DE4035823C1 - Hydraulic tensioner for chain drives - has pressure restrictor valve in bottom of tension piston guide - Google Patents

Hydraulic tensioner for chain drives - has pressure restrictor valve in bottom of tension piston guide

Info

Publication number
DE4035823C1
DE4035823C1 DE19904035823 DE4035823A DE4035823C1 DE 4035823 C1 DE4035823 C1 DE 4035823C1 DE 19904035823 DE19904035823 DE 19904035823 DE 4035823 A DE4035823 A DE 4035823A DE 4035823 C1 DE4035823 C1 DE 4035823C1
Authority
DE
Germany
Prior art keywords
guide bush
pressure
piston
guide
damping
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.)
Expired - Fee Related
Application number
DE19904035823
Other languages
German (de)
Inventor
Josef 8019 Steinhoering De Heiler
Karl 8000 Muenchen De Brinz
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Priority to DE19904035823 priority Critical patent/DE4035823C1/en
Application granted granted Critical
Publication of DE4035823C1 publication Critical patent/DE4035823C1/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

Links

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H7/0829Means for varying tension of belts, ropes, or chains with vibration damping means
    • F16H7/0836Means for varying tension of belts, ropes, or chains with vibration damping means of the fluid and restriction type, e.g. dashpot
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H7/0848Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H2007/0802Actuators for final output members
    • F16H2007/0806Compression coil springs
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H2007/0802Actuators for final output members
    • F16H2007/0812Fluid pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H2007/0802Actuators for final output members
    • F16H2007/0812Fluid pressure
    • F16H2007/0814Fluid pressure with valves opening on surplus pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H7/0848Means for varying tension of belts, ropes, or chains with means for impeding reverse motion
    • F16H2007/0859Check valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H7/00Gearings for conveying rotary motion by endless flexible members
    • F16H7/08Means for varying tension of belts, ropes, or chains
    • F16H2007/0889Path of movement of the finally actuated member
    • F16H2007/0891Linear path

Abstract

The hydraulic tensioner for chain drives includes a pressure restrictor valve (13) which is mounted in the bottom (19) of a tension piston guide with radial downstream path (20) and designed as a separate guide sleeve. The downstream path forms by an outer circumferential section (24) of the guide sleeve (2) and a radially spaced inner wall (23) of a component housing the guide sleeve an axially aligned downstream path (21) with a predefined annular cross-section (25) as a further restriction point (15) for the parallel acting damping. The downstream path (14) can be connected downstream of the further restriction point with the pressure connection (11). ADVANTAGE - Satisfactory parallel damping wherein the throttle cross-section between the surfaces of the components is non-sensitive to the particles floating in with the hydraulic medium.

Description

The invention relates to a hydraulic clamping device for traction mechanism transmissions, in particular chains drives in internal combustion engines, according to the in the preamble of claim 1 type described.

Such a tensioning device is from DE-A-32 17 632 known. In the range of usual loads of the Clamping piston through the traction mechanism gearbox is one hydraulic damping via the leakage of the tensioning piston leadership achieved, the degree of leakage in the we substantial about a predetermined game between instep piston and guidance results. With pronounced blows of the Traction means on the tensioning piston can bring them out ble leakage amounts are not sufficient for damping, so that this in fact a blocking of the clamping device can result in high pressures in the damping chamber. Around To counteract this fact, the damping chamber is included a pressure relief valve. This alone leads to a relatively quick response Pressure reduction in the damping chamber, so that the tensioning piston can be excited to undesirable natural vibrations. There is therefore one in the outflow path of the pressure relief valve  additional throttling point provided in the case of sudden Loads on the tensioning piston parallel to the above Leakage damping works.

The known further throttle point is as a throttle channel of considerable length with a minimal cross section a number of threads one in a cylindrical Bore of the clamping piston arranged threaded bolt educated. The minimum cross section of this restriction harbors the risk of occlusion with the hydrau particles washed into the medium.

The invention has for its object a Spannvor direction of the generic type with another Throttle point to create whose between surfaces existing throttle cross section to be trained in is essentially insensitive to the hydraulic pressure dium washed-in particles, so that the parallel damper is properly ensured.

This task is solved with the characteristic features len of claim 1.

With the invention, the further throttling point as an annular gap of considerable cross cut between an outer peripheral portion Clamping piston receiving guide bushing and one radial spaced inner wall of the guide bushing receiving component achieved, with this Ring cross section in a further advantageous manner essential against washed-in particles insensitive throttle point for parallel damping is created.

