EP2350463A1 - Tube de carter et entraînement linéaire équipé de ce dernier - Google Patents

Tube de carter et entraînement linéaire équipé de ce dernier

Info

Publication number
EP2350463A1
EP2350463A1 EP10709403A EP10709403A EP2350463A1 EP 2350463 A1 EP2350463 A1 EP 2350463A1 EP 10709403 A EP10709403 A EP 10709403A EP 10709403 A EP10709403 A EP 10709403A EP 2350463 A1 EP2350463 A1 EP 2350463A1
Authority
EP
European Patent Office
Prior art keywords
housing tube
inner part
housing
tube according
outer part
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.)
Granted
Application number
EP10709403A
Other languages
German (de)
English (en)
Other versions
EP2350463B1 (fr
Inventor
Harald Röhrig
Ulrich Kees
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 EP2350463A1 publication Critical patent/EP2350463A1/fr
Application granted granted Critical
Publication of EP2350463B1 publication Critical patent/EP2350463B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • F15B15/149—Fluid interconnections, e.g. fluid connectors, passages
    • 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
    • F15B15/1428—Cylinders

Definitions

  • the invention relates to a housing tube of a linear drive, whose wall is penetrated by a plurality of axially continuous, circumferentially distributed housing channels, which are formed by arranged on the inner circumference of a tubular outer part longitudinal recesses, which are covered radially inwardly by an enclosed by the outer part tubular inner part are.
  • the invention relates to a fluid-actuated linear drive equipped with such a housing tube, in which the tubular inner part defines the running surface for a drive piston.
  • An equipped with a housing tube of the aforementioned type, designed as a pneumatic cylinder linear drive is known from DE 10 2007 029 628 B3. It has a two-shell housing tube, in the wall of which one or more housing channels are provided for accommodating an attachment.
  • Housing channels are composed of a formed on the inner circumference of the tubular outer part longitudinal recess and the longitudinal recess covering the wall portion of the tubular inner part together.
  • the wall section performing the covering function is designed in the manner of a base with a flat base surface and dips over the entire width into the associated longitudinal recess.
  • the required specific design of the cross section of the tubular inner part has relatively high tooling costs result and results due to the large wall thickness in a high weight and material requirements.
  • a known from DE 199 25 600 Al hydraulic cylinder has a housing tube of two coaxially arranged inside circular cylindrical outer and inner parts.
  • Cross-sectional shapes can be realized very inexpensively.
  • housing channels in the cylinder wall however, resorted to a variety of strip-shaped pressure pieces, which must be used between the inner part and the outer part, resulting in a very time-consuming assembly of the hydraulic cylinder result.
  • the object is also achieved by a fluid-actuated linear drive whose housing has a built-up according to the aforementioned specifications housing tube. Due to the convexly curved outer contour of the longitudinal recesses covering wall sections, the tubular inner part can be produced very inexpensively with relatively simple tools. Conveniently, the convex outer contours of each of a longitudinal recess covering the wall portions of the inner part together on an imaginary cylindrical surface or cylindrical surface.
  • the housing can be realized particularly favorably in the case of an inner part whose inner circumference is cylindrically contoured, that is to say, for example, with a circular or elliptical or oval
  • Cross-section since it has the opportunity here, at least for the most part to form the wall sections covering the longitudinal recesses with a constant wall thickness.
  • a particularly advantageous embodiment provides that the inner part is cylindrical outside and in particular has a continuous circumferential course, which, among other things, offers the advantageous possibility of forming the inner part over the entire circumference with a constant wall thickness.
  • the joining of the outer part and the inner part take place without special mutual angular alignment, which keeps the assembly effort low, especially when the outer part and inner part for assembling the housing tube are inserted axially into one another.
  • the two-shell construction of the housing tube also offers the advantageous possibility of very easily combining different materials with one another in order to be able to take into account the most diverse applications and demands.
  • the circumference of the housing tube is intentionally subdivided into four adjoining peripheral sections each having a 90 ° circumferential extent, it is advantageous if one or more of the housing channels formed according to the invention are present in each of these four peripheral sections.
  • Diametrically opposite wall sections may in particular be formed point-symmetrically with respect to the longitudinal axis extending through the center of the inner part.
  • the outer contour of the housing tube is expediently formed by an outer envelope wall of the tubular outer part.
  • This envelope wall integrally connected, radially inwardly projecting web-shaped partitions can divide adjacent housing channels of each other and can also be used with appropriate design to support the outer part with respect to the inner part by contact with its outer surface.
