US20080318716A1 - Tensioning Device Pertaining to a Traction Mechanism Drive - Google Patents

Tensioning Device Pertaining to a Traction Mechanism Drive Download PDF

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Publication number
US20080318716A1
US20080318716A1 US11/910,552 US91055206A US2008318716A1 US 20080318716 A1 US20080318716 A1 US 20080318716A1 US 91055206 A US91055206 A US 91055206A US 2008318716 A1 US2008318716 A1 US 2008318716A1
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US
United States
Prior art keywords
tensioning
support element
support
piston
shoe
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/910,552
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English (en)
Inventor
Thomas Ullein
Reinhard Koch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
IHO Holding GmbH and Co KG
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
Assigned to SCHAEFFLER KG reassignment SCHAEFFLER KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KOCH, REINHARD, ULLEIN, THOMAS
Publication of US20080318716A1 publication Critical patent/US20080318716A1/en
Abandoned legal-status Critical Current

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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
    • 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
    • F16H7/18—Means for guiding or supporting belts, ropes, or chains
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0812—Fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0863—Finally actuated members, e.g. constructional details thereof
    • F16H2007/0872—Sliding members

Definitions

  • the invention relates to a tensioning device of a traction mechanism drive, with a tensioning piston, which is mounted so that it can move in the axial direction and which is provided with an attachment shaft facing the traction mechanism, with a tensioning shoe made from plastic mounted via a support hole on the attachment shaft, and with a disk-shaped metallic support element having a support hole fixed to the attachment shaft.
  • Traction mechanism drives such as chain drives and toothed belt drives, are used in many machines for power transfer due to their reliability and cost-effectiveness, e.g., also for driving camshafts in reciprocating internal combustion engines of motor vehicles.
  • Traction mechanism drives frequently have vibration dampers in the form of housing-fixed sliding shoes, which are preferably made from a low-friction polymer plastic or from a guide rail made from metal coated with this material and which are in sliding contact with the traction mechanism, for preventing vibrations of the traction mechanism chain or toothed belt.
  • the sliding shoes could be arranged both on the tensioned side and also on the loose side of the traction mechanism.
  • traction mechanism drives usually also have a tensioning device arranged on the loose side.
  • This tensioning device has available a tensioning piston, which is mounted so that it can move in the axial direction and which acts on a tensioning shoe loaded by a spring element and/or a compression means.
  • This tensioning shoe deflects the loose side of the traction mechanism normal toward its direction of motion and also toward the rotational axes of the gears and thus compensates for the longitudinal expansion and tensions the traction mechanism.
  • a tensioning device for a chain drive in which a tensioning shoe is formed as a separate component and which is mounted so that it can rotate about a housing-fixed shaft.
  • a tensioning piston which loads the tensioning shoe with a compressive force, is located at a distance from the shaft and thus presses this shoe against the loose side of the chain, whereby this is tensioned. Due to the slide-shifting contact of the tensioning shoe with the tensioning piston, rotation due to operation is largely prevented between the tensioning piston and the tensioning shoe.
  • a disadvantage in this known tensioning device is the large number of components and the relatively large spatial requirements.
  • a tensioning device for a chain drive in which two tensioning shoes made from a polymer plastic and aligned opposite one another are fixed rigidly to a tensioning lever, which is formed as a rocking lever and which is mounted between the two tensioning shoes so that it can rotate about a housing-fixed shaft.
  • a tensioning piston loads the tensioning lever at a distance from the shaft with a compressive force and thus presses both tensioning shoes in opposite directions against the loose side of the chain, whereby this is tensioned. Due to the rotating support of the tensioning lever and the sliding contact of the tensioning lever with the tensioning piston, no large rotation occurs between the tensioning shoes and the tensioning lever.
  • the number of components and the spatial requirements are increased disadvantageously relative to the construction named above.
  • a first tensioning device constructed in this way is known as a component of a camshaft chain drive from DE 40 06 910 C1, in which a tensioning shoe is arranged, with less projection of the tensioning piston and thus unfavorably smaller contact surface to the chain, directly on the attachment shaft of the tensioning piston.
  • a tensioning device that can be produced simply and economically, in which a tensioning shoe with large projection of the tensioning piston is produced from a polymer plastic, provided with a central support hole, and connected to this rigidly by insertion on a cylindrical support shaft of the tensioning piston.
