WO2016188525A1 - Unité de serrage mécanique à sabot - Google Patents

Unité de serrage mécanique à sabot Download PDF

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Publication number
WO2016188525A1
WO2016188525A1 PCT/DE2016/200229 DE2016200229W WO2016188525A1 WO 2016188525 A1 WO2016188525 A1 WO 2016188525A1 DE 2016200229 W DE2016200229 W DE 2016200229W WO 2016188525 A1 WO2016188525 A1 WO 2016188525A1
Authority
WO
WIPO (PCT)
Prior art keywords
clamping unit
spring
adjusting element
zugmittelleitschiene
end position
Prior art date
Application number
PCT/DE2016/200229
Other languages
German (de)
English (en)
Inventor
Johanna Mayer
Christopher Krawietz
Original Assignee
Schaeffler Technologies AG & 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 Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2016188525A1 publication Critical patent/WO2016188525A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F16H2007/0851—Wedges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0872—Sliding members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0893—Circular path

Definitions

  • the invention relates to a clamping unit, namely a mechanical wedge clamping unit for clamping a endless traction means of a traction mechanism, preferably a chain of a chain drive of an internal combustion engine, such as a gasoline or diesel engine, a motor vehicle, such as a motorcycle, with a Switzerlandstoffleitschiene, one for attachment to an internal combustion engine fixed Has storage area prepared pivot bearing point, and with an actuating element, which is slidably received along a guideway formed on the Switzerlandstoffleitschiene and forms a preferably obliquely employed to the guideway supporting surface.
  • the invention also relates to a traction mechanism drive with a continuous traction means and this endless traction means in a load strand or slack exciting clamping unit.
  • DE 10 2008 051 143 A1 discloses a tensioning device for compensating for elongations of a traction mechanism, with a tensioning means, wherein a tensioning element is arranged between the tensioning means and a support surface on the internal combustion engine.
  • the tensioning element is guided on a raceway of the tensioning means and designed as a clamping piece, wherein the raceway forms an angle relative to the supporting surface of the internal combustion engine.
  • the adjusting elements / clamping elements of these clamping units can fall off the guideway, in particular during the transport of the clamping unit. This is due in particular to the fact that the adjusting elements are prevented in any case from falling down due to the clamping forces occurring during operation in at least one displacement direction in a state installed on the internal combustion engine due to the support of the actuating element anyway.
  • transport in which still no supporting force acts on the actuator and this actuator not yet by the geometric installation conditions in the shift range is held, it may happen under certain circumstances, that solves this control elements of the guideway automatically.
  • the actuator By such a captive the actuator is permanently and safely held during transport on the guideway. An accidental slipping by occurring during transport, usual vibrations is thereby avoided.
  • the actuating element is biased by a compression spring in one direction (preferably in a first displacement direction) away from the pivot bearing point.
  • a compression spring in one direction (preferably in a first displacement direction) away from the pivot bearing point.
  • the compression spring is also guided along its spring travel by means of a spring dome in at least part of the displacement region of the control element, i. supported laterally / transversely to the displacement area / to the guideway, a particularly stable and reproducible bias is implemented by the compression spring.
  • the spring dome has a cross-shaped cross section.
  • the spring dome can be produced particularly effectively by means of an injection molding process from a plastic material.
  • the spring dome continues to be at a free end region, ie an end region, of a base region of the spring dome connected to the Switzerlandstoffleitschiene is turned away, chamfered / chamfered, it is avoided that the spring dome collides in operation with an internal combustion engine fixed area. As a result, damage to the spring dome is avoided. It is also expedient if the actuating element rests in a first end position of the displacement region against a first stop web of the Werstoffleitschiene (preferably in a second direction of displacement). As a result, the captive in a first stop / a first limit is particularly simple.
  • the actuating element is in a, opposite the first end position, the second end position of the displacement region (preferably in the first displacement direction) to a second stop web of Switzerlandstoffleitschiene, also a second stop / a second boundary of the captive is simply formed.
  • the actuating element has two elastic encompassing arms which are elastically deformable in such a way that they can be positively snapped / snapped onto the guideway. This makes it possible to mount the actuator particularly easy on the guideway.