  • One or more of the housing sections covered by wall sections of the inner part can each form a receiving channel in which extends in a finished linear drive, a tie rod, which is used to axially clamp the frontally arranged housing cover with the housing tube.
  • a receiving channel in which extends in a finished linear drive
  • a tie rod which is used to axially clamp the frontally arranged housing cover with the housing tube.
  • anti-rotation rib which is radially engaged with the tie rod.
  • one or more rib-shaped anti-rotation projections projecting radially outward may be present on the inner part for this purpose, which engage in the outer part.
  • at least one pair of anti-rotation ribs spaced apart from each other in the circumferential direction of the inner part can be present, wherein the anti-rotation ribs of this pair can each engage in one of the longitudinal recesses formed on the outer part for the purposes of preventing rotation, in order to bear against the lateral boundary surfaces thereof.
  • the two anti-rotation ribs can engage in different longitudinal recesses or in the same longitudinal recess.
  • the measured in the circumferential direction of the inner part width of the anti-rotation ribs is smaller than that of the opening of the associated longitudinal recess, so that the desired anti-rotation effect can be achieved with a minimum of material.
  • outer part is valid that it is expediently outside substantially rectangular and in particular square contoured, in particular with rounded corners.
  • the limited cross section of the inner part is expediently round, in particular circular or elliptical or oval.
  • one or more longitudinally extending anchoring grooves can be formed, in which additional parts, in particular sensors, can be detachably fixed.
  • additional parts in particular sensors
  • the anchoring grooves are particularly advantageous here to arrange the anchoring grooves so that their longitudinal center planes are aligned with the center of the inner part.
  • the groove base may in particular be provided on a wall portion of the outer part, which is supported directly on the outer circumference of the inner part. This wall portion may have a very small wall thickness, so that any installed sensors occupy the smallest possible radial distance from the inner peripheral surface of the inner part.
  • the outer part consists of a plastic material and the inner part of metal.
  • a reversed choice of materials is also possible. It is also possible to coat the inner peripheral surface of the inner part regardless of the respective choice of material with a nanomaterial to ensure a low-friction movement of the recorded drive piston. In this case, it may be possible to dispense with an additional lubricant.
  • the multi-shell construction of the housing tube makes it possible in the
  • FIG. 1 is an overall perspective view of a preferred embodiment of the linear drive according to the invention, which is equipped with a particularly advantageous embodiment of the housing tube according to the invention,
  • FIG. 2 shows a longitudinal section through the longitudinal central axis of the apparent from Fig. 2 linear drive
  • FIG. 4 is an end view of the present in the linear drive according to FIG. 1 to 3 housing tube in a single view with a line of sight according to section line IV-IV,
  • Fig. 5 is a longitudinal section of the housing tube in a perspective view
  • Fig. 6 in a comparable with Fig. 4 representation, a modified embodiment of the housing tube.
  • the total designated by reference numeral 1 linear actuator is operated with a fluidic pressure medium, which is in particular compressed air.
  • a fluidic pressure medium which is in particular compressed air.
  • Other gaseous media or liquids could also be used for actuation.
  • the housing 2 is composed of a housing tube 4 and two first and second housing covers 5, 6 arranged on the two end faces of the housing tube 4.
  • the housing covers 5, 6 are expediently attached to the respectively associated, axially oriented end face 7 of the housing tube 4.
  • the housing cover 5, 6 are clamped axially by tie rods 8 with the housing tube 4.
  • tie rods 8 are present, of which in Fig. 4 and 5, however, only two pieces are shown.
  • the tie rods 8 are, viewed in cross section, placed in the four corners of an imaginary square and thus arranged at an offset of 90 ° about the longitudinal axis 3 around.
  • Each tie rod 8 has a the tube wall 14 of the housing tube 4 axially passing through tie rod 12 which is bolted to both ends with a respective fastening screw 13, which is supported with its head on the associated housing cover 5, 6. It could also be present less than four tie rods, for example, only two pieces, which then expediently opposite to the longitudinal axis 3 diametrically opposite.
  • the tie rods 12 are tubular and the fastening screws 13 are screwed into the hollow Switzerlandankerstäbe 12, in particular by means of self-tapping thread.
  • FIG. 6 illustrates that the tube wall 14 of the housing tube 4 can also be penetrated by fastening channels 15, into which the fastening screws 13 for fixing the housing cover 5, 6 can be screwed directly, so that no tie rods 8 are required.
  • This variant can be used in particular if the sections of the pipe wall 14 defining the fastening channels 15 are made of metal, for example of aluminum material.