  • a tensioning shoe with large projection of the tensioning piston is produced from a polymer plastic, provided with a central support hole, and connected to this rigidly by insertion on a cylindrical support shaft of the tensioning piston.
  • a disk-shaped metallic transfer element with a central support hole in front of the tensioning shoe is pressed onto the support shaft and fused or welded with this.
  • the force transfer between the tensioning shoe and the tensioning piston is definitely improved, but disadvantageously the production process becomes more complicated.
  • the fusing or welding of the support element with the tensioning piston can lead to undesired deformation and twisting in both components.
  • the invention is based on the knowledge that through a large-area introduction of load forces and bending moments from the tensioning shoe made from a polymer plastic into the metallic support element and through forwarding of the bending moment into the tensioning piston essentially via the support element, smaller peak loads appear in the tensioning shoe and thus a more stable unit made from the tensioning piston, support element, and tensioning shoe is formed without complicated measures.
  • a tensioning device with the features of the preamble of claim 1 , in which the support element is pre-mounted in or on the tensioning shoe in a non-positive and/or positive fit connection and that the support element is connected in the mounted state to the tensioning piston by a press fit between its support hole and the attachment shaft, and also contacts a shoulder of the tensioning piston.
  • the tensioning shoe is connected to the disk-shaped support element with a non-positive and/or positive fit and the support element is pressed onto the attachment shaft of the tensioning piston and contacts the shoulder, loads occurring during operation are distributed between the tensioning shoe and the support element each over a relatively large area, so that local tensioning peaks and overloading the polymer plastic of the tensioning shoe, especially in the region of the support hole of the tensioning shoe, are prevented.
  • the generated load forces can be transmitted through the press fit in connection with the large-area contact on the shoulder between the support element and the tensioning piston.
  • the operation-dependent loads are introduced from the tensioning shoe into the tensioning piston essentially via the press fit of the support hole of the support element with the attachment shaft of the tensioning piston, and only to a smaller extent via the contact of the support hole of the tensioning shoe with the attachment shaft, which can be formed as a clearance fit or also as a loose press fit.
  • both components are pressed onto the attachment shaft of the tensioning piston in a common processing step.
  • the components are easily set up and thus can be produced economically.
  • the assembly of the components is also simple and can be performed quickly.
  • the support element is preferably extrusion coated with the polymer plastic of the tensioning shoe, which produces an optimum contact between the tensioning shoe and the support element and which also can be produced easily and economically.
  • the tensioning shoe on the side facing the tensioning piston has an over-dimensioned recess adapted to the support element with at least two projecting locking tabs, which are arranged on opposing edges of the recess and in which the supported element is pressed and locked.
  • the tensioning shoe is provided with a slot, which is open on one side and which is aligned parallel to the side facing the tensioning piston and which is adapted to the support element and in which the support element is pushed and fixed through the placement of the tensioning shoe onto the support shaft of the tensioning piston.
  • the support hole of the support element can also preferably have a narrow section, which can be formed, for example, by an inward deviation from the circular hole edge.
  • the reinforcement of the locking of the support element on the support shaft is here caused by a partial plastic deformation of the hole edge of the support element in the region of the throat.
  • FIG. 1 a a first embodiment of a tensioning device according to the invention in a lateral section IA-IA,
  • FIG. 1 b the tensioning device according to FIG. 1 a in a cross section IB-IB,
  • FIG. 2 a a second embodiment of a tensioning device in a lateral section IIA-IIA
  • FIG. 2 b the tensioning device according to FIG. 2 a in a cross section IIB-IIB
  • FIG. 3 a a third embodiment of a tensioning device in a lateral section IIIA-IIIA
  • FIG. 3 b the tensioning device according to FIG. 3 a in a cross section IIIB-IIIB
  • FIG. 6 a a second embodiment of a known tensioning device in a lateral section VIA-VIA
  • FIG. 6 b the known tensioning device according to FIG. 6 a in a cross section VIB-VIB
  • FIG. 7 a a first refinement of the tensioning device according to the invention in a top view of the support element
  • FIG. 7 b the first refinement according to FIG. 7 a in a top view of the tensioning piston
  • FIG. 8 a a second refinement of the tensioning device according to the invention in a top view of the support element
  • FIG. 8 b the second refinement according to FIG. 8 a in a top view of the tensioning piston.
  • a tensioning shoe 2 made from a polymer plastic is pressed with a central support hole 3 directly onto the cylindrical attachment shaft 4 of a tensioning piston 5 .
  • the tensioning shoe 2 projects over the tensioning piston 5 in the direction of motion 6 of the not-shown traction mechanism and each has a guide crossbar 7 for lateral guiding of the traction mechanism. Due to the smaller diameter of the attachment shaft 4 relative to the main part 8 of the tensioning piston 5 , a shoulder 9 is formed, which is used as a stop for the tensioning shoe 2 .
