WO2003100293A1 - Dispositif de tension hydraulique - Google Patents

Dispositif de tension hydraulique Download PDF

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Publication number
WO2003100293A1
WO2003100293A1 PCT/EP2003/005288 EP0305288W WO03100293A1 WO 2003100293 A1 WO2003100293 A1 WO 2003100293A1 EP 0305288 W EP0305288 W EP 0305288W WO 03100293 A1 WO03100293 A1 WO 03100293A1
Authority
WO
WIPO (PCT)
Prior art keywords
cylinder
piston
reservoir
clamping device
hydraulic fluid
Prior art date
Application number
PCT/EP2003/005288
Other languages
German (de)
English (en)
Inventor
Arbogast Grunau
Thomas Bertelshofer
Eduard Kratz
Christian SCHÄFER
Harald Schäfer
Dietmar JÄGER
Marco Orsi
Original Assignee
Ina-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 Ina-Schaeffler Kg filed Critical Ina-Schaeffler Kg
Priority to JP2004507714A priority Critical patent/JP2005526940A/ja
Priority to KR10-2004-7018334A priority patent/KR20050010801A/ko
Priority to AU2003240678A priority patent/AU2003240678A1/en
Publication of WO2003100293A1 publication Critical patent/WO2003100293A1/fr
Priority to US10/995,959 priority patent/US7686717B2/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
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • 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
    • 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
    • F16H7/0848—Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F16H2007/0859—Check valves
    • 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
    • F16H2007/0876—Control or adjustment of actuators
    • F16H2007/0878—Disabling during transport