  • the housing tube 4 is in principle arbitrary in its outer contour and may in particular also be circular. However, a design with a rectangular and preferably square outer contour is preferred, as is the case in the exemplary embodiment. The edges are expediently rounded.
  • the housing tube 4 bounded together with the two housing covers 5.6 a housing interior 16 in which a drive piston 17 is arranged linearly displaceable in the axial direction of the longitudinal axis 3.
  • the housing interior 16 is bounded radially by a preferably cylindrical, arranged on the housing tube 4 tread 18, on which the drive piston 17 is slidably applied.
  • the drive piston 17 of the housing interior 16 is axially divided into a first housing cover 5 associated first working chamber 22 and the second housing cover 6 associated second working chamber 23.
  • the drive piston 17 preferably carries, in the region of its outer circumference, an annular seal arrangement 24 which bears dynamically on the running surface 18 in a sealing manner.
  • each working chamber 22, 23 opens on the other hand to the outer surface of the housing 2 ausmündender own control channel 25a, 25b.
  • the ar- Beitshuntn 22, 23 controlled by a pressure medium are applied to cause the already mentioned, indicated by a double arrow linear stroke movement 26 of the drive piston 17.
  • the pressure medium can be connected to the outer 5 orifices of the control channels 25a, 25b and fluid lines leading off.
  • An output member 27 movably coupled to the drive piston 17 makes the lifting movement 26 possible and enables the tapping movement 26 to be picked up outside the housing 2.
  • the output member 27 is designed as a piston rod 27a, which is fastened to the drive piston 17 and passes through the first housing cover 5 in a slidable manner .
  • An annular sealing device 28 arranged on the first housing cover 5 surrounds the piston rod 27a and prevents i5 fluid leakage from the adjoining first working chamber 22.
  • a bearing bush 32 likewise fixed to the first housing cover 5 surrounds the piston rod 27a and ensures a sliding bearing of the same.
  • the output part 27 could, for example, as alongside alongside alongside
  • housing tube 4 arranged carriage may be formed, which is drivingly connected, for example, by magnetic force to the drive piston 17.
  • the housing tube 4 has expediently a bivalve structure.
  • the outer shell is a tubular outer part 33.
  • the inner shell is formed by a respect to the outer part 33 separate tubular inner part 34 which is completely surrounded by the outer part 33 radially outward.
  • the two equally long parts 33, 34 are inserted into one another with slight radial prestressing.
  • outer part 33 and inner part 34 together form the pipe wall 14 of the housing tube 4.
  • This is axially interspersed by a plurality of cavities, so that the housing tube 4 despite high stability has a low weight.
  • At least some of the cavities are bounded along part of their circumference by the wall 35 and along another part of their circumference by the wall 36, ie are defined jointly by the outer part 33 and the inner part 34.
  • housing channels 42 - are jointly formed by one on the inner circumference of the outer part 33 arranged longitudinal recess 43 and a radially inwardly directed recess opening 44 of the longitudinal recess 43 from radially inside covering wall portion 45 of the wall 36 of the Inner part 34.
  • the aforementioned wall sections 45 are also referred to below as covering wall sections 45.
  • cover wall portions 45 have a convexly curved outer contour. Each recess opening 44 is therefore closed by a covering wall section 45 having a convexly curved outer surface.
  • outer part 33 and inner part 34 are expediently based on the presence of a plurality of in the circumferential direction around the inner part 34 around, radially inwardly facing support surfaces 46 which bear against the outer peripheral surface 47 of the wall 36 of the inner part 34.
  • Each support surface 46 is strip-shaped and extends over the entire length of the outer part 33. Viewed in cross section according to FIGS. 4 and 6, the support surfaces 46 are in both embodiments on a circular line with the longitudinal axis 3 as the center.
  • the outer peripheral surface 47 of the inner member 34 is made cylindrical as a whole and has a continuous course in the circumferential direction without projections or steps.
  • the inner contour of the inner part 34, 5 which forms the tread 18 is preferably also cylindrical, which is advantageously round the same radial wall thickness results for the wall 36.
  • the outer contour and inner contour of the inner part 34 is circular. Other shapes, such as elliptical lo or oval are also possible. Uncircular inner contours of the inner part 34 are selected, in particular, if an antirotation of the drive piston 17 bearing against the running surface 18 is desired solely by the shaping.
  • the inner part 34 of the exemplary embodiment according to FIG. 6 differs from that of FIGS. 1 to 5 only in that, on its outer circumference, a plurality of radially outwardly extending, linearly extending axes in the longitudinal axis 3 over the entire length of the inner part 34 rib-shaped anti-rotation projections 48 are present. They cause a 20 over frictional measures beyond, based on positive locking rotation between the outer part 33 and inner part 34.
  • the anti-rotation projections 48 which are integral part of the wall 36, each engage a piece radially into one of the longitudinal recesses 43 and are supported in the circumferential direction on lateral boundary surfaces 52 of the longitudinal recesses 43, which adjoin the recess openings 44.
