenue par serrage dans une zone de serrage parmi deux zones de serrage (45a, 45b), adjacentes l'une à l'autre dans la direction périphérique de la rainure de réception (25), de la rainure de réception (25), dans lesquelles le corps de piston (16) présente respectivement au moins une partie faisant saillie de serrage (46a, 47a ; 46b, 47b) faisant saillie par rapport à l'un des flancs de rainure (33a, 33b) en rétrécissant localement la rainure de réception (25) et exerçant une compression au niveau de la face latérale (39a, 39b) de la bande magnétique (35).
  2. Piston selon la revendication 1, caractérisé en ce que le corps de piston (16) présente dans chaque zone de serrage (45a, 45b) de la rainure de réception (25) plusieurs parties faisant saillie de serrage (46a, 47a ; 46b, 47b).
  3. Piston selon la revendication 1 ou 2, caractérisé en ce que le corps de piston (16) présente, dans chaque zone de serrage (45a, 45b) de la rainure de réception (25), plusieurs parties faisant saillie de serrage (46a, 47a ; 46b, 47b) disposées à distance les unes des autres dans la direction périphérique de la rainure de réception (25).
  4. Piston selon la revendication 3, caractérisé en ce qu'au moins deux parties faisant saillie de serrage (46a, 47a ; 46b, 47b) disposées à distance les unes des autres dans la direction périphérique de la rainure de réception (25) au niveau de flancs de rainure (33a, 33b) différents sont disposées dans chaque zone de serrage (45a, 45b), dans lequel respectivement aucune partie faisant saillie de serrage au niveau de l'autre flanc de rainure (33b, 33a) ne fait face auxdites parties faisant saillie de serrage (46a, 47a ; 46b, 47b).
  5. Piston selon la revendication 4, caractérisé en ce que dans la zone de serrage (45a, 45b) respective la petite distance (A3) projetée mesurée dans le sens de la longueur du piston (4) entre les deux parties faisant saillie de serrage (46a, 47a ; 46b, 47b) espacées l'une de l'autre dans la direction périphérique de la rainure de réception (25) est plus petite que la largeur (B) de la bande magnétique (35).
  6. Piston selon la revendication 4 ou 5, caractérisé en ce que la petite distance entre chaque partie faisant saillie de serrage (46a, 47a ; 46b, 47b) et le flanc de rainure (33a, 33b) faisant face de la rainure de réception (25) est aussi grande ou plus grande que la largeur (B) de la bande magnétique (35).
  7. Piston selon l'une quelconque des revendications 4 à 6, caractérisé en ce que dans chaque zone de serrage (45a, 45b), la distance (A4) mesurée dans la direction périphérique de la rainure de réception (25) entre les parties faisant saillie de serrage (46a, 47a ; 46b, 47b) disposées au niveau de flancs de rainure différents est au moins aussi grande que la largeur (B) de la bande magnétique (35) est présente une valeur au maximum égale au double de largeur (B) de la bande magnétique (35).
  8. Piston selon l'une quelconque des revendications 1 à 7, caractérisé en ce que précisément deux parties faisant saillie de serrage (46a, 47a ; 46b, 47b) sont disposées dans chacune des deux zones de serrage (45a, 45b).
  9. Piston selon l'une quelconque des revendications 1 à 8, caractérisé en ce que les parties faisant saillie de serrage (46a, 47a ; 46b, 47b) sont réalisées respectivement de manière à présenter une forme de nervure présenter une configuration allongée et s'étendent respectivement en partant de la zone du fond de rainure (32) de la rainure de réception (25) en direction de l'ouverture de rainure (26) radiale de la rainure de réception (25), et/ou que les parties faisant saillie de serrage (46a, 47a ; 46b, 47b) sont biseautées, dans leur zone d'extrémité tournée vers l'ouverture de rainure (26) radiale en direction du flanc de rainure (33a, 33b) associé.
  10. Piston selon l'une quelconque des revendications 1 à 9, caractérisé en ce que la bande magnétique (35) a une section transversale rectangulaire, et/ou que la bande magnétique (35) présente un corps de bande en forme de boudin composé d'un matériau en plastique élastiquement déformable, qui est pourvu de moyens à aimantation permanente.
  11. Piston selon l'une une quelconque des revendications précédentes 1 à 10, caractérisé en ce que le corps de piston (16) est constitué d'un matériau rigide, de manière appropriée de métal.
  12. Piston selon l'une quelconque des revendications 1 à 11, caractérisé en ce que le corps de piston (16) présente, au niveau de deux zones périphériques diamétralement opposées, respectivement une région de serrage (44, 44a), disposant de deux zones de serrage (45a, 45b) adjacentes l'une à l'autre, pour la bande magnétique (35), dans lequel les deux régions de serrage (44, 44a) peuvent être utilisées en variante aux fins du serrage des deux sections de bande (35a, 35b).
  13. Piston selon l'une quelconque des revendications 1 à 12, caractérisé en ce que la rainure de réception (25) de forme annulaire est entourée de manière concentrique par un renfoncement de maintien (23) de forme annulaire réalisé dans le corps de piston (16), dans lequel elle est plus étroite que le renfoncement de maintien (23) et débouche, par son ouverture de rainure (26) située radialement à l'extérieur, dans le fond de renfoncement (27) du renfoncement de maintien (23), dans lequel une bande de guidage (22) recouvrant radialement côté extérieur la bande magnétique (35), structurée de manière à présenter une forme annulaire est maintenue dans le renfoncement de maintien (23).
  14. Piston selon l'une quelconque des revendications 1 à 13, caractérisée en ce qu'est réalisé, dans la région de la périphérie extérieure radiale du corps de piston (16), un renfoncement de maintien (23) de forme annulaire coaxial par rapport à l'axe longitudinal (5) du piston (4), pourvu de deux flancs de renfoncement (28a, 28b) latéraux tournés l'un vers l'autre, dans lequel est maintenue une bande de guidage (22) présentant une structure annulaire, qui présente deux sections de bande (22a, 22b) tournées l'une vers l'autre dans la direction périphérique du renfoncement de maintien (23), dans lequel les deux flancs de renfoncement (28a, 28b) du renfoncement de maintien (23) ont, vus en coupe transversale, respectivement un profilage contre-dépouillé et présente respectivement, à une distance radiale du fond de renfoncement (27) du renfoncement de maintien (23), une partie faisant saillie de maintien (38a, 38b) de forme annulaire dépassant en direction du flanc de renfoncement (28b, 28a) faisant face, laquelle partie faisant saillie de maintien est en prise par complémentarité de forme avec le bord latéral (37a, 37b) tourné de la bande de guidage (22).
  15. Piston selon la revendication 14, caractérisé en ce que les parties faisant saillie de maintien (38a, 38b) sont enfoncées dans le bord latéral (37a, 37b) respectivement associé de la bande de guidage (22) en déformant localement la bande de guidage (22) et en réalisant une prise par complémentarité de forme, dans lequel la bande de guidage (22) a de manière appropriée une section transversale rectangulaire dans l'état de départ, dans lequel elle n'est pas encore montée dans le renfoncement de maintien (23).
  16. Dispositif de réglage pouvant fonctionner avec un fluide, en particulier entraînement linéaire actionné par un fluide, comprenant un boîtier (2), dans lequel est disposé un piston (4) de manière à pouvoir coulisser de manière linéaire, caractérisé en ce que le piston (4) est réalisé selon l'une quelconque des revendications 1 à 15.
EP14796715.2A 2014-11-12 2014-11-12 Piston et un positionneur equipé avec le piston Active EP3164610B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/EP2014/003034 WO2016074691A1 (fr) 2014-11-12 2014-11-12 Piston et dispositif de réglage équipé de ce dernier