  • the guideway is rail-shaped / rail-like and has an elongate head portion which is encompassed by the Umgreifungsarmen the adjusting element form-fitting manner.
  • the Umgreifungsarme are then so far elastically deformable / deformable relative to each other / expandable that they can be pushed over the head region on the guideway. As a result, the assembly of the actuating element is further simplified.
  • a Einhakinate is designed on the actuator, which is prepared for receiving a setting tool.
  • a tool for example a hook or the like
  • the hooking eye of the adjusting element can then be grasped and this can be returned to the starting position (counter to the acting spring force of the compression spring) in the installation or reset case.
  • the Switzerlandstoffleitschiene suitably on a support body on which the guide rail is formed, wherein the support body is configured such that its free end under the clamping forces occurring during operation is elastically deformable by 1 mm to 3mm.
  • the free end of the supporting body is in this case that end which projects beyond the contact region of the supporting surface of the adjusting element with a combustion engine-resistant counter-surface on a side remote from the pivot bearing point.
  • the length of the free end is determined by the axial position of the actuating element on the guideway. It is particularly preferred if the free end can still be deformed by a distance of 1 mm to 3 mm in the first end position for a displacement position of the actuating element.
  • the invention thus relates to a mechanical
  • Tensioner / a mechanical clamping unit with a wedge-shaped sliding element (adjusting element).
  • the mechanical tensioner (clamping unit) is designed in particular for use in chain drives.
  • a wedge is provided as a sliding element, wherein this sliding element is supported by a supporting force of a spring / pressure spring such that the sliding element is pressed / biased in a direction away from a pivot bearing point / a center of rotation Buchstoffleitschiene the clamping arm.
  • FIG. 1 is a side view of a clamping unit according to the invention according to an advantageous embodiment, wherein the clamping unit is inserted in a schematically shown, a endless traction means having traction mechanism within an internal combustion engine and biased against the endless traction means, an isometric view of the clamping unit used in FIG the shift range of the control element is particularly easy to recognize
  • Fig. 3 is a side view of the clamping unit of FIG. 1, wherein the adjusting element now in a first end position, adjacent to a first stop web of the Switzerlandstoffschiene, is shifted and the clamping rail is set in a first wedge angle,
  • Fig. 4 is a side view of the clamping unit according to FIGS. 1 and 3, wherein the
  • Adjusting element is now arranged in a second end position, in which the compression spring which biases the actuating element is extended / relaxed and the actuator abuts against a second stop web of Switzerlandstoffleitschiene, wherein the second wedge angle generated by the actuating element is smaller than the first wedge angle 3,
  • Fig. 5 is an isometric view of the clamping unit of FIG. 2, wherein the
  • FIGS. 1 to 5 showing the two free end end deflection end positions that are acceptable in operation
  • Federdoms which serves for the lateral support of the compression spring during operation of the clamping unit and has a chamfered end portion
  • Fig. 8 is a plan view of the spring dome of FIG. 7, wherein the cross-shaped
  • Fig. 9 is an isometric view of the clamping unit together with the traction drive schematically shown in FIG. 1, wherein an adjusting tool is hooked into the Einhakinate on the actuator to adjust this actuator along the guideway.
  • the figures are merely schematic in nature and are for the sole purpose of understanding the invention. The same elements are provided with the same reference numerals.
  • the clamping unit 1 according to the invention according to an advantageous embodiment is shown in Fig. 1 clearly arranged.
  • the tensioning unit 1 is designed and prepared in the usual way for guiding and tensioning a pulling means 2, which is shown schematically here and designed as an endless traction means.
  • the traction means 2 is designed as a chain / drive chain and connects an output shaft 19 (designed as a crankshaft) of the clarity not shown in detail internal combustion engine (gasoline or diesel engine) of a motor vehicle, preferably a motorcycle, but alternatively also a car, truck, bus or agricultural utility vehicle, with a drive shaft 20, which is designed here as a camshaft of the internal combustion engine.
  • the clamping unit 1 is therefore part of a traction mechanism drive 21 of the internal combustion engine together with the traction means 2 and a further guide rail 22.
  • the clamping unit 1 is designed as a mechanical clamping unit, namely as a mechanical wedge clamping unit.
  • the bias of a Switzerlandstoffleitschiene 3 of the clamping unit 1 against the traction means 2 / the chain is carried out, as explained in more detail below, by means of a resiliently biased adjusting element 5.
  • the traction means 2 is biased in a load strand or an empty strand by means of the clamping unit 1.
