WO2001040682A1 - Tendeur de courroie crantee a antiretour flottant - Google Patents

Tendeur de courroie crantee a antiretour flottant Download PDF

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Publication number
WO2001040682A1
WO2001040682A1 PCT/CA2000/001403 CA0001403W WO0140682A1 WO 2001040682 A1 WO2001040682 A1 WO 2001040682A1 CA 0001403 W CA0001403 W CA 0001403W WO 0140682 A1 WO0140682 A1 WO 0140682A1
Authority
WO
WIPO (PCT)
Prior art keywords
arm
engagement member
lever member
pivoting
pivoting arm
Prior art date
Application number
PCT/CA2000/001403
Other languages
English (en)
Inventor
K. Mats Lipowski
Jorma J. Lehtovaara
Marek Frankowski
Jacek Stepniak
Original Assignee
Litens Automotive Partnership
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 Litens Automotive Partnership filed Critical Litens Automotive Partnership
Priority to DE10085330T priority Critical patent/DE10085330T1/de
Priority to CA002392560A priority patent/CA2392560C/fr
Priority to AU18464/01A priority patent/AU1846401A/en
Publication of WO2001040682A1 publication Critical patent/WO2001040682A1/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
    • 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

Definitions

  • This invention relates to a timing belt tensioner having a floating backstop assembly which allows a controlled movement of the tensioner arm.
  • a belt tensioner is a movable support structure that rotatably supports a portion of a belt in an engine or other mechanical system.
  • a belt tensioner is movable to compensate for increases or decreases in belt path length due to wear and other factors to provide a constant belt tensioning force on a timing or drive belt.
  • a common type of conventional belt tensioner includes a fixed structure and a pivoted structure pivotally mounted on the fixed structure.
  • the pivoted structure carries a belt-engaging pulley.
  • a coil spring has ends thereof connected between the fixed and pivoted structures to bias the latter with respect to the former toward a position of maximum belt take-up.
  • the spring biasing force decreases as the pivoted structure moves from a position of minimum belt take-up to a position of maximum belt take-up.
  • the spring force varies within the range of movement provided, a substantially constant tension is maintained on the belt.
  • a stroke limiter comprises fixed stops which will physically stop the rotation of the pivot arm a predetermined distance from the nominal pivot arm position.
  • a first stop will limit the arm rotation towards the belt and is commonly called a free arm stop.
  • a second stop limits the arm movement away from the belt and is commonly known as a back stop.
  • the back stop is normally positioned in such a way that even if the pivot arm is rotated against the back stop, there will not be enough slack in the belt for it to rise above teeth in any of the sprockets in the drive and jump over the teeth. In other words, the back stop is designed to prevent tooth skip which would cause error in timing between the sprockets and consequent equipment errors and damage.
  • the positioning of the back stop has become even more complicated with the requirement that belt tensioners be capable of adjusting their initial running position after installation without any interference or alignment by the operator.
  • United States Patent no. 4,145,934 describes a wedge which is pushed against the arm eccentric (lever) so that the arm cannot rotate outwards once the tensioner arm is biased towards the belt by a tensioning spring.
  • United States Patent no. 4,351,636 describes a tensioner similar in principle to the '934 patent except that the one-way wedge is replaced by a ratchet/pawl assembly. Another ratchet and pawl mechanism is described in United States Patent no. 4,634,407.
  • Each of the above-mentioned tensioners describe a one-way mechanism, which does not allow the tensioner arm to rotate away from the belt once the arm is allowed to move inwards towards the belt.
  • United States Patent no. 4,583,962 offers an improvement to these designs by describing a mechanism which allows a limited return stroke of the arm towards the backstop when required by the thermal expansion of the engine.
  • the detail design of this patent describes a spring clutch type one-way device and an arc shape slot wherein the arm is free to rotate backwards.
  • United States Patent no. 4,808,148 describes a tensioner wherein the slot controlled reverse stroke is replaced by a resilient biasing element such as elastomeric spring located between the ratchet and pawl assembly and the stationary mounting member.
  • United States Patent no. 4,923,435 describes a tensioner wherein the arm can have a return stroke controlled by a viscous clutch between the arm and the one-way mechanism.
  • a timing belt tensioner having a floating backstop assembly, which can resist an arm movement with a force exceeding the belt load to the tensioner.
  • a belt tensioner with a backstop assembly which can restrict the arm movement wiih forces which are of different magnitudes into back stop and free arm directions and which forces can vary according to the particular running conditions of the engine.
