WO2008061855A1 - Dispositif de tension d'une transmission par lien flexible - Google Patents

Dispositif de tension d'une transmission par lien flexible Download PDF

Info

Publication number
WO2008061855A1
WO2008061855A1 PCT/EP2007/061396 EP2007061396W WO2008061855A1 WO 2008061855 A1 WO2008061855 A1 WO 2008061855A1 EP 2007061396 W EP2007061396 W EP 2007061396W WO 2008061855 A1 WO2008061855 A1 WO 2008061855A1
Authority
WO
WIPO (PCT)
Prior art keywords
lever
housing
bearing
wedge
clamping
Prior art date
Application number
PCT/EP2007/061396
Other languages
German (de)
English (en)
Inventor
Johann Singer
Bernd Hartmann
Hans Bauer
Original Assignee
Schaeffler 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 Kg filed Critical Schaeffler Kg
Publication of WO2008061855A1 publication Critical patent/WO2008061855A1/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
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1209—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means
    • F16H7/1218—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley with vibration damping means of the dry friction type
    • 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
    • F16H7/10—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley
    • F16H7/12—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley
    • F16H7/1254—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means
    • F16H7/1281—Means for varying tension of belts, ropes, or chains by adjusting the axis of a pulley of an idle pulley without vibration damping means where the axis of the pulley moves along a substantially circular path
    • 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
    • F16H2007/081—Torsion 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
    • F16H7/0829—Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H2007/084—Means for varying tension of belts, ropes, or chains with vibration damping means having vibration damping characteristics dependent on the moving direction of the tensioner
    • 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 tensioning device of a traction mechanism drive, with a rotatably mounted on a base housing via a pivot bearing and radially spaced from the axis of rotation of the pivot bearing provided with a rotatable tension roller clamping lever, which is arranged by means of a thighless helical spring, coaxial with the pivot bearing and at the spring ends a pivotable about the axis of rotation of the pivot bearing, wherein the pivot bearing is formed by a bearing pin, a bearing hub and at least one arranged between the bearing pin and the bearing hub plain bearing bush, and wherein a middle radial force application plane of the tension roller is axially spaced from a central radial bearing plane of the pivot bearing.
  • Clamping devices with a plain bearing designed as a plain bearing, designed as a helical spring torsion spring and an axially spaced-apart arrangement of the tensioning roller and the pivot bearing come in different embodiments, preferably in ancillary trains of internal combustion engines for use.
  • Such tensioning devices are both in an internally mounted embodiment with a bearing of the rigidly connected to the clamping lever bearing pin in the forming a part of the base housing bearing hub and in an externally mounted design with a storage of rigidly connected to the clamping lever bearing hub on the one part of the base housing forming bearing pin known.
  • the base housing is provided in each case for fastening the respective clamping device to a motor housing, such as the crankcase or the control housing of a combustion piston engine.
  • the tensioning roller can in such a clamping device in addition between a so-called offset or Z-type, in which the tension roller is arranged axially on the side facing away from the base housing outside of the clamping lever, and a so-called inline or U-type , in which the tension roller is arranged radially laterally of the base housing axially on the inner side facing the base housing of the clamping lever, a distinction can be made.
  • the pivot bearing by which the radial bearing of the clamping lever is accomplished in or on the base housing, has at least one plain bearing bush, which is arranged between the bearing hub and the bearing pin and usually consists of a durable and at the same time low-friction plastic material.
  • the plain bearing bush and the inner bearing wall of the bearing hub and the outer bearing wall of the bearing bolt which are in contact therewith may be cylindrical or conical in a known manner, with an additional thrust bearing, e.g. in the form of a slide bearing disc arranged between a housing-fixed and a lever-fixed bearing plate, whereas a cone-cylindrical pivot bearing in conjunction with an axial prestressing of the torsion spring includes the axial bearing of the tensioning lever.
  • the driver is with respect to the rotational axis of the pivot bearing circumferentially arranged such that the stop surface is aligned normal to a resultant reaction force of a traction means on the tension roller.
  • the support of a reaction force of the clamping lever on the coil spring takes place relative to the base housing.
  • the middle of the lever-side spring end is axially spaced apart from the middle bearing plane of the pivot bearing in such a way that the tilting moments of the tangential spring force of the coil spring and that via the tensioning roller effectively cancel each other on the tensioning lever resulting reaction force of the traction means.