  • the anti-rotation projections 48 are assigned to each other expediently in pairs. As an example, four such 30 pairs of anti-rotation projections 48 are present.
  • Anti-rotation projections 48 engage each of these four pairs preferably in different longitudinal recesses 43, wherein they rest on facing in opposite circumferential directions boundary surfaces 52. In this way, the inner part 34 can rotate neither in one direction nor in the other direction with respect to the outer part 33.
  • All rib-shaped anti-rotation projections 48 are advantageously common that their measured width in the circumferential direction of the inner part 34 is substantially smaller than that of the recess opening 44. Between circumferentially successive recess projections 48, the outer peripheral surface 47 has a convexly curved contour. All convex outer contour sections of the inner part 34 lie on a common imaginary cylindrical surface.
  • the outer contour of the housing tube 4 is determined by the contour of the wall 35. This is thus designed in the embodiment substantially rectangular and in particular square, in particular with rounded corners.
  • Some further of the support surfaces 46 are formed in the embodiments of hereinafter referred to as bottom portions 55 wall portions of the outer envelope wall 53, which define the groove bottom in the axial direction of the longitudinal axis 3 extending anchoring grooves 56 which by corresponding contouring of the outer envelope wall 53 in the outer contour of the outer part 33 are formed.
  • anchoring grooves 56 which by corresponding contouring of the outer envelope wall 53 in the outer contour of the outer part 33 are formed.
  • These are undercut grooves which serve to fix sensors or other additional parts that can be used outside to the outer part 33 for detecting the position of the drive piston 17.
  • the drive piston 17 carries a preferably annular permanent magnet 57, to which the said sensors can respond.
  • longitudinal center planes 58 thus extend in the radial and axial directions, wherein they include the longitudinal axis 3.
  • the support surfaces 46 formed on the bottom portions 55 may be concavely curved according to the curved outer contour of the inner part 34.
  • the wall sections of the enveloping wall 53 that contain the base sections 55 and define the anchoring grooves 56 can also each function as partitions between circumferentially successive housing channels 42.
  • a plurality of the housing channels 42 each form a receiving channel 62 for one of the already mentioned tie rods 12. It is advantageous if the inserted tie rod 12 is not applied to the inner part 34 and is not in contact with the envelope wall 53. It is expedient if in at least one and expediently in each of the AufnähmekanäIe 62 more than 35 formed as integral components of the outer part 33 support ribs 63 project, which extend expediently over the entire length of the outer part 33 and at circumferentially distributed locations on the outer circumference of the tie rod Abut 12 to radially support and fix it.
  • a total of four support ribs 63 offset by 90 ° from one another are provided per receiving channel 62, which are arranged around a receiving region 64 of the receiving channel 62, into which the tie rod 12 can be inserted.
  • An inserted tie rod 12 is radially supported and centered by the support ribs 63.
  • the exemplary embodiment also has the special feature that the support ribs 63 each fulfill a dual function and, moreover, also function as anti-rotation ribs 65 for securing the associated tie rods 12 in a manner secure against rotation.
  • the tension rod rods 12 have longitudinally extending anti-rotation grooves 66 on the outer circumference, into each of which one of the anti-rotation ribs 65 dips.
  • the support ribs 63 and anti-rotation ribs 65 could also be formed separately.
  • a tie rod 12 is inserted into the receiving area 64, it subdivides the receiving channel 62 together with the supporting ribs 63 into a plurality of receiving channel subspaces arranged around the tie rod 12.
  • the tube wall 14 may extend around the longitudinal axis 3 via four adjoining peripheral sections each having a circumferential extent of at least 90 °, wherein a plurality of housing channels covered by the inner section are expediently formed in each of these four peripheral sections ,
  • Housing channels 42 do not all have to be identical, but may well differ from each other in their cross-sectional contour.
  • outer part 33 can optionally be equipped with inner parts 34 of different materials.
  • inner parts 34 of different materials.
  • a modular system for housing tubes can be realized, in which different outer parts 33 and / or different inner parts
  • outer part 33 and inner part 34 are provided, which can be combined with each other as needed. All designs have a low weight in common.
  • the preferred production of outer part 33 and inner part 34 takes place as an extruded profile.
  • a metal version of an outer part 33 could well but also from a folded
  • housing channels 42 may be foamed to increase the stability of the overall structure.
  • the foaming is expediently carried out after the outer part 33 and the inner part 34 have been joined together.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Professional, Industrial, Or Sporting Protective Garments (AREA)