  • the restricting forces are controlled in such a way that the pivoting arm can more easily move towards the free arm position.
  • restricting forces are created with a lever-action frictional floating backstop assembly which creates radial forces on one or several diametrical or arcuate surfaces of the pivoting arm and/or on stationary arcuate sliding surfaces, thereby creating tangential frictional forces, which act on the arm either slowing down or completely stopping the arm movement.
  • the lever-action floating backstop assembly is designed in such a way that it results in a frictional wedging action taking place between the backstop assembly and the pivoting arm, which wedging action has an increased wedge angle when the frictional wedge is driven further towards the arm surface.
  • the force acting perpendicular to the arm surface has a force component, resisting the movement of the lever member towards the arm surface, which component will increase the more the lever member rotates towards the arm surface.
  • the above-mentioned frictional wedging is created by constructing the lever member and the sliding surface for the wedging frictional element in such a way than the radius of the arcuate sliding surface is smaller than the pivoting arm length of the lever member.
  • a tensioner including a base and a pivot shaft extending from the base having a pivot axis.
  • a pivoting arm is rotatably mounted on the pivot shaft and has an arcuate surface structure.
  • a pulley is rotatably mounted on the pivoting arm and has an axis of rotation extending parallel to and spaced from the pivot axis.
  • a spring is connected with the pivoting arm to bias the arm into tensioning engagement with an endless drive component of an engine.
  • a floating backstop assembly comprises a lever member and an arm engagement member. The lever member is rotatably mounted on the base and the arm engagement member is engaged with the lever member.
  • the lever member and arm engagement member are oriented such that the arm engagement member can be biased by the spring into a direction towards the arcuate surface structure of the pivoting arm so as to apply a frictional force sufficient to stop movement of the arm.
  • the pivoting point of the lever member is to be arranged in such a way that the distance between the pivoting point and the contact point between the arm engagement member and its sliding surface remains longer that the curvature radius of the sliding surface.
  • the forces to bias the lever member and the arm engagement member towards the sliding surface of the pivoting arm can be created by weights, the main spring member, one or more separate springs and/or by the size, shape and flexibility of the lever member itself acting as a compression spring.
  • the construction of the lever member can take several forms depending the space available under and inside the circumferential face of the bottom cavity of the pivoting arm.
  • the pivoting point of the lever member can be of any known pivot construction, such as a rigid pin, cup joint with a semicircular swivel, etc.
  • the main body of the lever member can take any shape, which can connect the pivoting point and the arm engagement member and the body can be designed to be flexible thereby limiting the radial force the arm engagement member can compel on the pivoting arm.
  • the self-limiting wedging action can also be achieved by using an arcuate sliding surface, which is rigidly connected to the base as long as the construction radius of this surface is smaller than the pivoting arm length of the lever member.
  • a joint mechanism which can of any known construction, e.g. a pin and slot, or another arm engagement member between the pivoting arm and the lever member.
  • FIG. 1 is fragmentary front elevational view illustrating a portion of an automobile internal combustion engine having a timing belt assembly including a tensioner of the present invention
  • FIG. 2 is a side sectional view of the tensioner of FIG. 1 ;
  • FIG. 3 is a partial perspective view of the tensioner of FIG. 2, with the pulley assembly removed;
  • FIG. 4 is a partial top view of the tensioner of FIG. 2, with the pulley assembly and the coil spring removed.
  • FIG. 1 there is illustrated a timing belt system for an internal combustion engine.
  • a toothed pulley 112 is fixed to an output shaft 113 of the engine and an internally toothed belt 114 is driven by the pulley 112.
  • the toothed belt 114 is trained about a second externally toothed pulley 116 which is fixed to a cam shaft 118 of the engine.
  • a tensioner 10 is mounted in operative tensioning relation with the belt 114.
  • the tensioner 10 generally comprises a pulley 12 journal mounted on a pivoting arm 14 which is pivotally mounted on a pivot shaft 16.
  • the pulley 12 has an axis of rotation.
  • the pivot shaft 16 has a longitudinal axis which is generally parallel to and spaced from the axis of rotation of the pulley 12.
  • a coil spring 18 is mounted in the manner described below about the pivot shaft 16 and operably extends between the pivoting arm 14 and a tensioner base 20.