  • the support of the reaction force of the clamping lever on the coil spring is preferably carried out via a sliding block which is arranged offset back about the axis of rotation of the pivot bearing on the outer lever-side turn of the coil spring from the stop surface of the driver by about 90 °, radially inwardly on the outer lever-side turn of Coil spring rests, is guided in a radial guide of the clamping lever radially movable, and rests radially on the outside with a friction surface on a cylindrical inner wall of the base housing. This results in a high spring force proportional and thus dependent on the current position of the clamping lever friction damping of the pivotal movement of the clamping lever.
  • Another friction torque for damping a pivoting movement of the tensioning lever and a further lever force for balancing the pivot bearing can be achieved by a corresponding arrangement of a second sliding shoe on the outer housing-side turn of the coil spring.
  • the local reaction force of the base housing on the coil spring is effective both as radia- Ie contact force of the shoe against a cylindrical inner wall of the clamping lever and as a balancing leverage around the tilting axis of the plain bearing bushing of the pivot bearing.
  • the invention is based on the finding that a friction torque for friction damping of a pivoting movement of the clamping lever can also be generated by a support of the lever-side tangential spring force F F _ ⁇ of the torsion spring against the lever-fixed driver via a wedge element.
  • a radial contact force F KR is generated by a support of the wedge element on the driver on both sides wedge surfaces, pressed with the wedge member radially outward with an outer cylindrical friction surface against a cylindrical inner wall of the base housing and thus during a pivoting movement of the clamping lever due to the tangential relative movement between the Wedge element and the base housing a friction torque is generated.
  • the invention therefore relates to a tensioning device of a traction mechanism drive, with a rotatably mounted on a base housing via a pivot bearing and radially spaced from the axis of rotation of the pivot bearing provided with a rotatable tension roller clamping lever, which is arranged by means of a thighless helical spring, coaxial with the pivot bearing and to the spring ends on the casing side to the base housing as well as the lever side with the clamping lever in operative connection torsion spring having a torsional moment M ⁇ to the axis of rotation of the pivot bearing can be acted upon, wherein the pivot bearing is arranged by a bearing bolt, a bearing hub and at least one between the bearing pin and the bearing hub Plain bearing bush is formed, and wherein a mean radial force application plane of the tension roller is axially spaced from a central radial bearing plane of the pivot bearing.
  • the torsion-side spring end of the torsion spring is connected to the tensioning lever via a wedge element and a lever-fixed catch, wherein the wedge element bears against the lever-side spring end of the coil spring with an axially-radially aligned pressure surface radially outwardly of the lever-side spring end inclined wedge surface rests against an equally inclined wedge surface of the driver, and with an outer cylindrical Reibflä- che rests against a cylindrical inner wall of the base housing.
  • the wedge element causes the lever-side tangential spring force F F _ ⁇ of the torsion spring, whose height increases or decreases in proportion to the actual torsional moment between the tensioning lever and the base housing, to be dependent on the inclination of the wedge surfaces of the wedge element and the carrier in accordance with the vectorial equilibrium of forces the wedge element in a normal standing on the wedge surface of the wedge element supporting force F KN and converted into a radial contact force F KR .
  • the wedge member While the supporting force F KN is introduced via the wedge surface of the driver in the clamping lever and is used to balance the at least one plain bearing bushing of the pivot bearing, the wedge member is pressed by the radial contact force F KR with its outer cylindrical friction surface against the cylindrical inner wall of the base housing, creating a Friction torque for friction damping of a pivoting movement of the clamping lever is generated about the axis of rotation of the pivot bearing.
  • the angle of inclination of the two wedge surfaces serves as an adjustment parameter for adjusting the height and direction of the support force F KN and the height of the radial contact force F KR .
  • the wedge element also has the positive side effect that due to the tangential frictional force F RT between the wedge element and the clamping lever, the radial contact pressure F KR and thus the effective friction torque at a compression of the tensioning lever with respect to the torsion spring, which corresponds to a pivoting of the tensioning roller away from the traction means, additionally increased and at a rebound of the tensioning lever with respect to the torsion spring, which corresponds to a pivoting of the tensioning roller to the traction means out, is additionally reduced.
  • the driver is preferably arranged circumferentially with respect to the axis of rotation of the pivot bearing such that the wedge surfaces of the wedge element and the driver are largely normal, that is perpendicular, aligned to a resultant reaction force F Z _ R of a traction device on the tension roller, as a result, a direct compensation of the overturning moment the reaction force F ZR of the traction means on the tensioning roller about the tilting axis of the pivot bearing by the overturning moment of the supporting force F KN on the driver and thus a uniform load on the plain bearing bushing of the pivot bearing is possible.