  • a disk-shaped support element 11 made from steel with a central support hole 12 is pushed up to the shoulder 9 on the attachment shaft 4 of the tensioning piston 5 and welded with the main part 8 of the tensioning piston 5 .
  • the tensioning shoe 2 is pressed with its central support hole 3 up to contact with the support element 11 on the attachment shaft 4 of the tensioning piston 5 .
  • the force transmission from the tensioning shoe 2 into the tensioning piston 5 is improved by the support element 11 .
  • generated bending moments 10 are absorbed by the support element 11 and introduced into the tensioning piston 5 , so that the load in the support hole 3 of the tensioning shoe 2 becomes significantly less.
  • a disadvantage is the increased processing expense for the mounting of the components and possible deformation and twisting of the support element 11 and the tensioning piston 5 caused by the welding.
  • the support element 11 is extrusion coated with the polymer plastic of the tensioning shoe 2 .
  • the unit formed in this way from the tensioning shoe 2 and the support element 11 is pressed with its support holes 3 , 12 until contact of the support element 11 with the shoulder 9 on the attachment shaft 4 of the tensioning piston 5 .
  • the pairing of support hole 12 of the support element 11 with the attachment shaft 4 of the tensioning piston 5 forms a fixed press fit, so that the force transmission between the tensioning shoe 2 and the tensioning piston 5 is performed essentially via the support element 11 .
  • the pairing of the support hole 3 of the tensioning shoe 2 with the attachment shaft 4 of the tensioning piston 5 is constructed as a clearance fit or as a loose press fit.
  • the tensioning shoe 2 has on its inside 13 facing the tensioning piston 5 an under-dimensioned recess 14 . 1 , which is adapted to the support element 11 and in which the support element 11 is pressed.
  • the unit formed by the pre-mounting of the support element 11 in the tensioning shoe 2 is installed by pressing until the support element 11 contacts the shoulder 9 on the attachment shaft 4 of the tensioning piston 5 , wherein the pairing of the support hole 12 of the support element 11 with the attachment shaft 4 of the tensioning piston 5 forms, in turn, a fixed press fit.
  • the force transmission from the tensioning shoe 2 into the tensioning piston 5 has a very favorable construction also for this construction.
  • the tensioning shoe 2 on the inside 13 facing the tensioning piston 5 has an over-dimensioned recess 14 . 2 , which is adapted to the support element 11 and which is provided with at least two projecting locking tabs 16 arranged on opposing edges 15 of the recess 14 . 2 .
  • the support element 11 is pressed into the recess 14 . 2 and locked behind the locking tabs 16 .
  • the unit formed by the pre-mounting of the support element 11 in the tensioning shoe 2 is installed by pressing until the support element 11 contacts the shoulder 9 on the attachment shaft 4 of the tensioning piston 5 , wherein the pairing of the support hole 12 of the support element 11 forms, in turn, a fixed press fit with the attachment shaft 4 of the tensioning piston 5 . Therefore, for this construction the force transmission from the tensioning shoe 2 into the tensioning piston 5 is also optimal with a simple and economical setup.
  • the tensioning shoe 2 is provided with a slot 17 , which is open on one side and which is aligned parallel to the inside 13 facing the tensioning piston 5 and which is adapted to the support element 11 .
  • the support element 11 is pushed laterally into the slot 17 and fixed on the support shaft 4 of the tensioning piston 5 by pressing the unit formed from the tensioning shoe 2 and the support element 11 .
  • the tensioning shoe 5 is pressed onto the attachment shaft 4 of the tensioning piston 5 until the support element 11 contacts the shoulder 9 , and the pairing of the support hole 12 of the support element 11 with the attachment shaft 4 of the tensioning piston 5 forms a fixed press fit.
  • a favorable force transmission is also realized from the tensioning shoe 2 into the tensioning piston 5 in connection with a simple and economical setup.
  • the attachment shaft 4 of the tensioning piston 5 and the support hole 12 of the support element 11 each have shaped elements 18 . 1 and 18 . 2 , respectively, corresponding geometrically to each other for mutual directional fixing.
  • the shaped element 18 . 1 of the tensioning piston 5 is formed as a one-sided flattened section 19 . 1 of the circular cross section of the attachment shaft 4 and the shaped element 18 . 2 of the support element 11 is formed as a corresponding one-sided flattened section 19 . 2 of the circular support hole 12 in the form of a secant.
  • the support hole 12 of the support element 11 has throat sections 20 , which are formed in the present case by a formation of the hole edge 21 of the support hole 12 in the form of a hexagon polygonal secant course 22 .
  • the partial plastic deformation of the hole edge 21 caused in this way during the pressing of the unit formed from the tensioning shoe 2 and the support element 11 on the attachment shaft 4 of the tensioning piston 5 a reinforcement of the locking of the support element 11 on the support shaft 4 is produced. Therefore, the connection of the tensioning shoe 2 , support element 11 , and tensioning piston 5 can be loaded overall in a more stable and stronger way.