  • the clamping unit 1 is designed both with a Switzerlandstoffleitschiene 3 and with the adjusting element 5, which is also referred to as a clamping element or wedge element / wedge clamping element.
  • a Weritzleitschiene 3 namely on a support body 17 of Switzerlandstoffleitschiene 3, is a
  • Swivel bearing 4 designed in the form of a sleeve-shaped receiving area.
  • This pivot bearing 4 is used in the attached state / in the operating state of the clamping unit 1 for pivotally securing by means of a fastener, not shown here in detail, such as a bolt, on a combustion engine fixed storage area.
  • a fastener not shown here in detail, such as a bolt
  • the Switzerlandstoffleitschiene 3 is integrally mounted during operation of the internal combustion engine pivotally mounted on the combustion engine fixed storage area / recorded.
  • the Ceintzleitschiene 3 on a sliding coating 24, which is prepared for sliding attachment, ie for biasing the traction means 2.
  • Sliding surface 24 is positively mounted on the support body 17 and forms an elongated sliding surface 25, along which the traction means 2 is slidably guided during operation.
  • Supporting body 17 and sliding coating 24 are each made of a plastic.
  • the sliding lining 24 is made of a different plastic material than the supporting body 17.
  • the supporting body 17 is furthermore produced (entirely in one production step) by injection molding from a plastics material in an injection molding process.
  • the support body 17 has a plurality of reinforcing ribs 26, which reinforcing ribs extend to a substantially plate-shaped base portion 27 of the support body 17 transversely to the longitudinal direction of a sliding surface 25 and formed by the injection molding.
  • a guideway 6 configured on the Switzerland Bachstoffleitschiene 3, namely on the support body 17, a guideway 6 configured.
  • the adjusting element 5 in a displacement region 8, which is shown schematically in Fig. 2, linearly guided.
  • the adjusting element 5 is arranged on this rail-like / rail-shaped guide track 6, that it is held via a positive connection to the Switzerlandstoffleitschiene 3 / the support body 17
  • the actuating element 5 forms on a side facing away from the guideway 6 a wedge-shaped support surface 7, which support surface 7 is adjacent to a mating surface 28 arranged fixedly in operation during operation of an internal combustion engine.
  • the mating surface 7 is inclined to the guide track 6 / employed to the direction of displacement of the actuating element 5.
  • the support surface 7 is wedge-shaped in the sense of a convex curvature, but alternatively also in the sense of a straight plane executed. To allow the bias of the traction means 2, this support surface 7 is permanently in contact with the counter surface 28 in contact and supported on this.
  • a wedge angle 29, 30 of Switzerlandstoffleitschiene 3 is that angle which is formed between the longitudinal axis of the guide track 6 and the longitudinal axis of the straight extending counter surface 28.
  • the wedge angle 29, 30 is dependent on the displacement position of the actuating element 5.
  • the adjusting element 5 is in a first th end position / shift end position is located, so that the Glasstoffleitschiene 3 assumes a first wedge angle 29, which is around 17.5 °, whereby the traction means 2 is deflected / biased by a certain amount.
  • the adjusting element 5 is shifted to a second end position / displacement end position, so that the Glasstoffleitschiene 3 occupies a second wedge angle 30, which is smaller than the first wedge angle 29 to the 10th , Amounting to 5 °, is.
  • the traction means 2 is more strongly deflected / displaced in this second end position in the region of the Werstoffleitschiene 3 by the sliding surface 25 of the sliding coating 24 as in the first end position.
  • the actuator 5 is biased by a compression spring 9 elastic.
  • the compression spring 9 which is designed as a helical spring, thereby biases the adjusting element 5 in a first displacement direction, in the direction of the second end position.
  • the compression spring 9 therefore biases the tensioning element 5 away from the pivot bearing point 4 in the first displacement direction.
  • the compression spring 9 In the first end position shown in FIG. 3, the compression spring 9 is then compressed more strongly than in the second end position, but is just not compressed to block. In the second end position, the compression spring 9 is less strongly biased relative to the first end position and thereby has a greater spring length.
  • the adjusting element 5 is captively received on the guide track 6 / supported / held within the displacement region 8 between the first and the second end position. This was done by the actuator 5 is limited in its movement between two stop webs 12, 13, which are also each formed by a Verstärkungsrip- PE 26 of the support body 17.
  • the adjusting element 5 In the first end position, which can be seen in Fig. 3, the adjusting element 5 is adjacent to a first stop web 12 and supported in its (the first displacement direction opposite) second direction of displacement.
  • a second stop web 13 is arranged such that it defines the second end position by abutment of the actuating element 5.
  • the control element 5 is guided captive within the displacement area 8.