  • the angle of inclination of the wedge surfaces of the wedge element and the driver relative to the pressure surface of the wedge element, via which the height and direction of the used for balancing the pivot bearing support force F KN and the amount of the radial contact force F KR and thus of the friction torque used for the friction damping of the tensioning lever is adjustable relative to the tangential spring force F F _ ⁇ of the torsion spring is suitably in a range between 30 ° and 60 °.
  • the friction surface of the wedge element and / can or the cylindrical inner wall of the base housing may be provided with a friction lining.
  • the entire wedge element consists of a resistant and friction-resistant plastic, which is in frictional contact directly with its outer cylindrical friction surface with the cylindrical inner wall of the base housing provided with or without friction lining.
  • the wedge member is advantageously integrally connected to an open bearing ring which is disposed between the outer lever-side turn of the coil spring and the clamping lever, which is spaced from the wedge element against the clamping lever positively secured against rotation , and which is fully opened immediately adjacent to the wedge surface of the wedge element.
  • an open bearing ring which is disposed between the outer lever-side turn of the coil spring and the clamping lever, which is spaced from the wedge element against the clamping lever positively secured against rotation , and which is fully opened immediately adjacent to the wedge surface of the wedge element.
  • the wedge element can advantageously protrude at least partially axially outside of the bearing ring and engage in a provided with the lever-side wedge surface radial groove of the clamping lever.
  • the radial groove of the clamping lever can be provided on both sides in the circumferential direction with a wedge surface, as a result an identical clamping lever can be used both for a clamping device with clockwise clamping lever and for a clamping device with anti-clockwise clamping lever.
  • the wedge element and the driver are integrally connected to a slotted bearing ring, the PHg between the outer lever side Win- the coil spring and the clamping lever is arranged, the close to the driver against the clamping lever form-fitting against rotation and against a radial displacement is secured, and which is provided between the wedge surface of the wedge element and the wedge surface of the driver with a separating slot.
  • the application-specific design features such as the circumferential orientation and the angle of inclination of the wedge surfaces of the wedge element and the driver, combined in the bearing ring, wherein the positive fixation of the bearing ring on the clamping lever, the functional fixation of the driver and the separating slot relative mobility of the wedge element with respect to the keN surface of the driver is ensured.
  • the positive connection of the bearing ring with the clamping lever can be suitably formed by a respective axial bore and a bolt inserted into the axial bores.
  • the adaptation of the circumferential position and the direction of rotation of the clamping lever to the respective application can be done in a simple manner by the positioning of the lever-side axial bore in a standardized clamping lever.
  • the positive connection of the bearing ring with the clamping lever by an axially aligned inner radial groove of the bearing ring and engaging in this, axially extending outer radial web be formed of the clamping lever, since a load of the driver by the supporting force F KN on the relevant wedge surface occurs only in the circumferential direction and radially inward. Due to the positioning of the radial web, however, the clamping lever in this case represents an application-specific component.
  • the housing-side spring end of the torsion spring can also be connected to the base housing via a wedge element and a housing-mounted driver, the wedge element abutting against the housing-side spring end of the helical spring with an axially-radially aligned pressure surface radially outwardly of the housing side spring end inclined wedge surface rests against an equally inclined wedge surface of the driver, and rests with an outer cylindrical friction surface on a cylindrical inner wall of the clamping lever.
  • the radial contact force F KR of the wedge element is effective on the clamping lever, on the housing side by the radial contact force F K _R not only a frictional torque about the axis of rotation of the pivot bearing but also a usable for balancing the pivot bearing tilting moment about one in the middle bearing plane the slide bearing lying tilting axis generated.
  • lever-side spring end of the torsion spring or the lever-side region of the tensioning device are also applicable to the housing-side spring end of the torsion spring or the housing-side region of the tensioning device, taking into account a construction-related permutation of tensioning lever and base housing.
  • the lever-side support of the reaction force F F _ R of the clamping lever on the coil spring for generating a further frictional torque via a sliding shoe which is about the axis of rotation of the pivot bearing from the lever-side spring end is arranged offset by about 90 °, radially inwardly abuts the outer lever-side turn of the coil spring, is guided radially movable in a radial guide of the clamping lever, and rests with an outer cylindrical friction surface on a cylindrical inner wall of the base housing.
  • the housing-side support of the reaction force F FR of the base housing can take place on the coil spring via a sliding shoe, which is arranged offset from the housing side spring end about 90 ° about the axis of rotation of the pivot bearing, rests radially inwardly on the outer housing side winding of the coil spring is guided radially movable in a radial guide of the base housing, and with an outer cylindrical Friction surface bears against a cylindrical inner wall of the clamping lever, wherein the sliding shoe and the radial guide circumferentially on the side facing the housing side spring end each have a radially outwardly inclined to the housing side spring end wedge surface.