According to the invention of claim 1, the Hydraulikme dium downstream of the further throttle point for parallel  Damping freely in an essentially on the surrounding Drain off the pressurized area of the machine. A preferred embodiment of the invention in contrast lower circulation quantity of hydraulic or lubricant is described in claim 2. Starting from the from the DE-A-36 36 918 known clamping device with a in a guide bush slidably guided tensioning piston with one with the lubrication system of the machine in mediums leading connecting pantry for the Damping chamber is the hydraulic medium downstream of the another throttle point the pressure connection of the lubricant systems fed to the jig. The further one Throttle point is dimensioned so that the throttled Return to the pressure connection without influencing the pressure level in the lubrication system remains.

Preferred further embodiments of the invention be write claims 3 to 6.

The invention is based on Darge in the drawing presented preferred embodiments described. It shows:

Fig. 1 shows a first hydraulic tensioner with a pressure limiting valve and a throttle position as provided annular cross-section between a guide bush for the tensioning piston and the inner wall of the guide bush on receiving machine part,

Fig. 2 shows a modified clamping device according to Fig. 1 having an annular cross-section between a guide sleeve and is in the machine part arranged sleeve,

Fig. 3 shows a further modification of the clamping device according to Fig. 1 with a ring cross-section between a locking screw fixing a guide bush in the machine part and this guide bush.

A hydraulic tensioning device 1 for an endless traction mechanism, in particular chain tensioner for the valve drive of an internal combustion engine, not shown, comprises a in a guide bushing 2 slidably arranged tensioning piston 3 , the device in the direction of tension (arrow A) is acted upon by a compression spring 4 . The hollow-shaped tensioning piston 3 has a bottom part 5 against which the compression spring 4 rests and with which the tensioning piston 3 in the guide bushing 2 limits a damping chamber 6 . The damping chamber 6 is provided via a check valve 7 in the base part 5 from a storage space 8 in the hollow tensioning piston 3 with hydraulic medium. The storage space 8 is connected via an inlet bore 9 in the clamping piston 3 and an inlet 10 in the guide bush 2 with a pressure connection 11 in a machine part 12 receiving the clamping device 1 . The pressure connection 11 is connected to the pressure lubrication system of the internal combustion engine, not shown.

The hydraulic damping of the spring-loaded tensioning piston 3 is achieved at usual loads by displacing hydraulic medium from the damping chamber 6 via the play between the tensioning piston 3 and the guide bushing 2 , these leakage quantities via the check valve 7 from the storage space 8 when the tensioning piston 3 is extended Arrow direction "A" to be replaced. In order for impact loading of the tensioning piston 3 from the train center transmission a high pressure peaks in the pressure chamber 6 is connected, relative "blocking" or "stiffening" of the clamping device 1 to avoid the damping chamber 6 acts with a pressure relief valve 13 and a in a discharge path 14 (20 and 21) of this valve 14 arranged throttle point 15 together. A pressure relief valve 13 without a downstream throttle point causes a steep or rapid pressure drop in the damping chamber 6, as a result of which the spring-loaded tensioning piston 3 is excited in a disadvantageous manner to undesirable natural vibrations. With the downstream throttle point 15 for the aforementioned damping leakage of a small amount via the play of the tensioning piston 3 in the guide bushing 2 , a leakage of a relatively large amount, which acts in parallel according to the high pressures in the damping chamber, is avoided by means of the natural vibrations of the tensioning piston 3 are.

As Fig. 1 shows, the separate bushing 2 is centered in a recess 16 of the machine part 12 in kolbenseiti gen end region via a collar 17 and secured at the other end by a closure screw 18. In the strike on the screw 18 the bottom 19 of the guide bush 2 , the pressure limiter valve 13 is arranged, the radial outflow paths 20 are assigned. This is followed by an axial outflow path 21 , a portion of the inner wall 23 of the recess 16 with the outer periphery 24 of the guide bush 2 forming a throttle 15 acting as a ring cross section 25 between the screw plug 18 and the pressure connection 11 with a circumferential channel 22 . The ring cross-section 25 acting as a throttle point 15 is thus achieved over spaced surfaces of given components and thus eliminates the need for additional means. Furthermore, the ring cross-section 25 is dimensioned such that the leakage quantity flowing to the pressure connection 11 or to the peripheral channel 22 does not exceed the delivery pressure present in the pressure connection 11 . This avoids adverse effects on the lubrication system of the internal combustion engine. In addition, with the connection of the outflow path 14 or 21 downstream of the throttle point 15 to the pressure connection 11 connected to the pressure lubrication system, the circulating quantity of hydraulic medium is reduced.