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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)
US11/910,552 2005-04-28 2006-03-21 Tensioning Device Pertaining to a Traction Mechanism Drive Abandoned US20080318716A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102005019694.2 2005-04-28
DE102005019694A DE102005019694A1 (de) 2005-04-28 2005-04-28 Spannvorrichtung eines Zugmitteltriebes
PCT/EP2006/002549 WO2006114168A1 (de) 2005-04-28 2006-03-21 Spannvorrichtung eines zugmitteltriebes

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/002549 A-371-Of-International WO2006114168A1 (de) 2005-04-28 2006-03-21 Spannvorrichtung eines zugmitteltriebes

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US12/685,848 Division US8696501B2 (en) 2005-04-28 2010-01-12 Tensioning device pertaining to a traction mechanism drive

Publications (1)

Publication Number Publication Date
US20080318716A1 true US20080318716A1 (en) 2008-12-25

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Application Number Title Priority Date Filing Date
US11/910,552 Abandoned US20080318716A1 (en) 2005-04-28 2006-03-21 Tensioning Device Pertaining to a Traction Mechanism Drive
US12/685,848 Expired - Fee Related US8696501B2 (en) 2005-04-28 2010-01-12 Tensioning device pertaining to a traction mechanism drive

Family Applications After (1)

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US12/685,848 Expired - Fee Related US8696501B2 (en) 2005-04-28 2010-01-12 Tensioning device pertaining to a traction mechanism drive

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US (2) US20080318716A1 (ko)
EP (1) EP1877682B1 (ko)
KR (1) KR101277879B1 (ko)
DE (2) DE102005019694A1 (ko)
WO (1) WO2006114168A1 (ko)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012166358A2 (en) * 2011-06-03 2012-12-06 Borgwarner Inc. Tensioner and shoe therefor
CN108533703A (zh) * 2017-03-02 2018-09-14 伊威斯发动机系统有限责任两合公司 带有侧向环绕的夹子元件的张紧轨道或导向轨道

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007046816A1 (de) * 2007-09-29 2009-04-02 Schaeffler Kg Kettenspanneinrichtung, insbesondere für einen Steuerkettentrieb
JP2013083292A (ja) * 2011-10-07 2013-05-09 Tsubakimoto Chain Co 伝動装置用ガイド
DE102015008877A1 (de) * 2015-07-08 2016-08-04 Iwis Motorsysteme Gmbh & Co. Kg Modulare Gleit- oder Spannschiene
JP6408974B2 (ja) * 2015-10-21 2018-10-17 株式会社椿本チエイン チェーンガイド
KR20200105922A (ko) * 2018-01-31 2020-09-09 보르그워너 인코퍼레이티드 캡 디스크 스프링을 구비한 가변력 텐셔너 아암

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US2963918A (en) * 1958-08-12 1960-12-13 Perry Chain Company Ltd Chain or belt tensioning devices
US3626776A (en) * 1969-09-15 1971-12-14 Winkelhofer & Soehne Joh Chain tensioning device
US3802286A (en) * 1972-03-16 1974-04-09 Winkelhofer & Soehne Joh Chain tensioning device
US3812733A (en) * 1972-05-17 1974-05-28 Yamakyu Chan Kk Tensioning device for flexible members
US4472161A (en) * 1981-03-03 1984-09-18 Nhk Spring Co., Ltd. Tension providing mechanism
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US4722720A (en) * 1985-04-30 1988-02-02 Nhk Spring Co., Ltd. Tension providing device
US4747811A (en) * 1986-01-25 1988-05-31 Fuji Jukogyo Kabushiki Kaisha Automatic belt tensioner
US4838840A (en) * 1987-03-23 1989-06-13 Fuji Jukogyo Kabushiki Kaisha Automatic belt tensioner
US5030170A (en) * 1989-05-10 1991-07-09 Nhk Spring Co., Ltd. Belt or chain tensioner for power transmitting system
US5088966A (en) * 1989-10-27 1992-02-18 Tsubakimoto Chain Co. Tensioner having pad made of plastics
US5197420A (en) * 1990-12-24 1993-03-30 General Motors Corporation Camshaft adjuster and tensioner
US5248282A (en) * 1991-10-23 1993-09-28 Tsubakimoto Chain Co. Oil-operated tensioner
US5595549A (en) * 1994-01-17 1997-01-21 Sachs Industries S.A. (Huret Et Maillard Reunis) Hydraulic tensioner with lubricator for IC engine transmission chain
US5601505A (en) * 1994-09-12 1997-02-11 Borg-Warner Automotive, K.K. Hydraulic tensioner
US5606941A (en) * 1994-08-17 1997-03-04 Dr.Ing. H.C.F. Porsche Ag Variable timing camshaft drive system
US5628701A (en) * 1995-12-08 1997-05-13 Borg-Warner Automotive, Inc. Hydraulic tensioner with sealing element
US5782625A (en) * 1995-12-07 1998-07-21 Cloyes Gear & Products Automatic tensioner with one-pin locking mechanism