  • the resultant force vector from the radial contact force F KR of the wedge element and effective as a radial contact force of the sliding shoe reaction force should F to the fullest possible balancing of the pivot bearing FR should be aligned largely parallel to the resulting reaction force F ZR of the traction device on the tension roller.
  • the lever-side support of the reaction force F FR of the clamping lever on the coil spring via a direct contact of a about the axis of rotation of the pivot bearing of the lever-side spring end of about 90 ° back portion of the outer lever-side turn of the coil spring with a cylindrical Inner wall of the base housing carried, wherein at least the outer lever-side winding of the coil spring and / or the cylindrical inner wall of the base housing is provided with a friction coating.
  • the helical spring can advantageously be completely provided with a friction coating.
  • This friction coating also acts as corrosion protection, so that an otherwise required corrosion protection treatment of the coil spring can be omitted.
  • FIG. 3 shows an axial view of a bearing ring of the tensioning device according to FIG. 1 and FIG. 2 with an axially outward looking direction
  • FIGS. 1 to 3 shows the forces acting on a wedge element of the tensioning device according to FIGS. 1 to 3 in a schematic illustration
  • FIG. 4b shows the static equilibrium of forces on the wedge element according to FIG. 4a in a vector illustration
  • FIG. 4c shows the dynamic equilibrium of forces on the wedge element according to FIG. 4a in the case of a pivoting movement of the tensioning lever that excites the torsion spring in a vector illustration, FIG.
  • FIG. 4d shows the dynamic equilibrium of forces on the wedge element according to FIG. 4a in the case of a pivoting movement of the tensioning lever which relaxes the torsion spring in a vector representation
  • FIG. 5 shows an alternative embodiment of a clamping device according to the invention in a partially sectioned axial view
  • FIG. 6b shows a tensioning lever of the further variant of the tensioning device according to the invention according to FIG. 6a in a schematic axial view
  • FIG. 7 shows a first embodiment of a spring force support of the torsion spring of the tensioning device in a schematic axial view
  • FIG. 8 shows a second embodiment of a spring force support of the torsion spring of the tensioning device in a schematic sectional view.
  • FIG. 1 A preferred embodiment of the tensioning device 1 according to the invention of a traction mechanism drive is shown in FIG. 1 in a perspective exploded view.
  • a tensioning lever 2 is mounted rotatably on a cup-shaped base housing 4 via a pivot bearing 3.
  • Radially spaced from the axis of rotation 5 of the pivot bearing 3, the clamping lever 2 is provided with a present not shown, about an axially parallel axis of rotation 6 rotatable tension roller over which the traction means of a traction mechanism is guided in the installed state.
  • the pivot bearing 3 is presently cylindrical and is formed of a rigidly connected via a serration 7 to the base housing 4 bearing pin 8, a rigidly connected to the clamping lever 2 bearing hub 9 and arranged between the bearing pin 8 and the bearing hub 9 plain bearing bush 10.
  • a Gleitla- gerusion 11 is provided, which is integrally connected to the plain bearing bush 10 and between a lever-fixed bearing plate 12 and a rigidly connected to the bearing pin 8 bearing plate 13 is arranged.
  • the clamping lever 2 and the base housing 4 are positively connected to each other via a torsion spring 14 in operative connection, which is designed as a load-bearing in the open sense legless coil spring 15 with blunt spring ends 16, 17 and coaxial with the pivot bearing 3.
  • the tensioning lever 2 is acted upon by tensioning the associated traction means by means of the helical spring 15 with a torsional moment M ⁇ about the axis of rotation 5 of the pivot bearing 3, whereby the tensioning roller springs over the tensioning lever 2 to the traction means and thus the traction means is tense.
  • a bearing ring 19 made of a durable plastic is arranged between the outer lever-side turn 18 of the coil spring 15 and the tensioning lever 2.
  • a bearing ring 19 made of a durable plastic is arranged between the outer lever-side turn 18 of the coil spring 15 and the tensioning lever 2.
  • the lever-side spring end 16 of the torsion spring 14 is connected to the tensioning lever 2 via a wedge element 20 and a lever-fixed driver 21 ,
  • the wedge element 20 rests with an axially-radially aligned pressure surface 22 on the lever-side spring end 16 of the helical spring 15 and with a wedge surface 23 inclined radially outward from the lever-side spring end 16 on an equally inclined wedge surface 24 of the driver 21 and with an outer cylindrical friction surface 25 on a cylindrical inner wall 26 of the base housing 4 at.
  • the wedge member 20 and the driver 21 are integrally connected to the bearing ring 19.
  • the bearing ring 19 is positively secured near the driver 21 against the clamping lever 2 against rotation and against radial displacement, and provided between the wedge surface 23 of the wedge element 20 and the wedge surface 24 of the driver 21 with a separating slot 27.
  • the positive connection of the bearing ring 19 with the clamping lever 2 is presently formed by an axially aligned inner radial groove 28 of the bearing ring 19 and an engaging in this axially extending outer radial web 29 of the clamping lever 2.