Definitions

  • the present invention relates to a hydraulic-mechanical acting clamping device, which is intended for a traction drive.
  • the tensioning device comprises a pot-shaped housing which is pivotally fastened at one end, but in which a cylinder which is arranged radially offset to an outer wall of the housing is centrally arranged.
  • a longitudinally displaceable piston is guided in the cylinder and delimits on one side a pressure chamber of the cylinder filled with hydraulic fluid.
  • the piston is indirectly connected to a tensioning roller, which is supported by a compression spring, on a traction means, in particular a belt of the traction mechanism drive.
  • the pressure chamber of the cylinder is separated by a one-way valve from an annular interior, which is radially delimited by the outer wall of the cylinder and the inner wall of the housing.
  • the circular interior is partially filled with hydraulic fluid.
  • a piston movement causes a volume exchange between the pressure chamber and the interior. Depending on the direction of movement of the piston, this volume exchange of the hydraulic fluid takes place via the one-way valve or via a leakage gap that occurs between the piston and the cylinder.
  • a hydraulic tensioning device with a structure described above is known.
  • Such hydraulic tensioning device lines are preferably used in traction mechanism drives of internal combustion engines, for driving units such as water pumps, power steering pumps, air conditioning compressors or generators.
  • the tensioning device heats up, like all other components of the internal combustion engine.
  • the hydraulic fluid located in the leakage gap can be completely sucked into the pressure chamber as well as additional air due to a reduction in the volume of the pressure chamber in the clamping device.
  • an air inclusion in the pressure chamber of the tensioning device has the disadvantage that the compressible air does not allow a defined position of the tensioning device and thus the tensioning roller, which has a disadvantageous effect on the pretensioning force of the traction device and at the same time triggers a noise development of the entire tensioning device.
  • the reservoir is dimensioned or designed in such a way that a change in volume of the pressure chamber that occurs in the event of extreme temperature differences between the operating state and the standstill of the tensioning device can also be compensated for.
  • a corresponding size of the reservoir does not cause the leakage gap to empty in the cooling phase of the tensioning device, - when the internal combustion engine is at a standstill, - in which a negative pressure can develop in the pressure chamber of the cylinder.
  • the hydraulic fluid reservoir thus effectively prevents a so-called idle stroke, ie an air lock in the pressure chamber, which adversely affects the function of the tensioning device in the operating state affected.
  • the idle stroke leads to a malfunction of the tensioning device.
  • the cause is that during the cooling process of the tensioning device, ie when the internal combustion engine is at a standstill, a negative pressure is established in the pressure chamber of the cylinder.
  • the vacuum is not sufficient to open the one-way valve.
  • the negative pressure causes the hydraulic fluid enclosed in the leakage gap to be sucked up. After the leakage gap has been sucked empty, air from the interior of the housing penetrates through the leakage gap into the pressure chamber, which triggers the previously described idle stroke of the tensioning device.
  • the compressible air enclosed in the pressure chamber prevents the tensioning pulley from being clearly supported on the traction mechanism. Rather, an undefined pre-tensioning of the traction device occurs, combined with disadvantageous noise development, slippage of the traction device and an associated increased wear.
  • the air trapped in the pressure chamber only escapes after several strokes, i.e. H. Adjustments of the piston in the cylinder.
  • At least one circumferential groove is made in the inner wall of the cylinder.
  • a groove is alternatively also suitable, which is made in the outer surface of the piston.
  • a hydraulic fluid reservoir according to the invention can furthermore be formed by the combination of a groove arranged in the cylinder in connection with a piston groove.
  • a particularly advantageous configuration of the hydraulic fluid reservoir in terms of assembly provides for the groove in the cylinder and / or the groove in the piston to be designed in a wave shape. This measure enables an unimpeded axial insertion of the piston into the cylinder, the Piston to achieve a stroke limitation comprises a radially preloaded snap ring inserted in a piston groove, which in the installed position experiences a travel limitation on a projecting contour of the cylinder.
  • the hydraulic fluid reservoir which is designed as a corrugated groove, prevents the radially preloaded snap ring from locking in unintentionally.
  • a spiral-shaped circumferential groove on the inner wall of the cylinder is also suitable.
  • a circumferential chamfer or a rounded transition area on the groove wall of the reservoir oriented in the direction of the one-way valve is suitable.
  • Such a groove wall after the radially preloaded snap ring has locked into the groove, and when the piston is pushed in further, allows the snap ring to automatically move for the piston groove, i.e. shifts radially inwards.
  • the design diversity of the invention further enables the arrangement of several axially stepped grooves, which together form the hydraulic fluid reservoir.
  • Another variant of the invention includes a beveled or rounded transition area between the end face and the inner wall of the cylinder as a reservoir.
  • the required chamfer or chamfer on the cylinder can preferably be increased accordingly.
  • it is advisable for the chamfer to run at an angle "" of 10 ° or rounded.
  • An advantageous further exemplary embodiment according to the invention provides one or more bores which are preferably made radially or obliquely in the piston as the hydraulic fluid reservoir. Such a reservoir neither has a negative influence on the strength of the piston, nor does such a reservoir require a modified assembly.
  • the tensioning device provides that regardless of the position of the piston in the associated cylinder, the reservoir always remains in the area of the leakage gap. This measure ensures that the leakage gap has a sufficient hydraulic fluid volume and thus effectively avoids an adverse idle stroke.
  • a cylindrical shell is also suitable as the hydraulic fluid reservoir.
  • the separate component which is also shaped as a collar, is positively and / or fastened to the cylinder and thus brings about an axial extension of the piston.
  • the shell thus represents an axial extension of the cylinder and forms a large-volume, annular reservoir, which neither has an adverse effect on the strength of the piston-cylinder unit, nor does it adversely affect the assembly.
  • FIG. 1 shows a longitudinal section of a clamping device with a hydraulic fluid reservoir according to the invention in the leakage gap between the piston and the cylinder of the clamping device;
