WO2006111988A1 - Tightener for a belt drive operating in the presence of oil - Google Patents

Tightener for a belt drive operating in the presence of oil Download PDF

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Publication number
WO2006111988A1
WO2006111988A1 PCT/IT2005/000230 IT2005000230W WO2006111988A1 WO 2006111988 A1 WO2006111988 A1 WO 2006111988A1 IT 2005000230 W IT2005000230 W IT 2005000230W WO 2006111988 A1 WO2006111988 A1 WO 2006111988A1
Authority
WO
WIPO (PCT)
Prior art keywords
tightener
arm
oil
base plate
pin
Prior art date
Application number
PCT/IT2005/000230
Other languages
French (fr)
Other versions
WO2006111988A8 (en
Inventor
Michele Cantatore
Original Assignee
Dayco Europe S.R.L. Con Unico Socio
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 Dayco Europe S.R.L. Con Unico Socio filed Critical Dayco Europe S.R.L. Con Unico Socio
Priority to PCT/IT2005/000230 priority Critical patent/WO2006111988A1/en
Priority to CN2005800501818A priority patent/CN101218453B/en
Priority to JP2008507274A priority patent/JP4772865B2/en
Priority to AT05743469T priority patent/ATE502233T1/en
Priority to DE602005027001T priority patent/DE602005027001D1/en
Priority to EP05743469A priority patent/EP1877683B1/en
Priority to US11/912,117 priority patent/US20080287233A1/en
Publication of WO2006111988A1 publication Critical patent/WO2006111988A1/en
Publication of WO2006111988A8 publication Critical patent/WO2006111988A8/en
Priority to US13/271,457 priority patent/US8690718B2/en

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
    • F16H7/0831—Means for varying tension of belts, ropes, or chains with vibration damping means of the dry friction type