The exemplary embodiment according to FIG. 2 differs from that of FIG. 1 only in that a sleeve 27, which is arranged coaxially with the guide bushing 26 and extends from the pressure limiting end region 19 to the collar 17 , has an opening 28 corresponding to the pressure connection 11 over a section the inner wall 29 with the outer circumference 30 of the guide bush 26 forms an annular cross section 31 acting as a throttle point 15 . With the in the recess 16 of the machine part 12 between the collar 17 of the guide sleeve 26 and the locking screw 18 releasably arranged th sleeve 27 can be adapted to the respective application requirements of the hydraulic clamping device 1 by appropriate choice of their inner diameter of the ring cross section 31 .

Fig. 3 finally shows a hydraulic Spannvorrich device 1 with a guide bush 32 , the cylindrical bottom 19 with a constriction 33 on the closure screw 18 forms an annular cross section 34 of the throttle point 15 . The amount of leakage flowing out over the ring cross section 34 is fed via a channel 35 to a suction-side collecting chamber for the lubricant of the machine (not shown). Instead of the channel 35 , the arrangement shown can of course also be formed with a feed to the pressure connection 11 .

In the context of the invention, the throttle point 15 can also be variable, in particular variable depending on the pressure, for. B. by one of the cross-sectional change serving movable piston valve.

Claims (6)

1. hydraulic tensioning device for traction mechanism transmissions, in particular chain drives in internal combustion engines,
  • - In which in the clamping direction spring-loaded clamping piston ( 3 ) in a guide (guide bush 2, 26, 32 ) a via a check valve ( 7 ) connected to a hydraulic system of the machine damping chamber ( 6 ) from which
  • - For a first damping of the tensioning piston ( 3 ) via a predetermined play between the tensioning piston ( 3 ) and the guide ( 2 ), hydraulic medium throttled as a leak, and
  • - The damping chamber ( 6 ) also interacts with a pressure limiting valve ( 13 ) and a further throttle point arranged in an outflow path ( 14 or 21 ) of this valve for a parallel damping, characterized in that
  • - That the pressure relief valve ( 13 ) in the bottom ( 19 ) egg ner as a separate guide bush ( 2 , 26 , 32 ) designed th clamping piston guide with a radial outflow path ( 20 ) is arranged,
  • - of, on an outer peripheral portion (24, 30, or 19) of the guide bush (2, 26, 32) and a radially spaced inner wall (23, 29, 33) of the guide bush (2, 26, 32) receiving component (machine part 12 Sleeve 27 , screw plug 18 ) form an axially directed th outflow path ( 21 ) with a predetermined ring cross section ( 25 , 31 , 34 ) as a further throttle point ( 15 ) for the parallel damping.
2. Clamping device according to claim 1, wherein the guide bush ( 2 , 26 , 32 ) in a recess ( 16 ) from a machine part ( 12 ) with a connected to the lubrication system of the machine, the damping chamber ( 6 ) via a storage space ( 8 ) in a hollow pressure piston ( 3 ) supplying pressure connection ( 11 ) is arranged, characterized in that
  • - That the discharge path ( 14 or 21 ) downstream of the further throttle point ( 15 ) with the pressure connection ( 11 ) is in communication. ( Fig. 1-3)
3. Clamping device according to claims 1 to 2, characterized in
  • - That in the recess ( 16 ) of the machine part ( 12 ) arranged guide bush ( 2 ) in the pressure relief valve end region (bottom 19 ) held by a screw plug ( 18 ) and provided in the piston-side end region via a connection beyond the pressure ( 11 ) Collar ( 17 ) is centered,
  • - Wherein between the screw plug ( 18 ) and the pressure connection ( 11 ) with a circumferential channel ( 22 ) a portion of the inner wall ( 23 ) of the recess ( 16 ) with the outer circumference ( 24 ) of the guide bush ( 2 ) as a further throttle point ( 15th ) acting ring cross section ( 25 ). ( Fig. 1)
4. Clamping device according to claims 1 to 2, characterized in that
  • - That the in a recess ( 16 ) of the machine part ( 12 ) arranged guide bush ( 26 ) in the pressure relief valve end area held by a screw plug ( 18 ) and in the piston-side end area via a pressure connection ( 11 ) provided beyond the collar ( 17 ) is centered
  • - With a to the guide sleeve ( 26 ) angeord nete, from the pressure relief valve end region (bottom 19 ) to the collar ( 17 ) extending sleeve ( 27 ) with a pressure connection ( 11 ) corresponding opening ( 28 ) over a portion of the inner wall ( 29 ) with the outer circumference ( 30 ) of the guide bush ( 26 ) forms a ring cross section ( 31 ) acting as the further throttle point ( 15 ). ( Fig. 2)
5. Clamping device according to claim 4, characterized in that the sleeve ( 27 ) in the recess ( 16 ) of the machine part ( 12 ) between the collar ( 17 ) of the guide bush ( 26 ) and the locking screw ( 18 ) is arranged. ( Fig. 2)
6. Clamping device according to claim 4, characterized in that the sleeve with the Ver locking screw or the guide bush firmly connected that is.
DE19904035823 1990-11-10 1990-11-10 Hydraulic tensioner for chain drives - has pressure restrictor valve in bottom of tension piston guide Expired - Fee Related DE4035823C1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19904035823 DE4035823C1 (en) 1990-11-10 1990-11-10 Hydraulic tensioner for chain drives - has pressure restrictor valve in bottom of tension piston guide