  • a bolt 22 extends through the pivot shaft 16 to engage the tensioner 10 to an engine mounting surface.
  • the bottom section of the pivoting arm 14 is in a shape of a cylindrical skirt 46.
  • the skirt 46 is preferably made of steel and it can be either an integral part of the arm 14 or connected to the separate arm part 14 with any known techniques, such as press fit, cast in, or riveted.
  • a sector of the internal circumferential surface of the skirt 46 is especially prepared to engage an arm engagement member 30, in the form of a floating shoe, as will be described later.
  • the base 20 is generally cup shaped with a central opening and boss formation which engages the pivot shaft 16 in a friction fit.
  • the base 20 has a lip 24 extending about the perimeter of the base 20.
  • a lever pivot cradling structure 26 extends upwardly from the lip 24.
  • the cradling structure 26 is generally arcuate in shape.
  • a lever-action floating backstop assembly of the present invention generally comprises the arm engagement member 30, (also termed as a “floating shoe” or “shoe member”), a pivoting shoe 34 and a lever member 36.
  • the arm engagement member 30 is generally sector shaped with an arcuate outer surface 38.
  • the inner face of the arm engagement member 30 has a groove for receiving and pivotally interlocking with the lever member 36.
  • the lip 24 Diametrically opposed to the cradling structure 26, the lip 24 has a gap 28, defined by stops 29 and 31, in which the arm engagement member 30 is fitted.
  • the structure 26 receives the pivoting shoe 34.
  • the shoe 34 has a pivot lobe 35 which engages the cradling structure 26.
  • the pivot lobe 35 minimizes circumferential sliding movement and allows the shoe 34 to pivot about a pivot point.
  • the shoe 34 is configured to receive and interlock with the preferably ring-shaped lever member 36.
  • An upwardly extending pin 40 is press-fitted into the lever member 36 and acts as a support for the spring 18. It is contemplated that the shoe 34 is a part of a larger plastic piece which is molded over and attached to the base 20. In this contemplated embodiment, the shoe 34 would not pivot on the cradling structure 26.
  • the arm engagement member 30 and the shoe 34 are made from known frictional materials.
  • One end of the spring 18 is provided with a tang 42 which is inserted in a correspondingly sized slot in the lip 24 of the base 20, as shown in Fig. 3.
  • the opposite end of the spring 18 has a tang 44 which engages the skirt 46, as shown in Fig. 2.
  • Spring 18 provides a bias for the pivoting arm 14 to urge the pulley 12 into tensioning engagement with the timing belt 114 towards the free arm position.
  • the skirt 46 has generally a downwardly extending cup shape.
  • the skirt 46 has a central opening for frictionally engaging the pivoting arm 14.
  • the skirt 46 is sized to fit within the inner diameter of the pulley 12 and has an axial extent to nestingly receive the base 20.
  • the arm engagement member 30 frictionally engages the inner circumferential face of the skirt 46.
  • the inner circumferential face of the skirt 46 has a curvature that corresponds with the arcuate outer surface 38.
  • the inner circumferential face of the skirt 46 also has a suitable surface finish for engagement with the arm engagement member 30 and may be coated with a friction controlling material.
  • the lever member 36 can be of any shape which can connect to the lever pivot at the shoe 34 and the arm engagement member 30, allowing the pivotal movement of the lever member 36 even when the wear of the arm engagement member 30 allows further rotational movement of the lever member 36.
  • the lever member 36 is preferably made of steel and can be designed to act as a compression member allowing a radial movement of the arm engagement member 30 in relation to the pivot point of the shoe 34.
  • the lever member 36 has a generally circular outline extending about the pivot shaft 16 but not necessarily coaxial thereto. The distance between the pivoting point at the shoe 34 and the arm engagement member 30 may vary according to the spring rate of the lever member 36 and the force acting on the arm engagement member 30.
  • the biasing force to drive the arm engagement member 30 into a frictional contact with the arm skirt 46 is created by the coil spring 18.
  • the base end tang 42 of the spring 18 is inserted in a correspondingly sized slot in the lip 24 of the base 20 located in such an angular position in relation to the pivoting shoe 34 that at least a bottom coil 50 of the spring 18 rests against the pin 40 attached to the lever 36, so that the torsional action on the spring 18 pushes the bottom coil 50 and the pin 40 towards the arm engagement member 30 forcing the latter against the skirt 46.