Definitions

  • the present invention relates to a tightener for a belt drive operating in the presence of oil .
  • Known belt drives such as for driving an internal combustion engine camshaft, are normally used in dry- applications, in which a tightener is used to maintain correct tension of the belt.
  • Cam tighteners for dry applications comprising a fixed member with a supporting pin; a spring-loaded cam arm; an idle pulley fitted to the cam arm and cooperating with a timing belt; and a bushing of friction material interposed radially between the fixed pin and the cam arm to damp vibration of the belt .
  • chains are normally used, which cooperate with a shoe to maintain correct tension.
  • Figure 1 shows an exploded view in perspective of a tightener in accordance with the present invention
  • Figure 2 shows a front view of Figure 1;
  • Figure 3 shows a section along line III-III in Figure 2.
  • Number 1 in Figure 1 indicates a tightener for a belt drive operating in the presence of oil, and comprising a fixed pin 2; a metal cam arm 3 mounted for rotation on fixed pin 2 and connected to a tensioning spring 4; and a hollow pulley 5 radially surrounding cam arm 3 and cooperating with and contacting a cog belt .
  • fixed pin 2 has a cylindrical mounting surface 6 having an axis A; a through hole 7 having an axis B eccentric with respect to axis A; an end shoulder 8; and a contoured head 9 at the opposite end of cylindrical surface 6 to end shoulder 8.
  • Through hole 7 extends through contoured head 9, which is symmetrical with respect to a plane through axes A and B.
  • Cam arm 3 fits radially onto mounting surface 6 by means of a bushing 10 made of antifriction material, e.g. teflon, and has an annular housing 11, and a cylindrical outer surface 12 having an axis C eccentric with respect to axes A and B. More specifically, cylindrical outer surface 12 supports hollow pulley 5 by means of a bearing 13, and housing 11 is open towards end shoulder 8, houses the whole of tensioning spring 4, and has a slot for connection to an end portion 14 of tensioning spring 4.
  • a bushing 10 made of antifriction material, e.g. teflon
  • Cam arm 3 is supported axially by an annular base plate 15 connected perpendicularly to fixed pin 2, and by a friction ring 16 interposed between cam arm 3 and base plate 15 and made of material capable of maintaining friction even in the presence of oil, such as BERAL 1122 marketed by Federal-Mogul Friction Products Gmbh.
  • the friction material used comprises an oil-resistant binder comprising caoutchouc; and a mixture of additives for obtaining friction in the presence of oil and comprising rock wool, magnesium oxide, graphite, and clay.
  • the physical characteristics of the material used are: specific weight (measured at 20 0 C) 2.04*10 A -3 kg/cm A 3; thermal conductivity 1.00 W/m*°C; approximate dry friction coefficient 0.47; and approximate oil-bath friction coefficient 0.10.
  • cam arm 3 has an integral, radially peripheral collar 17 facing base plate 15 and defining a seat to make friction ring 16 radially integral with cam arm 3.
  • Base plate 15 comprises an inner edge 18 which rests axially on end shoulder 8; and a projection 19 projecting towards cam arm 3 and cooperating both with arm 3, to define two limit positions, and with an end portion (not shown) opposite end portion 14, to tension spring 4.
  • cam arm 3 and contoured head 9 of fixed pin 2 define an annular seat 21 coaxial with axis A and for housing a supporting cup made of plastic, a Belleville washer 24, and a circular cover plate 25.
  • cup 23 comprises, integrally, a flat portion 26 perpendicular to axis A; and a peripheral edge 27 parallel to axis A.
  • Peripheral edge 27 houses
  • Bellville washer 24 radially, and, together with cover plate 25, defines an annular gap 28 to allow oil in to lubricate Belleville washer 24 and mounting surface 6.
  • Belleville washer 24 is pressed axially against flat portion 26 by cover plate 25. More specifically, cover plate 25 is connected angularly rigidly to contoured head
  • Tightener 1 is fitted to a wall of an internal combustion engine by means of a screw 29 housed inside through hole 7. More specifically, contoured head 9 is bounded by a supporting surface 30 projecting axially with respect to cover plate 25, and end shoulder 8 is bounded by a supporting surface 31 projecting axialIy with respect to base plate 15, so that, when tightener 1 is fixed to the engine, the head 32 of screw 29 cooperates with supporting surface 30, and supporting surface 31 directly contacts the wall of the engine to keep base plate 15 detached.
  • the pull exerted by the screw is therefore transmitted to fixed pin 2, and the axial load of friction ring 16, which is much less than the pull exerted by the screw, is controlled accurately by sizing Belleville washer 24.
  • Belleville washer 24 in fact, is used in the maximum-compression condition, in which it exerts substantially constant force alongside minor variations in the axial dimension of cam arm 3 , caused, for example, by in-service wear of friction ring 16.
  • tightener 1 comprises numerous component parts in common with a dry-operating tightener, thus enabling mass production cost benefits. More specifically, by replacing friction ring 16 with a PTFE ring, tightener 1 may also be used dry. Moreover, using an oil-resistant friction material, cost is further reduced by eliminating in-process cleaning of metal parts, i.e. fixed pin 2 and cam arm 3. The fact that the whole of tensioning spring 4 is housed axially inside housing 11 of cam arm 3 provides for reducing length to adapt to applications featuring belts operating in the presence of oil, and which generally tend to replace chains which permit particularly short lengths.
  • friction ring 16 may be housed inside a groove defined by cam arm 3, or may be glued.
  • Hollow pulley 5 and bearing 13 may be replaced by a shoe having a ring member fitted to cylindrical outer surface 12 and integral with cam arm 3.
  • supporting cup 23 may be eliminated, and Belleville washer 24 may contact cam arm 3 directly, provided gap 28 is sized to allow sufficient oil through to lubricate the surfaces in relative motion.
  • the friction material used comprises a caoutchouc- based binder if a flexible friction ring 16 is required. If a rigid friction ring is required, caoutchouc is not used.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Pulleys (AREA)
  • Transmission Devices (AREA)
  • Advancing Webs (AREA)
  • Jigs For Machine Tools (AREA)
  • Mounting, Exchange, And Manufacturing Of Dies (AREA)

Abstract

A tightener (1) cooperating with a belt in the presence of oil, and having a pin (2) having a first axis (A); a base plate (15) integral with and substantially perpendicular to the pin (2); a cam arm (3) connected in rotary manner to the pin (2) and movable with respect to the base plate (15); a contact member (5) carried by the cam arm (3); and an elastic member (4) connected to the cam arm (3) to activate the contact member (5) against the belt. The tightener (1) also has a friction member (16) made of oil-resistant material and axially supporting the cam arm (3) on the base plate (15); and axial elastic means (24) for loading the friction member (16) against the base plate (15).