  • FIG. 2 shows a detail of the tensioning device according to FIG. 1 on an enlarged scale, the reservoir each comprising a groove in the cylinder and in the piston;
  • Figure 3 is a representation corresponding to Figure 2, in which the
  • Hydraulic fluid reservoir has two grooves in the cylinder and in the piston;
  • Figure 4 shows a half section, which is limited to a detail of the
  • Piston and cylinder provided with a wave-shaped groove of the cylinder
  • FIG. 5 shows a hydraulic fluid reservoir which is formed by a groove of the cylinder which extends in the form of a screw line;
  • FIG. 6 shows a hydraulic fluid reservoir which is provided in a transition area between the end face and the inner wall of the cylinder
  • Figure 7 shows a detail of the piston-cylinder unit, the different
  • Reservoirs includes.
  • a first reservoir is designed as a bore made radially in the piston.
  • the second reservoir is formed using a separate component.
  • FIG. 1 shows a hydraulic-mechanical clamping device 1, which comprises a pot-like, rotationally symmetrical housing 2, which is fixed via a mounting eye 3 but can be pivoted, for example, to an internal combustion engine not shown in FIG. 1.
  • a cylinder 5 is inserted centrally in the housing at a radial distance from an outer wall 4, in that a piston 6 is guided so as to be longitudinally displaceable.
  • the piston 6, which delimits a pressure chamber 7 in the cylinder 5 at the end, is provided at the end facing away from the pressure chamber 7 with a fastening eye 8, which cooperates directly or indirectly with a tensioning roller that engages Traction device, in particular a belt, biases the traction mechanism drive.
  • the tensioning roller is non-positively actuated by means of a helical compression spring 9, which is supported with a first spring end on a base 10 of the housing 2 and mutually with a second spring end on a spring support 11 which is integrally connected to the fastening eye 8 or to the piston 6.
  • An annular inner space 12 of the housing 2, which surrounds the cylinder 5, is filled with hydraulic fluid in the lower area directed towards the bottom 10, as is the pressure chamber 7.
  • An actuating movement of the piston 6 that reduces the pressure chamber 7 displaces hydraulic fluid via a leakage gap 13, which is established between a lateral surface 14 of the piston 6 and an inner wall 15 of the cylinder 5.
  • An opposite adjusting movement of the piston, which enlarges the pressure space 7, causes the hydraulic fluid to flow from the interior 12 via a one-way valve 16 arranged at the end of the cylinder 5 in the region of the base 10.
  • a reservoir 17a is provided in the area of the leakage gap 13.
  • the inner wall 15 of the cylinder 5 has a circumferential annular groove which fills with hydraulic fluid in the operating state of the tensioning device 1.
  • the idle state that is to say, for example, when the internal combustion engine is at a standstill
  • cooling of the tensioning device 1 can result in a negative pressure being established in the pressure chamber 7, which on the one hand is not sufficient to draw in hydraulic fluid via the one-way valve, but on the other hand sucks the leakage gap 13 filled with hydraulic fluid.
  • Air enclosed in the pressure chamber 7 leads to a so-called idle stroke, which, in the operating state of the tensioning device 1, does not allow a defined pretensioning of the traction means, due to the air compressibly enclosed in the pressure chamber 7.
  • the reservoir 17a according to the invention is dimensioned in such a way that it is used even in extreme temperature applications Clamping device 1 effectively prevents air from entering the pressure chamber 7.
  • the hydraulic fluid enclosed in the reservoir 17 a can consequently effectively compensate for a temperature-related hydraulic fluid requirement in the pressure chamber 7.
  • the tensioning device 1 also has an end stop 18 provided between the piston 6 and the cylinder 5.
  • a radially preloaded snap ring 19 is inserted into an annular groove 20 in the piston 6, which in the installed state locks onto a step 21 of the cylinder 5.
  • the cylinder 5 is provided on the end face with an insertion bevel 22 which, when the piston 6 is inserted into the cylinder 5, displaces the snap ring 19 radially inward into the annular groove 20, the snap ring 19 automatically expanding radially after reaching step 21 and one secure stroke limitation on the end stop 18 ensures.
  • FIGS. 2 to 7 show different hydraulic fluid reservoirs according to the invention, each of which is shown in connection with enlarged details of the tensioning device 1.
  • FIG. 2 shows a section of the tensioning device 1 which, in addition to the reservoir 17a already described in FIG. 1, has a second hydraulic fluid reservoir 17b arranged in the piston 6.
  • This measure increases the hydraulic fluid available in the leakage gap 13, which can flow in when a vacuum occurs in the pressure chamber 7.
  • the reservoir 17a is also designed such that when the piston 6 is inserted into the cylinder 5, the snap ring 19 does not permanently latch into the reservoir 17a designed as a groove.
  • the wall pointing in the direction of the pressure chamber 7 is provided with a rounded transition area 23.
  • the reservoir shown in Figure 3 is formed from two small-sized reservoirs 17a, 17b in the piston 6 and in the cylinder 5.
  • FIGS. 4 and 5 each show a partial section of the cylinder 5 in a half section.
  • the position and shape of the reservoirs 17c, 17d prevent the snap ring 19 connected to the piston 6 from latching into the reservoir 17c, 17d.
  • FIG. 4 shows a groove running on the circumferential side, which forms the reservoir 17c.
  • the reservoir 17d is designed in the form of a groove running helically on the inner wall 15.
  • the reservoir 17e according to FIG. 6 represents an enlarged insertion bevel 22, which, as explained in the description of FIG. 1, simplifies the assembly and the insertion of the piston 6 into the cylinder 5.
  • the reservoir 17e preferably has a wedge-shaped or triangular cross-sectional profile and can be manufactured inexpensively in the manufacturing process of the cylinder 5.
  • FIG. 7 shows sections of the cylinder 5 and the piston 6, which have two differently designed reservoirs 17f, 17g.
  • the reservoir 17f is formed by a bore made in the piston 6 that is inclined radially or obliquely. Both one or more blind holes and one or more through holes are suitable for this.
  • the reservoir 17g represents a separate cylindrical component, designed as a collar 25, which causes the cylinder 5 to be axially extended in the direction of the spring support 11.
  • the collar 25 thus radially delimits the annularly shaped reservoir 17g.
  • the collar 25 can be non-positively attached to the outer contour of the cylinder 5 or can be non-detachably connected to the cylinder 5, for example by means of soldering or welding.
  • a radially inwardly directed bead 26 of the collar 25 determines the installation position of the collar 25.
  • the collar 25 is preferably provided at the end with a radially inwardly directed fold 27.
  • the tensioning device 1 can be provided with the previously described differently designed hydraulic fluid reservoirs 17a to 17g, any combination of different reservoirs also being possible.
  • One-way valve a reservoir b reservoir c reservoir d reservoir e reservoir f reservoir g reservoir