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19904035823 DE4035823C1 (en) 1990-11-10 1990-11-10 Hydraulic tensioner for chain drives - has pressure restrictor valve in bottom of tension piston guide

Publications (1)

Publication Number Publication Date
DE4035823C1 true DE4035823C1 (en) 1991-12-19

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ID=6418021

Family Applications (1)

Application Number Title Priority Date Filing Date
DE19904035823 Expired - Fee Related DE4035823C1 (en) 1990-11-10 1990-11-10 Hydraulic tensioner for chain drives - has pressure restrictor valve in bottom of tension piston guide

Country Status (1)

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DE (1) DE4035823C1 (en)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0686787A1 (en) * 1994-06-06 1995-12-13 JOH. WINKLHOFER & SÖHNE GmbH & Co KG Hydraulic tensioning device for endless, flexible transmission elements
DE4443095A1 (en) * 1994-12-03 1996-06-13 Ford Werke Ag Chain tensioner / belt tensioner
DE19631607A1 (en) * 1996-08-05 1998-02-12 Schaeffler Waelzlager Kg Spring-loaded chain tensioning device
EP0908646A1 (en) * 1997-10-09 1999-04-14 Borg-Warner Automotive, Inc. Hydraulic chain tensioner with a deep drawn bore cup
DE19828534A1 (en) * 1998-06-26 1999-12-30 Schaeffler Waelzlager Ohg Hydraulically working support element with new design of securing device
EP1106789A2 (en) 1999-12-10 2001-06-13 Bayerische Motoren Werke Aktiengesellschaft Chain drive for a V-type engine with overhead camshafts
DE19929668C2 (en) * 1999-06-28 2002-07-11 Winklhofer & Soehne Gmbh Tensioning device for an endless drive element with variable damping behavior
DE10155370A1 (en) * 2001-11-10 2003-05-22 Bayerische Motoren Werke Ag Hydraulic tensioning device for combustion engine incorporates piston, pressurized oil chamber, return valve, leakage gaps, compression spring, displacer body and support flange
DE10155364A1 (en) * 2001-11-10 2003-05-22 Bayerische Motoren Werke Ag Hydraulic tensioner for chain or belt drives of internal combustion engines has tension piston and cylindrical insert between compression spring and chamber base as piston valve controlling outlet opening in piston wall
DE10155360A1 (en) * 2001-11-10 2003-05-22 Bayerische Motoren Werke Ag Hydraulic tensioning arrangement has pressurized oil chamber and holder, with return valve and compression spring, leakage gaps, extension, displacer and piston valve
US6811505B2 (en) * 2001-01-10 2004-11-02 Tsubakimoto Chain Co. Hydraulic tensioner
WO2006021271A1 (en) 2004-08-19 2006-03-02 Schaeffler Kg Hydraulic tensioning device for a traction mechanism drive
US7108621B2 (en) 2000-08-08 2006-09-19 INA Wälzlager Schaeffler oHG Chain tensioner
WO2007134652A1 (en) * 2006-05-24 2007-11-29 Iwis Motorsysteme Gmbh & Co. Kg Chain tensioner having a two-part screw-in housing
DE102006054744A1 (en) * 2006-11-21 2008-05-29 Schaeffler Kg Hydraulic traction mechanism with integrated clamping force limitation
EP1983218A2 (en) 2007-04-21 2008-10-22 Bayerische Motoren Werke Aktiengesellschaft Hydraulic tensioning device for a tractor transmission system
DE102008011787A1 (en) 2008-02-28 2009-09-03 Schaeffler Kg Valve cap for a check valve
EP2458246A1 (en) * 2010-11-29 2012-05-30 iwis motorsysteme GmbH & Co. KG Tensioning device with dampening unit comprising a minimum uptake volume