Description

TIGHTENER FOR A BELT DRIVE OPERATING IN THE PRESENCE OF OIL
TECHNICAL FIELD
The present invention relates to a tightener for a belt drive operating in the presence of oil . BACKGROUND ART
Known belt drives, such as for driving an internal combustion engine camshaft, are normally used in dry- applications, in which a tightener is used to maintain correct tension of the belt.
Cam tighteners for dry applications are known comprising a fixed member with a supporting pin; a spring-loaded cam arm; an idle pulley fitted to the cam arm and cooperating with a timing belt; and a bushing of friction material interposed radially between the fixed pin and the cam arm to damp vibration of the belt .
For applications in the presence of oil, chains are normally used, which cooperate with a shoe to maintain correct tension.
Belt applications in the presence of oil have recently been developed, in which known tighteners have proved ineffective in maintaining correct tension.
DISCLOSURE OF INVENTION
It is an object of the present invention to provide a tightener for a belt drive operating in the presence of oil, designed to eliminate the aforementioned drawback.
According to the present invention, there is provided a tightener as claimed in Claim 1.
BRIEF DESCRIPTION OF THE DRAWINGS
A preferred, non-limiting embodiment of the present invention will be described by way of example with reference to the accompanying drawings, in which:
Figure 1 shows an exploded view in perspective of a tightener in accordance with the present invention;
Figure 2 shows a front view of Figure 1; Figure 3 shows a section along line III-III in Figure 2.
BEST MODE FOR CARRYING OUT THE INVENTION
Number 1 in Figure 1 indicates a tightener for a belt drive operating in the presence of oil, and comprising a fixed pin 2; a metal cam arm 3 mounted for rotation on fixed pin 2 and connected to a tensioning spring 4; and a hollow pulley 5 radially surrounding cam arm 3 and cooperating with and contacting a cog belt .
More specifically, fixed pin 2 has a cylindrical mounting surface 6 having an axis A; a through hole 7 having an axis B eccentric with respect to axis A; an end shoulder 8; and a contoured head 9 at the opposite end of cylindrical surface 6 to end shoulder 8. Through hole 7 extends through contoured head 9, which is symmetrical with respect to a plane through axes A and B.
Cam arm 3 fits radially onto mounting surface 6 by means of a bushing 10 made of antifriction material, e.g. teflon, and has an annular housing 11, and a cylindrical outer surface 12 having an axis C eccentric with respect to axes A and B. More specifically, cylindrical outer surface 12 supports hollow pulley 5 by means of a bearing 13, and housing 11 is open towards end shoulder 8, houses the whole of tensioning spring 4, and has a slot for connection to an end portion 14 of tensioning spring 4.
Cam arm 3 is supported axially by an annular base plate 15 connected perpendicularly to fixed pin 2, and by a friction ring 16 interposed between cam arm 3 and base plate 15 and made of material capable of maintaining friction even in the presence of oil, such as BERAL 1122 marketed by Federal-Mogul Friction Products Gmbh.
More specifically, the friction material used comprises an oil-resistant binder comprising caoutchouc; and a mixture of additives for obtaining friction in the presence of oil and comprising rock wool, magnesium oxide, graphite, and clay. The physical characteristics of the material used are: specific weight (measured at 200C) 2.04*10A-3 kg/cmA3; thermal conductivity 1.00 W/m*°C; approximate dry friction coefficient 0.47; and approximate oil-bath friction coefficient 0.10.
More specifically, cam arm 3 has an integral, radially peripheral collar 17 facing base plate 15 and defining a seat to make friction ring 16 radially integral with cam arm 3.