  • the arm engagement member 30 may change orientation in relation to the lever member 36 during operation. Specifically, the arm engagement member 30 may pivot on the lever member 36. As shown in Fig. 4, it is contemplated that a rear surface of the groove of the arm engagement member 30 has a protuberance 33. The protuberance 33 is received within a notch 37 formed in an outer peripheral surface of the lever member 36 when the arm engagement member 30 is interlocked with the lever member 36. Thus, the arm engagement member 30 may pivot on the lever member 36 about the protuberance 33. This pivotal movement allows the entire outer surface 38 of the arm engagement member 30 to maintain engagement with the skirt 46 during operation. It is further contemplated that the arm engagement member 30 may have some sliding free stroke in relation to the lever member 36.
  • the initial bias urging the arm engagement member 30 into contact with the skirt 46 can also arranged by using other means such as weights, separate springs or the spring action of the lever body. In these cases the coil spring 18 is not brought into contact with the lever member 36 and the location of the tang 42 can be made totally independent on the lever member 36.
  • the force by which the arm engagement member 30 is initially pressed against the sliding surface of the skirt 46 one can also provide some frictional damping of the tensioner 10. In the preferred embodiment of the invention, during the free standing condition before the initial installation of the tensioner onto the engine, the arm engagement member 30 will abut against the stop 31 in the base 20.
  • the angular position of the stop 31 is preferably selected in such a way that it does not allow the lever member 36 beyond its neutral position, i.e. the position where there is a least radial force between the arm engagement member 30 and the skirt 46, during its stroke towards free arm.
  • the pivoting arm 14 After the tensioner has been installed onto engine using a bolt or stud applied through the longitudinal hole in the pivot shaft 16, the pivoting arm 14 must be rotated towards the back stop direction towards stop 29 until there is enough clearance around the pulley 12 to place the belt member around the pulley 12. While the pivoting arm 14 is rotated into back stop direction, the arm engagement member 30, which has a frictional connection with the arm skirt 46 will initially, together with the lever member 36, follow the rotational movement of the arm 14.
  • the arm engagement member 30 will be wedged towards the arm skirt 46 under the radially inwardly directed force applied by spring 18 on pin 40 increasing the frictional forces between the arm engagement member 30 and the skirt 46. Because of the geometric relationship between the skirt 46, the arm engagement member 30 and the lever pivot point within pivot shoe 34 and the optional compression spring action of the lever member 36, the torque to resist the rotation of the lever member 36 will become greater than the rotational torque created by the friction force between the arm engagement member 30 and the skirt 46, and the arm engagement member 30 will start sliding on the skirt 46 allowing the pivoting arm 14 to continue its rotation towards back stop direction while the arm engagement member 30 stops moving.
  • the operator releases the pivoting arm 14, which will now be rotated towards the belt by the spring 18.
  • the arm engagement member 30 and the lever member 36 will follow the arm 14.
  • the arm engagement member 30 may be able to return as far as the stop 31.
  • the geometry of the lever mechanism and/or frictional characteristics between the arm engagement member 30 and the skirt 46, as well as within the lever mechanism itself, should be selected in such a way that they will not prohibit the easy return stroke of the arm 14, but will effectively stop the excessive arm movement towards the back stop direction during engine kick backs.
  • the spring 18 engages the pin 40 to bring the lever member 36 and hence the arm engagement member 30 into frictional engagement with the arm 14.
  • the pivoting arm length decreases which wedges the lever member 36 into the arm 14 and thus increases the frictional force between the arm engagement member 30 and the arm 14.
  • the increased frictional force is sufficient to stop movement of the arm 14 towards the back stop direction or a position of minimum belt take-up.
  • the tensioner multiplies the initial spring force by the wedging action of the lever member 36 and the arm engagement member 30.
  • the bias of the spring 18 and wedging action of the lever member 36 is not sufficient to increase the friction between the arm 14 and the arm engagement member 30 such that the arm 14 is permitted to move towards the free arm direction or a maximum belt take-up position.
  • the arm engagement member 30 is adapted to slide on the arm 14 if readjustment is necessary. Relative movement between the arm 14 and the arm engagement member 30 occurs only on readjustment of the belt and also on installation. Thus, movement of the arm 14 is inhibited only when the arm 14 moves towards the back stop direction, not towards the free arm direction.
  • lever member 36 pivots as much as the tensioner geometry, engine driving forces, coefficients of friction in both shoe 34 and arm engagement member 30, and overall spring rate of the design allows.