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US2963918A (en) * 1958-08-12 1960-12-13 Perry Chain Company Ltd Chain or belt tensioning devices
US3626776A (en) * 1969-09-15 1971-12-14 Winkelhofer & Soehne Joh Chain tensioning device
US3802286A (en) * 1972-03-16 1974-04-09 Winkelhofer & Soehne Joh Chain tensioning device
US3812733A (en) * 1972-05-17 1974-05-28 Yamakyu Chan Kk Tensioning device for flexible members
US4472161A (en) * 1981-03-03 1984-09-18 Nhk Spring Co., Ltd. Tension providing mechanism
US4702726A (en) * 1985-04-26 1987-10-27 Nhk Spring Co., Ltd. Tension providing device
US4722720A (en) * 1985-04-30 1988-02-02 Nhk Spring Co., Ltd. Tension providing device
US4747811A (en) * 1986-01-25 1988-05-31 Fuji Jukogyo Kabushiki Kaisha Automatic belt tensioner
US4838840A (en) * 1987-03-23 1989-06-13 Fuji Jukogyo Kabushiki Kaisha Automatic belt tensioner
US5030170A (en) * 1989-05-10 1991-07-09 Nhk Spring Co., Ltd. Belt or chain tensioner for power transmitting system
US5088966A (en) * 1989-10-27 1992-02-18 Tsubakimoto Chain Co. Tensioner having pad made of plastics
US5197420A (en) * 1990-12-24 1993-03-30 General Motors Corporation Camshaft adjuster and tensioner
US5248282A (en) * 1991-10-23 1993-09-28 Tsubakimoto Chain Co. Oil-operated tensioner
US5595549A (en) * 1994-01-17 1997-01-21 Sachs Industries S.A. (Huret Et Maillard Reunis) Hydraulic tensioner with lubricator for IC engine transmission chain
US5606941A (en) * 1994-08-17 1997-03-04 Dr.Ing. H.C.F. Porsche Ag Variable timing camshaft drive system
US5601505A (en) * 1994-09-12 1997-02-11 Borg-Warner Automotive, K.K. Hydraulic tensioner
US5782625A (en) * 1995-12-07 1998-07-21 Cloyes Gear & Products Automatic tensioner with one-pin locking mechanism
US5628701A (en) * 1995-12-08 1997-05-13 Borg-Warner Automotive, Inc. Hydraulic tensioner with sealing element

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012166358A2 (en) * 2011-06-03 2012-12-06 Borgwarner Inc. Tensioner and shoe therefor
WO2012166358A3 (en) * 2011-06-03 2013-03-07 Borgwarner Inc. Tensioner and shoe therefor
US20140106913A1 (en) * 2011-06-03 2014-04-17 Borgwarner Inc. Tensioner and shoe therefor
JP2014518997A (ja) * 2011-06-03 2014-08-07 ボーグワーナー インコーポレーテッド テンショナおよびテンショナ用シュー
US9366322B2 (en) * 2011-06-03 2016-06-14 Borgwarner Inc. Tensioner and shoe therefor
CN108533703A (zh) * 2017-03-02 2018-09-14 伊威斯发动机系统有限责任两合公司 带有侧向环绕的夹子元件的张紧轨道或导向轨道

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Publication number Publication date
EP1877682B1 (de) 2009-03-18
DE502006003190D1 (de) 2009-04-30
KR20080003837A (ko) 2008-01-08
US8696501B2 (en) 2014-04-15
US20100113198A1 (en) 2010-05-06
DE102005019694A1 (de) 2006-11-02
WO2006114168A1 (de) 2006-11-02
EP1877682A1 (de) 2008-01-16
KR101277879B1 (ko) 2013-06-21

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