Base plate 15 comprises an inner edge 18 which rests axially on end shoulder 8; and a projection 19 projecting towards cam arm 3 and cooperating both with arm 3, to define two limit positions, and with an end portion (not shown) opposite end portion 14, to tension spring 4.
On the opposite side to base plate 15, cam arm 3 and contoured head 9 of fixed pin 2 define an annular seat 21 coaxial with axis A and for housing a supporting cup made of plastic, a Belleville washer 24, and a circular cover plate 25.
More specifically, cup 23 comprises, integrally, a flat portion 26 perpendicular to axis A; and a peripheral edge 27 parallel to axis A. Peripheral edge 27 houses
Bellville washer 24 radially, and, together with cover plate 25, defines an annular gap 28 to allow oil in to lubricate Belleville washer 24 and mounting surface 6.
Belleville washer 24 is pressed axially against flat portion 26 by cover plate 25. More specifically, cover plate 25 is connected angularly rigidly to contoured head
9 by a matching shape fit, and is fixed axially by caulking.
Tightener 1 is fitted to a wall of an internal combustion engine by means of a screw 29 housed inside through hole 7. More specifically, contoured head 9 is bounded by a supporting surface 30 projecting axially with respect to cover plate 25, and end shoulder 8 is bounded by a supporting surface 31 projecting axialIy with respect to base plate 15, so that, when tightener 1 is fixed to the engine, the head 32 of screw 29 cooperates with supporting surface 30, and supporting surface 31 directly contacts the wall of the engine to keep base plate 15 detached. The pull exerted by the screw is therefore transmitted to fixed pin 2, and the axial load of friction ring 16, which is much less than the pull exerted by the screw, is controlled accurately by sizing Belleville washer 24. Belleville washer 24, in fact, is used in the maximum-compression condition, in which it exerts substantially constant force alongside minor variations in the axial dimension of cam arm 3 , caused, for example, by in-service wear of friction ring 16.
The advantages of the tightener according to the present invention are as follows.
Using an axially-loaded, oil-resistant friction ring 16 provides for achieving satisfactory damping in the presence of oil. Moreover, tightener 1 comprises numerous component parts in common with a dry-operating tightener, thus enabling mass production cost benefits. More specifically, by replacing friction ring 16 with a PTFE ring, tightener 1 may also be used dry. Moreover, using an oil-resistant friction material, cost is further reduced by eliminating in-process cleaning of metal parts, i.e. fixed pin 2 and cam arm 3. The fact that the whole of tensioning spring 4 is housed axially inside housing 11 of cam arm 3 provides for reducing length to adapt to applications featuring belts operating in the presence of oil, and which generally tend to replace chains which permit particularly short lengths.
Clearly, changes may be made to the tightener as described and illustrated herein without, however, departing from the scope pf the present invention as defined in the accompanying Claims. For example, friction ring 16 may be housed inside a groove defined by cam arm 3, or may be glued.
Hollow pulley 5 and bearing 13 may be replaced by a shoe having a ring member fitted to cylindrical outer surface 12 and integral with cam arm 3. To reduce the number of component parts of tightener 1, supporting cup 23 may be eliminated, and Belleville washer 24 may contact cam arm 3 directly, provided gap 28 is sized to allow sufficient oil through to lubricate the surfaces in relative motion. The friction material used comprises a caoutchouc- based binder if a flexible friction ring 16 is required. If a rigid friction ring is required, caoutchouc is not used.