Abstract

La présente invention concerne un dispositif de tension hydraulique (1) dans lequel un piston (6) est guidé de façon à se déplacer longitudinalement dans un cylindre (5). Un espace de fuite (13) se formant entre le piston (6) et le cylindre (5) est pourvu d'un réservoir à fluide hydraulique (17a).
PCT/EP2003/005288 2002-05-23 2003-05-20 Dispositif de tension hydraulique WO2003100293A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2004507714A JP2005526940A (ja) 2002-05-23 2003-05-20 液圧式の緊張装置
KR10-2004-7018334A KR20050010801A (ko) 2002-05-23 2003-05-20 유압식 인장 장치
AU2003240678A AU2003240678A1 (en) 2002-05-23 2003-05-20 Hydraulic tensioning device
US10/995,959 US7686717B2 (en) 2002-05-23 2004-11-23 Hydraulic tensioner

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10222752A DE10222752A1 (de) 2002-05-23 2002-05-23 Hydraulische Spannvorrichtung
DE10222752.7 2002-05-23

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US10/995,959 Continuation US7686717B2 (en) 2002-05-23 2004-11-23 Hydraulic tensioner

Publications (1)

Publication Number Publication Date
WO2003100293A1 true WO2003100293A1 (fr) 2003-12-04

Family

ID=29414045

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2003/005288 WO2003100293A1 (fr) 2002-05-23 2003-05-20 Dispositif de tension hydraulique

Country Status (6)

Country Link
JP (1) JP2005526940A (fr)
KR (1) KR20050010801A (fr)
CN (1) CN100443772C (fr)
AU (1) AU2003240678A1 (fr)
DE (1) DE10222752A1 (fr)
WO (1) WO2003100293A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009074566A1 (fr) * 2007-12-10 2009-06-18 Schaeffler Kg Élément élastique mécanique pour transmissions par lien souple

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4891697B2 (ja) * 2006-08-10 2012-03-07 株式会社オティックス 油圧式オートテンショナ
DE102007047170A1 (de) * 2006-11-24 2008-05-29 Schaeffler Kg Plattenventil für Zugmittelspannsysteme
WO2008087900A1 (fr) * 2007-01-16 2008-07-24 Ntn Corporation Tensionneur automatique
DE102007031292A1 (de) 2007-07-05 2009-01-08 Schaeffler Kg Hydraulisch-mechanische Spannvorrichtung für einen Zugmitteltrieb
DE102008011787A1 (de) * 2008-02-28 2009-09-03 Schaeffler Kg Ventilkappe für ein Rückschlagventil
US8066598B2 (en) * 2008-10-09 2011-11-29 GM Global Technology Operations LLC Chain tensioning apparatus with temperature-based leakdown
DE102008057041A1 (de) * 2008-11-12 2010-05-20 Schaeffler Kg Linear wirkendes Spannelement
DE102010049900A1 (de) * 2010-10-28 2012-05-03 Schaeffler Technologies Gmbh & Co. Kg Spanneinrichtung mit zylindrischem Rastsystem
DE102013217272A1 (de) 2013-08-29 2015-03-05 Branson Ultraschall Niederlassung Der Emerson Technologies Gmbh & Co. Ohg Zugmittelspanner, Vibrationsschweißanlage mit Zugmittelspanner sowie Herstellungsverfahren eines Zugmittelspanners
US10452094B2 (en) 2014-09-08 2019-10-22 Schaeffler Technologies AG & Co. KG Tensioning device having a transport securing concept
JP6539564B2 (ja) * 2015-10-26 2019-07-03 Ntn株式会社 油圧式オートテンショナ