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EP3164610A1 EP3164610A1 (fr) 2017-05-10
EP3164610B1 true EP3164610B1 (fr) 2017-10-18

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EP (1) EP3164610B1 (fr)
KR (1) KR20170082500A (fr)
CN (1) CN107076179B (fr)
WO (1) WO2016074691A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102017115481B4 (de) * 2017-07-11 2022-09-01 Schaeffler Technologies AG & Co. KG Doppelmagnethalterung für einen Kolben eines CSCs mit Sensor und Nehmerzylinder mit Doppelmagnethalterung

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Publication number Priority date Publication date Assignee Title
US3639868A (en) * 1971-03-17 1972-02-01 Bimba Mfg Co Magnetic switch mounting means for a fluid motor unit
DE2947516C2 (de) * 1979-11-24 1981-09-03 Festo-Maschinenfabrik Gottlieb Stoll, 7300 Esslingen Kolben für berührungslose Abtastung der Kolbenstellung
DE3731158A1 (de) * 1987-09-17 1989-03-30 Festo Kg Kolben-zylinder-aggregat
JP4063402B2 (ja) * 1998-05-27 2008-03-19 株式会社アミテック シリンダ位置検出装置
DE202005005508U1 (de) * 2005-04-07 2005-06-02 Festo Ag & Co. Kolben und damit ausgestattete fluidbetätigte Stellvorrichtung
DE202005010618U1 (de) * 2005-07-06 2005-09-29 Festo Ag & Co. Kolben für einen Arbeitszylinder
CN201062601Y (zh) * 2007-07-27 2008-05-21 毛信强 二级缓冲活塞式气缸
DE102011120596A1 (de) * 2011-12-08 2013-06-13 Trw Automotive Gmbh Kolben für eine doppeltwirkende Kolben-Zylinder-Einheit und hydraulische Servolenkung mit einem solchen Kolben

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Publication number Publication date
CN107076179B (zh) 2018-11-30
CN107076179A (zh) 2017-08-18
EP3164610A1 (fr) 2017-05-10
KR20170082500A (ko) 2017-07-14
WO2016074691A1 (fr) 2016-05-19

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