Claims

1) A tightener (1) for a belt drive operating in the presence of oil, comprising a pin (2) having a first axis (A) ; a base plate (15) integral with and substantially perpendicular to said pin (2) ; a cam arm (3) connected in rotary manner to said pin (2) and movable with respect to said base plate (15) ; a contact member (5) carried by said arm (3) ; and an elastic member (4) connected to said arm (3) to activate said contact member (5) against said belt; characterized by comprising a friction member (16) made of oil-resistant polymer material and axially supporting said arm (3) on said base plate (15) ; and axial elastic means (24) for loading said friction member (16) against said base plate (15) .
2) A tightener as claimed in Claim 1, characterized in that said arm (3) defines a seat (21) coaxial with said first axis (A) ; and in that said axial elastic means (24) are housed inside said seat (21) . 3) A tightener as claimed in Claim 2, characterized by comprising a tightening plate (25) connected rigidly to said pin (2) to compress said axial elastic means (24) .
4) A tightener as claimed in Claim 3, characterized in that said tightening plate (25) defines a gap (28) to permit lubrication of said axial elastic means (24) .
5) A tightener as claimed in any one of the foregoing Claims, characterized in that said axial elastic means (24) directly contact said arm (3) .
6) A tightener as claimed in any one of the foregoing Claims, characterized in that said contact member (5) comprises a hollow pulley. 7) A tightener as claimed in any one of the foregoing Claims, characterized in that said contact member comprises a shoe connected to said arm (3) .
8) A tightener as claimed in any one of the foregoing Claims, characterized in that said friction ring (16) comprises rock wool, magnesium oxide, graphite, and clay.
9) A tightener as claimed in Claim 8, characterized in that said friction ring (16) comprises a caoutchouc- based binder. 10) A tightener as claimed in any one of the foregoing Claims, characterized in that said arm (3) defines a housing (11) completely housing said elastic member (4) .
PCT/IT2005/000230 2005-04-20 2005-04-20 Tightener for a belt drive operating in the presence of oil WO2006111988A1 (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
PCT/IT2005/000230 WO2006111988A1 (en) 2005-04-20 2005-04-20 Tightener for a belt drive operating in the presence of oil
CN2005800501818A CN101218453B (en) 2005-04-20 2005-04-20 Tightener for a belt drive operating in the presence of oil
JP2008507274A JP4772865B2 (en) 2005-04-20 2005-04-20 Tensioner for belt drive operating in oil
AT05743469T ATE502233T1 (en) 2005-04-20 2005-04-20 TENSIONING DEVICE FOR A BELT DRIVE WORKING IN THE PRESENCE OF OIL
DE602005027001T DE602005027001D1 (en) 2005-04-20 2005-04-20 IN THE PRESENCE OF OIL WORKING CLAMPING DEVICE FOR A BELT DRIVE
EP05743469A EP1877683B1 (en) 2005-04-20 2005-04-20 Tightener for a belt drive operating in the presence of oil
US11/912,117 US20080287233A1 (en) 2005-04-20 2005-04-20 Tightener for a Belt Drive Operating in the Presence of Oil
US13/271,457 US8690718B2 (en) 2005-04-20 2011-10-12 Tightener for a belt drive operating in the presence of oil

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/IT2005/000230 WO2006111988A1 (en) 2005-04-20 2005-04-20 Tightener for a belt drive operating in the presence of oil

Related Child Applications (2)

Application Number Title Priority Date Filing Date
US11/912,117 A-371-Of-International US20080287233A1 (en) 2005-04-20 2005-04-20 Tightener for a Belt Drive Operating in the Presence of Oil
US13/271,457 Division US8690718B2 (en) 2005-04-20 2011-10-12 Tightener for a belt drive operating in the presence of oil

Publications (2)

Publication Number Publication Date
WO2006111988A1 true WO2006111988A1 (en) 2006-10-26
WO2006111988A8 WO2006111988A8 (en) 2007-05-31

Family

ID=34968018

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/IT2005/000230 WO2006111988A1 (en) 2005-04-20 2005-04-20 Tightener for a belt drive operating in the presence of oil

Country Status (7)

Country Link
US (2) US20080287233A1 (en)
EP (1) EP1877683B1 (en)
JP (1) JP4772865B2 (en)
CN (1) CN101218453B (en)
AT (1) ATE502233T1 (en)
DE (1) DE602005027001D1 (en)
WO (1) WO2006111988A1 (en)

Cited By (8)