  • the bearing ring is also provided with sleeve segments 30 which abut radially in the mounted state on the turns of the coil spring 15.
  • FIG. 4 a shows the forces acting on the wedge element 20 according to FIG. 3.
  • the tangential spring force F F _ ⁇ of the spring end 16 of the helical spring 15 acts normally on the wedge surface 23 of the wedge element 20
  • the reaction force of the driver 21 acts on the support force F KN of the wedge element 20
  • normal or radial to the friction surface 25 of the wedge element 20 acts the reaction force of the cylindrical inner wall 26 of the base housing 4 to the radial pressing force F R of the wedge element ⁇ 20th
  • Torsisonsfeder 14 are compressing the pivoting movement 31 of the tensioning lever 2 in addition, the frictional force by drawn represented F R T on the friction surface 25 of the wedge element acts 20 in a direction directed ausfedernden pivoting movement 32 of the tensioning lever 2 in the opposite direction, the frictional force F RT shown in dashed lines acting on the Friction surface 25 of the wedge element 20th
  • Fig. 4b the static force equilibrium is shown on the wedge member 20, which adjusts at a certain position of the clamping lever 2 without a pivoting movement.
  • Fig. 4c the dynamic balance of forces on the wedge member 20 is shown, which adjusts itself at a certain position of the clamping lever 2 during a torsional spring 14 einfedernden pivotal movement 31 of the clamping lever 2, resulting in an increase in the radial contact force F KR of the wedge member 20 and Consequently, an increase in the friction damping of the pivoting movement 31 results.
  • FIG. 4d shows the dynamic equilibrium of forces on the wedge element 20 which, at a specific position of the tensioning lever 2, adjusts during a pivoting movement 32 of the tensioning lever 2 which rebounds with respect to the torsion spring 14, resulting in a reduction in the radial contact pressure F KR of the wedge element 20 and consequently a reduction in the frictional damping of the pivoting movement 32 sets.
  • This ensures tet, that the clamping lever 2 opposes an outward swinging of the traction means an increased resistance, whereas an inward swinging of the traction means, a reduced resistance is opposed, so that the tensioning lever 2 mounted on the tension roller follows the movement of the traction means and remains in contact therewith.
  • FIG. 5 An alternative embodiment of the tensioning device 1 'according to the invention is shown in FIG. 5 in a simplified, partially sectioned axial view as viewed from the base housing to the outer tensioning lever 2.
  • the tensioning lever 2 is urged by the helical spring 15 in the opposite direction of rotation to the tensioning device 1 according to FIGS. 1 to 3 with the torsional moment M ⁇ , whereby the tensioning roller 33 is spring-loaded to an associated traction means and a resultant reaction force Fz R to the tensioning roller 33 or the tensioning lever 2 is generated.
  • the wedge element 20 and the driver 21 are, as in the previously described embodiment, integrally connected to the bearing ring 19, which consists of an elastic and resistant plastic, is arranged between the outer winding 18 of the helical spring 15 and the tensioning lever 2 between the wedge surfaces 23, 24 of the wedge member 20 and the driver 21 has a separating slot 27 exaggerated here.
  • the wedge surfaces 23, 24 of the wedge element 20 and the driver 21 are largely normal to the reaction force F Z _ R aligned.
  • the non-rotatable and radially fixed connection of the bearing ring 19 with the clamping lever 2 is present, as indicated in Fig. 5, in the form of a close to the driver 21 on the bearing ring 19 arranged axial bore 34, an arranged on the clamping lever 2 axial bore 35 and a in the axial bores 34, 35 used bolt 36 is formed.
  • the lever-side axial bore 35 can be arranged in different angular positions. Ones are attached, so that the use of a largely identical clamping lever 2 in several different clamping devices is possible.
  • FIGS. 6a and 6b A further embodiment variant of the tensioning device 1 "according to the invention is shown in FIGS. 6a and 6b in each case in a simplified, partially cut axial view looking from the base housing to the outer tensioning lever 2.
  • FIG. 6a shows the lever-side bearing ring 19 'with the outer lever side Winding 18 of coil spring 15, while Fig. 6b shows tensioning lever 2 with tensioning roller 33.
  • Wedge element 20 is integrally connected to bearing ring 19 'which has a radially continuous opening 37 immediately adjacent wedge surface 23 of wedge element 20
  • Driver 21 with the local wedge surface 24 is in this case practically in the clamping lever 2 'integrated by this is provided with a limited by the wedge surface 24 radial groove 38 in the mounted state, an axial extension of the wedge element 20 engages with its wedge surface 23
  • Tension lever 2 'even with a jig with Titanges To be able to use the last pivoting direction, the radial groove 38 is circumferentially opposite by a further wedge surface 24 'limited.
  • FIG. 7 the lever-side support of the reaction force F FR of the clamping lever 2 is shown in a schematic axial view of the coil spring 15 via a sliding block 39, whereby an additional friction torque for damping a pivoting movement of the clamping lever 2 is generated.
  • the shoe 39 is disposed about the axis of rotation 5 of the pivot bearing 3 from the lever-side spring end 16 set back by about 90 °, is located radially inward on the outer lever-side winding 18 of the coil spring 15, is radially guided in a radial guide 40 of the clamping lever 2, and lies with an outer cylindrical friction surface 41 against a cylindrical inner wall 26 of the base housing 4.