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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 un tendeur (10) comprenant une base (20) et un arbre pivot (16) s'étendant depuis la base. Un ressort (18) est connecté bras pivotant (14) afin de solliciter le bras (14) dans un engagement de tension avec un composant d'entraînement sans fin du moteur. Un assemblage antiretour flottant comprend un élément levier (36) et un élément d'engagement de bras (30). L'élément levier (36) est monté tournant sur la base, et l'élément d'engagement de bras (30) est engagé avec l'élément levier. L'élément levier (36) et l'élément d'engagement de bras (30) sont orientés de façon à ce que l'élément d'engagement de bras (30) puisse être sollicité par le ressort (18) en direction de la structure de surface arquée du bras pivotant (14) de façon à appliquer une force de friction qui suffit à arrêter le mouvement du bras (14).
PCT/CA2000/001403 1999-11-29 2000-11-29 Tendeur de courroie crantee a antiretour flottant WO2001040682A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE10085330T DE10085330T1 (de) 1999-11-29 2000-11-29 Synchronriemen-Spannvorrichtung mit schwimmendem Gegenhalter
CA002392560A CA2392560C (fr) 1999-11-29 2000-11-29 Tendeur de courroie crantee a antiretour flottant
AU18464/01A AU1846401A (en) 1999-11-29 2000-11-29 Timing belt tensioner having a floating backstop