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WO2008068782A1 (en) 2006-12-04 2008-06-12 Dayco Europe S.R.L. Pulley tensioner for a belt drive for use in contact with oil.
US20080176687A1 (en) * 2007-01-22 2008-07-24 Holger Schever Tensioner and installation assembly
WO2008149389A1 (en) 2007-06-05 2008-12-11 Dayco Europe S.R.L. Pulley tensioner for an oil wet belt drive
WO2008149390A1 (en) * 2007-06-05 2008-12-11 Dayco Europe S.R.L. Pulley tensioner for an oil wet belt drive
US7951030B2 (en) 2008-12-04 2011-05-31 The Gates Corporation Tensioner
US8326514B2 (en) 2007-03-27 2012-12-04 Dayco Europe S.R.L. Drive for an internal combustion engine comprising an oil wet toothed belt and a tensioning shoe
US8734279B2 (en) 2011-06-08 2014-05-27 Gates Corporation Tensioner
US8926462B2 (en) 2012-10-24 2015-01-06 The Gates Corporation Tensioner

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WO2006111988A1 (en) 2005-04-20 2006-10-26 Dayco Europe S.R.L. Con Unico Socio Tightener for a belt drive operating in the presence of oil
CN102261443B (en) * 2010-05-27 2014-03-12 盖茨优霓塔传动系统（上海）有限公司 Tensioner
DE202010017870U1 (en) * 2010-09-03 2012-11-27 Schaeffler Technologies AG & Co. KG Eccentric tensioner
WO2014063228A1 (en) 2012-10-22 2014-05-01 Litens Automotive Partnership Tensioner with increased damping
DE112014004168T5 (en) * 2013-09-11 2016-06-16 Litens Automotive Partnership CLAMPING DEVICE WITH INCREASED CUSHIONING AND ARM-ON-BASE CUP CONFIGURATION
ITTO20131032A1 (en) * 2013-12-17 2015-06-18 Dayco Europe Srl TENSIONER FOR A BELT DRIVE
US10859141B2 (en) * 2015-10-28 2020-12-08 Litens Automotive Partnership Tensioner with first and second damping members and increased damping
DE102015222203B4 (en) * 2015-11-11 2020-03-12 Schaeffler Technologies AG & Co. KG Backlash-free pendulum bearing on the decoupling clamp
US20180056157A1 (en) * 2016-08-27 2018-03-01 Bernard Cohen Backyard tailgating golf game
US10989280B2 (en) * 2017-06-16 2021-04-27 Gates Corporation Tensioner
US10995829B2 (en) * 2017-06-16 2021-05-04 Gates Corporation Tensioner
US10968988B2 (en) * 2017-06-16 2021-04-06 Gates Corporation Tensioner
US11421561B2 (en) * 2017-07-05 2022-08-23 Gates Corporation Synchronous belt drive system
US10753436B2 (en) * 2018-06-20 2020-08-25 Gates Corporation Tensioner
US11168767B2 (en) * 2018-10-23 2021-11-09 Gates Corporation Tensioner
CN109611523B (en) * 2019-02-20 2023-08-22 无锡永凯达齿轮有限公司 High damping timing belt tensioner
US11255414B2 (en) * 2019-05-15 2022-02-22 Gates Corporation Tensioner
US11359702B2 (en) * 2019-07-25 2022-06-14 Shihwen Chan Multi-configuration belt tensioner
JP2024507592A (en) * 2021-02-26 2024-02-20 デイコ アイピー ホールディングス，エルエルシー High offset belt tensioner with counterbalancing torsion spring force
IT202100014756A1 (en) * 2021-06-07 2022-12-07 Dayco Europe Srl TENSIONER WITH DOUBLE DAMPING SYSTEM FOR A TIMING BELT DRIVE
EP4423407A1 (en) * 2021-10-29 2024-09-04 Gates Corporation Bearing pivot tensioner assembly

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US20080287233A1 (en) 2008-11-20
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DE602005027001D1 (en) 2011-04-28
EP1877683B1 (en) 2011-03-16
US20120040789A1 (en) 2012-02-16
CN101218453B (en) 2012-06-20
US8690718B2 (en) 2014-04-08
WO2006111988A8 (en) 2007-05-31
ATE502233T1 (en) 2011-04-15
JP2008537079A (en) 2008-09-11

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