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3217632A1 (en) * 1982-05-11 1983-11-17 Porsche Ag Hydraulic chain tensioner
EP0330362A1 (en) * 1988-02-15 1989-08-30 Tsubakimoto Chain Co. Tensioner for toothed belts

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3217632A1 (en) * 1982-05-11 1983-11-17 Porsche Ag Hydraulic chain tensioner
EP0330362A1 (en) * 1988-02-15 1989-08-30 Tsubakimoto Chain Co. Tensioner for toothed belts

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0686787A1 (en) * 1994-06-06 1995-12-13 JOH. WINKLHOFER & SÖHNE GmbH & Co KG Hydraulic tensioning device for endless, flexible transmission elements
DE4443095A1 (en) * 1994-12-03 1996-06-13 Ford Werke Ag Chain tensioner / belt tensioner
DE19631607A1 (en) * 1996-08-05 1998-02-12 Schaeffler Waelzlager Kg Spring-loaded chain tensioning device
EP0908646A1 (en) * 1997-10-09 1999-04-14 Borg-Warner Automotive, Inc. Hydraulic chain tensioner with a deep drawn bore cup
US5967920A (en) * 1997-10-09 1999-10-19 Borg-Warner Automotive, Inc. Hydraulic tensioner with a bore cup
DE19828534A1 (en) * 1998-06-26 1999-12-30 Schaeffler Waelzlager Ohg Hydraulically working support element with new design of securing device
DE19929668C2 (en) * 1999-06-28 2002-07-11 Winklhofer & Soehne Gmbh Tensioning device for an endless drive element with variable damping behavior
EP1106789A2 (en) 1999-12-10 2001-06-13 Bayerische Motoren Werke Aktiengesellschaft Chain drive for a V-type engine with overhead camshafts
DE19959594C1 (en) * 1999-12-10 2001-06-21 Bayerische Motoren Werke Ag Chain drive of a V-engine with overhead camshafts
EP1106789A3 (en) * 1999-12-10 2002-12-18 Bayerische Motoren Werke Aktiengesellschaft Chain drive for a V-type engine with overhead camshafts
US7108621B2 (en) 2000-08-08 2006-09-19 INA Wälzlager Schaeffler oHG Chain tensioner
US6811505B2 (en) * 2001-01-10 2004-11-02 Tsubakimoto Chain Co. Hydraulic tensioner
DE10155364A1 (en) * 2001-11-10 2003-05-22 Bayerische Motoren Werke Ag Hydraulic tensioner for chain or belt drives of internal combustion engines has tension piston and cylindrical insert between compression spring and chamber base as piston valve controlling outlet opening in piston wall
DE10155370A1 (en) * 2001-11-10 2003-05-22 Bayerische Motoren Werke Ag Hydraulic tensioning device for combustion engine incorporates piston, pressurized oil chamber, return valve, leakage gaps, compression spring, displacer body and support flange
DE10155370B4 (en) * 2001-11-10 2013-10-17 Bayerische Motoren Werke Aktiengesellschaft Hydraulic tensioning device for a traction mechanism, in particular chain or belt drives of internal combustion engines
DE10155360A1 (en) * 2001-11-10 2003-05-22 Bayerische Motoren Werke Ag Hydraulic tensioning arrangement has pressurized oil chamber and holder, with return valve and compression spring, leakage gaps, extension, displacer and piston valve
WO2006021271A1 (en) 2004-08-19 2006-03-02 Schaeffler Kg Hydraulic tensioning device for a traction mechanism drive
WO2007134652A1 (en) * 2006-05-24 2007-11-29 Iwis Motorsysteme Gmbh & Co. Kg Chain tensioner having a two-part screw-in housing
DE102006054744A1 (en) * 2006-11-21 2008-05-29 Schaeffler Kg Hydraulic traction mechanism with integrated clamping force limitation
EP1983218A2 (en) 2007-04-21 2008-10-22 Bayerische Motoren Werke Aktiengesellschaft Hydraulic tensioning device for a tractor transmission system
DE102007018961A1 (en) 2007-04-21 2008-10-23 Bayerische Motoren Werke Aktiengesellschaft Hydraulic clamping device for a traction mechanism
DE102008011787A1 (en) 2008-02-28 2009-09-03 Schaeffler Kg Valve cap for a check valve
EP2458246A1 (en) * 2010-11-29 2012-05-30 iwis motorsysteme GmbH & Co. KG Tensioning device with dampening unit comprising a minimum uptake volume
US8814734B2 (en) 2010-11-29 2014-08-26 Iwis Motorsysteme Gmbh & Co., Kg Tensioning device with a damping means comprising a minimum capacity

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