Landscapes

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

Abstract

Dispositif de tension d'une transmission par lien flexible, comprenant un levier tendeur (2) monté de manière rotative via un palier d'articulation sur un boîtier de base (4) et muni à distance radiale de l'axe de rotation du palier d'articulation (3) d'une poulie de tension (33) rotative, lequel levier est disposé coaxialement au palier d'articulation (3) à l'aide d'un ressort de torsion (14) réalisé en tant que ressort à boudin sans branche (13). Pour l'amélioration de l'équilibrage du palier d'articulation et de la finesse d'ajustement de l'atténuation de la friction du levier tendeur, l'extrémité de ressort (16) du côté du levier du ressort de torsion (14) est en liaison avec le levier tendeur (2) par l'intermédiaire d'un élément de clavette (20) et un entraîneur (21) fixe du levier. L'élément de clavette (20) repose, avec une surface de pression (22) orientée de manière axiale-radiale, contre l'extrémité de ressort (16) du ressort à boudin (15) ; avec une surface de clavette (23) inclinée radialement vers l'extérieur en opposition à l'extrémité de ressort (16) du côté du levier, contre une surface de clavette (24) également inclinée de l'entraîneur (21) ; et avec une surface de friction cylindrique extérieure (25), contre une paroi intérieure cylindrique (26) du boîtier de base (4).
PCT/EP2007/061396 2006-11-22 2007-10-24 Dispositif de tension d'une transmission par lien flexible WO2008061855A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006054963.5A DE102006054963B4 (de) 2006-11-22 2006-11-22 Spannvorrichtung eines Zugmitteltriebs
DE102006054963.5 2006-11-22

Publications (1)

Publication Number Publication Date
WO2008061855A1 true WO2008061855A1 (fr) 2008-05-29

Family

ID=39027056

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/061396 WO2008061855A1 (fr) 2006-11-22 2007-10-24 Dispositif de tension d'une transmission par lien flexible