Abstract

L'invention concerne un tube de carter (4) pour un entraînement linéaire dont la paroi (14) est traversée en continu et axialement par plusieurs canaux (42) répartis sur la périphérie. Les canaux (42) sont formés par des cavités longitudinales (43) disposées à la périphérie intérieure d'une partie tubulaire externe (33), lesdites cavités longitudinales (43) étant recouvertes radialement à l'intérieur par une partie tubulaire interne (34) entourée par la partie tubulaire externe (33). Les segments de paroi (45) de la partie interne (34) qui recouvrent les cavités longitudinales (43) présentent un contour externe convexe. L'invention concerne également un entraînement linéaire actionné par un fluide et équipé d'un tel tube de carter (4).
EP10709403.9A 2009-03-25 2010-03-06 Tube de carter et entraînement linéaire équipé de ce dernier Not-in-force EP2350463B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009014815A DE102009014815A1 (de) 2009-03-25 2009-03-25 Gehäuserohr und damit ausgestatteter Linearantrieb
PCT/EP2010/001404 WO2010108589A1 (fr) 2009-03-25 2010-03-06 Tube de carter et entraînement linéaire équipé de ce dernier

Publications (2)

Publication Number Publication Date
EP2350463A1 true EP2350463A1 (fr) 2011-08-03
EP2350463B1 EP2350463B1 (fr) 2013-07-24

Family

ID=42257513

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10709403.9A Not-in-force EP2350463B1 (fr) 2009-03-25 2010-03-06 Tube de carter et entraînement linéaire équipé de ce dernier

Country Status (4)

Country Link
EP (1) EP2350463B1 (fr)
CN (1) CN102362077A (fr)
DE (1) DE102009014815A1 (fr)
WO (1) WO2010108589A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014145557A2 (fr) * 2013-03-15 2014-09-18 Actuant Corporation Ensemble de cylindre hydraulique
CN104533878B (zh) * 2014-12-31 2017-01-11 嘉兴米克气动设备有限公司 位置可任意移动式中间轴耳安装结构
DE102017115653A1 (de) * 2017-07-12 2019-01-17 Festool Gmbh Saugschlauch für einen Staubsauger
WO2024125769A1 (fr) * 2022-12-13 2024-06-20 Festo Se & Co. Kg Kit de construction pour la production d'un cylindre de travail actionné par un fluide
WO2024125768A1 (fr) * 2022-12-13 2024-06-20 Festo Se & Co. Kg Cylindre moteur actionné par un fluide

Family Cites Families (8)

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Publication number Priority date Publication date Assignee Title
DE4408639C2 (de) * 1994-03-09 1998-04-16 Mannesmann Ag Arbeitszylinder mit einem Zylindergehäuseprofil
JP3780052B2 (ja) * 1997-01-16 2006-05-31 Ｓｍｃ株式会社 流体圧機器におけるスイッチ取付機構
JP3150078B2 (ja) * 1997-05-30 2001-03-26 エスエムシー株式会社 溝カバー付き流体圧シリンダ
DE19925600A1 (de) 1999-06-04 2000-12-14 Sbs Sondermaschinen Gmbh Leichtbau-Hydraulikzylinder mit Zugankern
DE20110965U1 (de) 2001-07-03 2001-09-06 FESTO AG & Co., 73734 Esslingen Arbeitszylinder
JP3780187B2 (ja) 2001-08-31 2006-05-31 Ｓｍｃ株式会社 流体圧シリンダ用シリンダチューブ
EP1978262B1 (fr) * 2007-04-03 2016-05-25 FESTO AG & Co. KG Dispositif d'entraînement
DE102007029628B3 (de) 2007-06-26 2009-01-15 Robert Bosch Gmbh Pneumatikzylinder mit einem Zylindergehäuse aus stranggepresstem Metall

Non-Patent Citations (1)

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Title
See references of WO2010108589A1 *

Also Published As

Publication number Publication date
DE102009014815A1 (de) 2010-09-30
CN102362077A (zh) 2012-02-22
WO2010108589A1 (fr) 2010-09-30
EP2350463B1 (fr) 2013-07-24

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