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US16768099P 1999-11-29 1999-11-29
US60/167,680 1999-11-29

Publications (1)

Publication Number Publication Date
WO2001040682A1 true WO2001040682A1 (fr) 2001-06-07

Family

ID=22608352

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CA2000/001403 WO2001040682A1 (fr) 1999-11-29 2000-11-29 Tendeur de courroie crantee a antiretour flottant

Country Status (4)

Country Link
AU (1) AU1846401A (fr)
CA (1) CA2392560C (fr)
DE (1) DE10085330T1 (fr)
WO (1) WO2001040682A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002095262A3 (fr) * 2001-05-24 2003-04-10 Gates Corp Tendeur a amortissement asymetrique pour systeme de commande de courroie
WO2006137086A1 (fr) * 2005-06-20 2006-12-28 Dayco Europe S.R.L. Con Unico Socio Tendeur pour courroie asymétrique d’amortissement
CN109690132A (zh) * 2016-09-20 2019-04-26 舍弗勒技术股份两合公司 皮带张紧器

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4145934A (en) 1977-09-30 1979-03-27 Sragal Richard F Flexible endless drive means tensioning device
US4351636A (en) 1980-06-06 1982-09-28 Hager Clarence H Belt tensioning device
US4473362A (en) 1981-07-08 1984-09-25 Litens Automotive Inc. Belt tensioner with variably proportional damping
US4583962A (en) 1984-12-07 1986-04-22 Litens Automotive Inc. Timing belt tensioner with damped constant spring tensioning and belt tooth disegagement prevention
US4634407A (en) 1985-08-12 1987-01-06 Federal-Mogul Corporation Self-tensioning belt tightener
US4808148A (en) 1988-04-04 1989-02-28 Federal-Mogul Corporation Temperature compensated self-tensioning idler pulley
US4822322A (en) 1988-07-25 1989-04-18 Ina Bearing Co., Inc. Tensioning device for timing belt or chain in automotive engine applications
US4834694A (en) 1988-07-25 1989-05-30 Ina Bearing Co., Inc. Belt tensioning apparatus
US4923435A (en) 1986-12-27 1990-05-08 Koyo Seiko Co., Ltd. Chain or belt tensioner with a one-way clutch
DE4029940A1 (de) * 1990-09-21 1992-03-26 Kugelfischer G Schaefer & Co Daempfungseinrichtung fuer ein riemenspannsystem
EP0780597A1 (fr) * 1995-12-18 1997-06-25 The Gates Corporation d/b/a/ The Gates Rubber Company Tendeur de courroie avec moyens d'absorption des vibrations et système de transmission à courroie

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4145934A (en) 1977-09-30 1979-03-27 Sragal Richard F Flexible endless drive means tensioning device
US4351636A (en) 1980-06-06 1982-09-28 Hager Clarence H Belt tensioning device
US4473362A (en) 1981-07-08 1984-09-25 Litens Automotive Inc. Belt tensioner with variably proportional damping
US4473362B1 (fr) 1981-07-08 1991-07-09 Litens Automotive Inc
US4583962A (en) 1984-12-07 1986-04-22 Litens Automotive Inc. Timing belt tensioner with damped constant spring tensioning and belt tooth disegagement prevention
US4634407A (en) 1985-08-12 1987-01-06 Federal-Mogul Corporation Self-tensioning belt tightener
US4923435A (en) 1986-12-27 1990-05-08 Koyo Seiko Co., Ltd. Chain or belt tensioner with a one-way clutch
US4808148A (en) 1988-04-04 1989-02-28 Federal-Mogul Corporation Temperature compensated self-tensioning idler pulley
US4822322A (en) 1988-07-25 1989-04-18 Ina Bearing Co., Inc. Tensioning device for timing belt or chain in automotive engine applications
US4834694A (en) 1988-07-25 1989-05-30 Ina Bearing Co., Inc. Belt tensioning apparatus
DE4029940A1 (de) * 1990-09-21 1992-03-26 Kugelfischer G Schaefer & Co Daempfungseinrichtung fuer ein riemenspannsystem
EP0780597A1 (fr) * 1995-12-18 1997-06-25 The Gates Corporation d/b/a/ The Gates Rubber Company Tendeur de courroie avec moyens d'absorption des vibrations et système de transmission à courroie

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2002095262A3 (fr) * 2001-05-24 2003-04-10 Gates Corp Tendeur a amortissement asymetrique pour systeme de commande de courroie
AU2002312046B2 (en) * 2001-05-24 2005-01-20 The Gates Corporation Asymmetric damping tensioner belt drive system
WO2006137086A1 (fr) * 2005-06-20 2006-12-28 Dayco Europe S.R.L. Con Unico Socio Tendeur pour courroie asymétrique d’amortissement
US8337344B2 (en) 2005-06-20 2012-12-25 Dayco Europe S.R.L. Asymetric damping belt tensioner
CN109690132A (zh) * 2016-09-20 2019-04-26 舍弗勒技术股份两合公司 皮带张紧器
US11131366B2 (en) 2016-09-20 2021-09-28 Schaeffler Technologies AG & Co. KG Belt tensioner
CN109690132B (zh) * 2016-09-20 2022-06-17 舍弗勒技术股份两合公司 皮带张紧器

Also Published As

Publication number Publication date
DE10085330T1 (de) 2002-10-24
AU1846401A (en) 2001-06-12
CA2392560C (fr) 2008-06-17
CA2392560A1 (fr) 2001-06-07

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