Country Status (2)

Country Link
DE (1) DE102006054963B4 (fr)
WO (1) WO2008061855A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103968019B (zh) * 2014-03-25 2017-01-04 宁波丰茂远东橡胶有限公司 一种发动机用大阻尼低衰减张紧器

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060100049A1 (en) * 2004-11-05 2006-05-11 Dayco Products, Llc Belt tensioner and method for assembly
WO2006099731A1 (fr) * 2005-03-21 2006-09-28 Litens Automotive Partnership Tendeur de courroie a dispositif de compensation d’usure
DE102006004507A1 (de) * 2006-02-01 2007-08-02 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere für einen Riemen oder eine Kette
WO2007113039A1 (fr) * 2006-03-31 2007-10-11 Schaeffler Kg dispositif de serrage pour une commande par moyen de traction

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5964674A (en) * 1997-03-21 1999-10-12 The Gates Corporation Belt tensioner with bottom wall of base juxtaposed pivot arm
JP3732446B2 (ja) * 2002-01-30 2006-01-05 三ツ星ベルト株式会社 オートテンショナ
DE102005047265A1 (de) * 2005-10-01 2007-04-05 Schaeffler Kg Spannvorrichtung eines Zugmitteltriebs
DE102006044178A1 (de) * 2006-09-15 2008-03-27 Schaeffler Kg Spannvorrichtung für einen Zugmitteltrieb

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060100049A1 (en) * 2004-11-05 2006-05-11 Dayco Products, Llc Belt tensioner and method for assembly
WO2006099731A1 (fr) * 2005-03-21 2006-09-28 Litens Automotive Partnership Tendeur de courroie a dispositif de compensation d’usure
DE102006004507A1 (de) * 2006-02-01 2007-08-02 Schaeffler Kg Spanneinrichtung für ein Zugmittel, insbesondere für einen Riemen oder eine Kette
WO2007113039A1 (fr) * 2006-03-31 2007-10-11 Schaeffler Kg dispositif de serrage pour une commande par moyen de traction

Also Published As

Publication number Publication date
DE102006054963A1 (de) 2008-05-29
DE102006054963B4 (de) 2020-11-05

Similar Documents

Publication Publication Date Title
EP2005028B1 (fr) Dispositif de serrage pour une commande par moyen de traction
DE60225716T2 (de) Riemenspanner mit reibungsgesteuerter stopposition
DE69610811T2 (de) Dämpfungsmechanismus für einen Riemenspanner
WO2008119594A1 (fr) Dispositif de serrage d'un mécanisme de traction
DE3225411A1 (de) Riemenspannvorrichtung
EP1277989A2 (fr) Tendeur, notamment pour courroies de transmission
DE102007031298A1 (de) Dämpfungsvorrichtung eines mechanischen Spannsystems für einen Zugmitteltrieb
WO2011138101A1 (fr) Dispositif de tensionnement
WO2010130553A1 (fr) Ensemble tendeur de courroie
DE102008014325A1 (de) Riemenspanner
EP0636815B1 (fr) Dispositif de tension d'une courroie de transmission
EP3943778B1 (fr) Dispositif de tension de courroie et entraînement de courroie doté d'un tel dispositif de tension de courroie
DE102009039841A1 (de) Feder-Dämpfer-Element für eine Fahrerhauslagerung
WO2007051788A1 (fr) Dispositif tendeur pour un moyen de traction, en particulier une courroie
WO2008061855A1 (fr) Dispositif de tension d'une transmission par lien flexible
WO2004042253A1 (fr) Dispositif de suspension et d'amortissement
DE102007020738A1 (de) Spannvorrichtung für einen Zugmitteltrieb
DE102007049908A1 (de) Spannvorrichtung für das Zufmittel eines Zugmitteltriebes
DE10053186B4 (de) Lager für einen Riemenspannarm
DE102006012033A1 (de) Drehdämpfer
WO2009050048A1 (fr) Ensemble amortisseur de vibrations de torsion
DE102010045874A1 (de) Spannsystem für einen Zugmitteltrieb
WO2010130534A1 (fr) Unité de tendeur de courroie
DE19706313A1 (de) Riemenspannvorrichtung
DE9313182U1 (de) Spannvorrichtung für Riementrieb

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 07821759

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 07821759

Country of ref document: EP

Kind code of ref document: A1