  • control element 5 as can be seen particularly well in Fig. 5, has two
  • Umgreifungsarme 14 wherein only one of these two Umgreifungsarme 14 to be achieved know, the other Umgreifungsarm 14, however, on the non-recognizable back of the actuating element 5, the guideway 6 also surrounds.
  • the two Umgreifungsarme 14 are elastically deformable to each other.
  • Umgreifungsarme 14 are so far elastically deformable to each other that they can be snapped on the guideway 6 from the outside / snapped.
  • the guideway 6 has a head region 31, which extends in the form of a strip along the extent of the guideway 6 with a constant cross section.
  • the encompassing arms 14 are adapted to be elastically deformable on the head region 31 in such a way that they are deformed from the outside by an elastic expansion /
  • the compression spring 9 is always guided in at least part of the displacement region 8 along its spring travel through the spring dome 10. In the first end position, the compression spring 9 is supported by the spring dome 10 in its entire spring length, in the second end position at least in a partial region of its spring length.
  • the spring dome 10 has a base region 32, which is integrally, ie, in one piece, connected to the support body 17.
  • the spring dome 10 is rod-shaped and extends parallel to the guide track 6.
  • a guide of the compression spring 9 is implemented within the shift range 8.
  • the compression spring 9 designed as a helical spring is pushed onto the outside of the spring dome 10.
  • this spring dome 10 has a cross-shaped cross-section for improving the production of injection-molded ceramics.
  • the cross-shaped cross section is implemented by extending along the spring dome 10 four groove-shaped recesses 33 which are each offset by 90 ° in the circumferential direction.
  • the spring dome 10 which is also injection molded as an integral part of the support body 17, cures as free of distortion as possible. Further is on the spring dome 10, namely at a side facing away from the base region 32 free end portion 1 1 a bevel / bevel 34 attached. This chamfer 34 is formed on one of the counter surface 28 facing / the guide track 6 facing away from the spring dome 10. This ensures that the free end region 1 1 of the spring dome 10 in the entire displacement region 8, ie also in the first end position of the adjusting element 5, wherein the end portion 1 1 then protrudes through a through hole 35 in the adjusting element 5, spaced from the Counter surface 28 is positioned. As can furthermore be seen in FIG.
  • a hooking eye 15 is integrally formed on the adjusting element 5.
  • This hooking lug 15 is geometrically configured / prepared for receiving a setting tool 16. If the tensioning unit 1, for example, due to maintenance of the internal combustion engine back to the starting position, ie returned to the first end position, the adjusting tool 16 is easy to thread in the region of its hook-shaped end in the Einhakinate 15 and to bring the actuator 5 in the respective displacement position. As a result, a particularly simple displacement of the actuating element 5 is implemented.
  • a free end 18 of the support body 17 is elastically deformable.
  • the free end 18 of the support body 17 is that end that the
  • Swivel bearing 4 which is also formed at one end of the support body 17, facing away.
  • an end of that longitudinal region 36 of the support body 17 / Switzerlandstoffleitschiene 3 along the sliding surface 25 is referred to, which is arranged from one of the pivot bearing 4 side facing away from the support surface 7.
  • This longitudinal region 36 is elastically deformable.
  • the longitudinal region 36 of the support body 17 is elastically deformable such that the free end 18 bends / flexes between 1 and 3 mm below the usual operating forces in operation, in Fig. 6, the two deflection end positions in the range of 1 mm deflection and 3mm Deflection are shown schematically.
  • a mechanical wedge clamping unit 1 is thus implemented, which is used in particular as a mechanical chain tensioning system for motorcycles.
  • the wedge (adjusting element 5) is in a retightening from the screw point (pivot bearing point 4) of the wedge clamping unit 1 by the pressure feather 9 pushed away.
  • the Keilweg / shift range 8 (between the first and the second end position) is around 33 mm.
  • the wedge angle 29, 30 is adjustable between 10.5 ° and 17.5 °.
  • the screw point 4 is located close to the camshaft 20.
  • the spring dome 10 has a kind of cross design.
  • the spring dome 10 also has application related a chamfer 34, as this otherwise with the
  • Housing wall (mating surface 28) of the internal combustion engine would collide.
  • an eyelet (Einhakinate 15) is located.
  • the wedge 5 snapped onto the support body 17.
  • the lower end of the wedge track (as the second stop web 13 of the guide track 6) may be formed closed.
  • the support body 17 has a certain elasticity.
  • the support body 17 of the rail 1 bends elastically under load by the chain force. Under operating conditions, the elastic deflection between the wedge support surface (mating surface 28) and the free end 18 of the support body 17 moves between 1 mm and 3 mm.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)