Citations (6)

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Publication number Priority date Publication date Assignee Title
US4790801A (en) * 1988-04-04 1988-12-13 Ina Walzlager Schaeffler Kg Mechanic-hydraulic actuating element for a belt tightener
EP0718525A2 (fr) * 1993-10-01 1996-06-26 Gustav Wahler GmbH u. Co Dispositif d'actionnement pour mécanisme tendeur
DE19653066A1 (de) * 1995-12-20 1997-07-17 Tsubakimoto Chain Co Spannvorrichtung
DE19828309A1 (de) * 1998-06-25 1999-12-30 Schaeffler Waelzlager Ohg Spanneinrichtung
FR2803005A1 (fr) * 1999-12-24 2001-06-29 Sachs Automotive France Sa Tendeur hydraulique pour lien sans fin, systeme de distribution comprenant un tel tendeur et moteur equipe d'un tel systeme de distribution
JP2001221306A (ja) * 2000-02-07 2001-08-17 Otics Corp 油圧式オートテンショナ

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DE4124500C2 (de) * 1991-07-24 1997-07-10 Ebern Fahrzeugtech Gmbh Hydraulisch gedämpftes Spannelement
DE29508244U1 (de) * 1995-05-18 1995-08-24 Schaeffler Waelzlager Kg Hydraulische Spannvorrichtung für einen Zugmitteltrieb
JP3058815B2 (ja) * 1995-08-11 2000-07-04 株式会社オティックス 油圧式オートテンショナ
DE19539616A1 (de) * 1995-10-25 1997-04-30 Suspa Compart Ag Mit Fluid gefüllte Zylinder-Kolbenstangen-Einheit, insbesondere Gasfeder
JP3378719B2 (ja) * 1996-01-26 2003-02-17 株式会社オティックス 油圧式オートテンショナ
DE19609420B4 (de) * 1996-03-11 2004-02-19 Ina-Schaeffler Kg Spanneinrichtung für Zugmittel
JP4084485B2 (ja) * 1999-01-14 2008-04-30 株式会社オティックス 油圧式オートテンショナ
JP4025448B2 (ja) * 1999-02-01 2007-12-19 株式会社オティックス 油圧式オートテンショナ

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4790801A (en) * 1988-04-04 1988-12-13 Ina Walzlager Schaeffler Kg Mechanic-hydraulic actuating element for a belt tightener
EP0718525A2 (fr) * 1993-10-01 1996-06-26 Gustav Wahler GmbH u. Co Dispositif d'actionnement pour mécanisme tendeur
DE19653066A1 (de) * 1995-12-20 1997-07-17 Tsubakimoto Chain Co Spannvorrichtung
DE19828309A1 (de) * 1998-06-25 1999-12-30 Schaeffler Waelzlager Ohg Spanneinrichtung
FR2803005A1 (fr) * 1999-12-24 2001-06-29 Sachs Automotive France Sa Tendeur hydraulique pour lien sans fin, systeme de distribution comprenant un tel tendeur et moteur equipe d'un tel systeme de distribution
JP2001221306A (ja) * 2000-02-07 2001-08-17 Otics Corp 油圧式オートテンショナ

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Title
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 25 12 April 2001 (2001-04-12) *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009074566A1 (fr) * 2007-12-10 2009-06-18 Schaeffler Kg Élément élastique mécanique pour transmissions par lien souple

Also Published As

Publication number Publication date
CN1656328A (zh) 2005-08-17
CN100443772C (zh) 2008-12-17
JP2005526940A (ja) 2005-09-08
DE10222752A1 (de) 2003-12-04
KR20050010801A (ko) 2005-01-28
AU2003240678A1 (en) 2003-12-12

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