Abstract

La présente invention concerne une unité de serrage (1) conçue pour serrer un moyen de traction sans fin (2) d'un moteur à combustion interne, comprenant un rail de guidage de moyen de traction (3) qui présente un emplacement pour palier pivotant (4) préparé conçu pour être fixé au niveau d'une région de palier fixe sur le moteur à combustion interne, un élément de réglage (5) qui est reçu de façon à pouvoir coulisser le long d'une voie de guidage (6) ménagée sur le rail de guidage de moyen de traction (3) et forme une surface d'appui (7), lequel élément de réglage (5) est reçu dans une région de coulissement (8) de manière imperdable sur la voie de guidage (6) ; ainsi qu'un mécanisme d'entraînement de moyen de traction (21) comprenant un moyen de traction sans fin (2) et l'unité de serrage (1) qui serre ledit moyen de traction sans fin (2) en brin tendu ou en brin mou.
PCT/DE2016/200229 2015-05-26 2016-05-17 Unité de serrage mécanique à sabot WO2016188525A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015209599.1 2015-05-26
DE102015209599.1A DE102015209599B4 (de) 2015-05-26 2015-05-26 Mechanische Keilspanneinheit

Publications (1)

Publication Number Publication Date
WO2016188525A1 true WO2016188525A1 (fr) 2016-12-01

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ID=56116163

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2016/200229 WO2016188525A1 (fr) 2015-05-26 2016-05-17 Unité de serrage mécanique à sabot

Country Status (2)

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DE (1) DE102015209599B4 (fr)
WO (1) WO2016188525A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008051143A1 (de) 2008-10-09 2010-07-08 Schaeffler Technologies Gmbh & Co. Kg Spannvorrichtung
DE102012204868A1 (de) * 2011-07-07 2013-01-10 Schaeffler Technologies AG & Co. KG Blechbiegeteil mit integriertem Führungsdorn für eine Keilspanneinheit eines Zugmitteltriebes
DE102011081880A1 (de) * 2011-08-31 2013-02-28 Schaeffler Technologies AG & Co. KG Tragkörper in einer Hybridbauweise für eine Spannvorrichtung
WO2013182233A1 (fr) * 2012-06-06 2013-12-12 Schaeffler Technologies AG & Co. KG Dispositif de tension comprenant une bande de roulement lisse qui présente des portions orientées longitudinalement augmentant la friction, et dispositif de transmission par lien souple

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011006795A1 (de) * 2011-04-05 2012-10-11 Schaeffler Technologies Gmbh & Co. Kg Spannvorrichtung
JP2014070672A (ja) * 2012-09-28 2014-04-21 Honda Motor Co Ltd チェーンテンショナー装置
DE102014211252A1 (de) * 2014-06-12 2015-12-17 Schaeffler Technologies AG & Co. KG Mechanische Spannvorrichtung mit optimiertem Keilprinzip
DE102014211198A1 (de) * 2014-06-12 2015-12-17 Schaeffler Technologies AG & Co. KG Spannvorrichtung für einen Zugmitteltrieb

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008051143A1 (de) 2008-10-09 2010-07-08 Schaeffler Technologies Gmbh & Co. Kg Spannvorrichtung
DE102012204868A1 (de) * 2011-07-07 2013-01-10 Schaeffler Technologies AG & Co. KG Blechbiegeteil mit integriertem Führungsdorn für eine Keilspanneinheit eines Zugmitteltriebes
DE102011081880A1 (de) * 2011-08-31 2013-02-28 Schaeffler Technologies AG & Co. KG Tragkörper in einer Hybridbauweise für eine Spannvorrichtung
WO2013182233A1 (fr) * 2012-06-06 2013-12-12 Schaeffler Technologies AG & Co. KG Dispositif de tension comprenant une bande de roulement lisse qui présente des portions orientées longitudinalement augmentant la friction, et dispositif de transmission par lien souple

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DE102015209599B4 (de) 2017-09-07

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