WO2015019838A1 - 油圧式オートテンショナ - Google Patents

油圧式オートテンショナ Download PDF

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Publication number
WO2015019838A1
WO2015019838A1 PCT/JP2014/069307 JP2014069307W WO2015019838A1 WO 2015019838 A1 WO2015019838 A1 WO 2015019838A1 JP 2014069307 W JP2014069307 W JP 2014069307W WO 2015019838 A1 WO2015019838 A1 WO 2015019838A1
Authority
WO
WIPO (PCT)
Prior art keywords
leak
rod
pressure chamber
leak gap
check valve
Prior art date
Application number
PCT/JP2014/069307
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
洋生 森本
前野　栄二
Original Assignee
Ntn株式会社
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 Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2015019838A1 publication Critical patent/WO2015019838A1/ja

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    • 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
    • F16H7/1236—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 fluid and restriction type, e.g. dashpot
    • 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 
    • 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 
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0893—Circular path

Definitions

  • the present invention relates to a hydraulic auto tensioner used for adjusting the tension of a belt that drives an auxiliary machine such as an alternator, a water pump, and a compressor of an air conditioner.
  • an engine equipped with an ISG (Integrated Starter Generator) idle stop mechanism that stops the engine when the vehicle stops and starts the engine instantly when the vehicle starts when the accelerator pedal is depressed. Proposed.
  • ISG Integrated Starter Generator
  • FIG. 7 shows an engine belt transmission equipped with an ISG idle stop mechanism that achieves both engine auxiliary drive and engine start, and includes a crankshaft pulley P 1 attached to a crankshaft 51 and an ISG starter generator. 52 and the starter-generator pulley P 2 which is attached to the rotation shaft of, passing over the belt 54 between the accessory pulley P 3 attached to a rotating shaft of the auxiliary machine 53 such as a water pump, during normal operation of the engine, the as shown in FIG. (a), to drive the starter-generator 52 and the auxiliary 53 by rotation in the direction indicated by the arrow of the crankshaft pulley P 1, and so as to function the starter-generator 52 as a generator.
  • auxiliary machine 53 such as a water pump
  • the belt transmission device as described above, a tension pulley 55 provided on the crankshaft pulley P 1 and the starter generator belt portion 54a over the pulley P 2, the swingable pulley arm 56 for rotatably supporting the tension pulley 55
  • the adjustment force of the hydraulic auto tensioner A is applied to urge the pulley arm 56 in the direction in which the tension pulley 55 presses the belt 54, and the tension change of the belt 54 is absorbed by the hydraulic auto tensioner A.
  • a sealed reservoir chamber is provided between the inner periphery of the cylinder and the outer periphery of the valve sleeve, and the lower portion of the reservoir chamber and the lower portion of the pressure chamber communicate with each other through an oil passage formed in the bottom surface of the cylinder.
  • a check valve is installed in the lower end, and when the pushing force is applied to the rod and the pressure in the pressure chamber becomes higher than the pressure in the reservoir chamber, the check valve is closed to block the communication between the oil passage and the pressure chamber. ing.
  • the hydraulic auto tensioner configured as described above connects the connecting piece provided on the lower surface of the cylinder to the pulley arm 56 shown in FIG. 7A, and rotates the connecting piece provided on the upper surface of the spring seat to the engine block.
  • the check valve is closed and the oil sealed in the pressure chamber is removed from the sliding surface of the valve sleeve and the rod.
  • the fluid is caused to flow through a leak gap formed therebetween, and a hydraulic damper force is generated in the pressure chamber by the viscous resistance of the oil at the time of flow to buffer the pushing force.
  • the leak gap is set to a size that can absorb fluctuations in belt tension during normal operation of the engine, the leak gap is large, so that the rod is pushed in greatly when the engine is started by driving the starter generator 52, and the belt 54
  • the life of the belt may be shortened or the starter / generator 52 may fail to start the engine.
  • the leak gap is set to a size that can absorb fluctuations in the tension of the belt 54 when the engine is started by driving the starter / generator 52, the tension of the belt 54 during normal operation of the engine is reduced because the leak gap is small.
  • the belt 54 becomes excessively high and the belt 54 becomes over-tensioned, and the bearings that rotatably support the belt 54 and the pulleys P 1 to P 3 are easily damaged, resulting in a problem that fuel consumption increases.
  • An object of the present invention is to provide a hydraulic auto tensioner that can apply an appropriate tension to a belt during normal operation of an engine and when the engine is started by a starter generator.
  • a valve sleeve is projected from the bottom of a bottomed cylinder filled with oil, and the lower end of the rod is slidably inserted into the valve sleeve.
  • a pressure spring is provided in the valve sleeve, and a return spring that urges the cylinder and the rod in the extending direction is incorporated between a spring seat provided at the top of the rod and the bottom surface of the cylinder, and the inner circumference of the cylinder and the valve sleeve
  • a reservoir chamber is provided between the outer periphery of the cylinder, and an oil passage is formed in the bottom of the cylinder to connect the lower portion of the reservoir chamber and the lower portion of the pressure chamber.
  • the pressure in the pressure chamber is stored in the lower end of the valve sleeve.
  • a first check valve is provided that closes when the pressure in the chamber becomes higher and shuts off the communication between the pressure chamber and the oil passage. When the pushing force is applied to the rod, the first check valve is provided.
  • the leak flow path is composed of a first leak gap and a second leak gap having a larger flow path resistance than the first leak gap, and the rod is provided with a communication path that connects the first leak gap and the pressure chamber.
  • the communication path is configured to be openable and closable by a second check valve whose set pressure is higher than that of the first check valve.
  • a cylinder when adjusting the belt tension in the belt drive device for driving an auxiliary machine of an engine equipped with an ISG idle stop mechanism, a cylinder is connected to a tensioner mounting target such as an engine block, The spring seat at the tip of the rod is connected to a pulley arm that supports a tension pulley, and the tension pulley urges the pulley arm in a direction to press the belt portion between the crankshaft pulley and the motor / generator pulley, thereby tensioning the belt.
  • the belt tension increases rapidly and the pressure in the pressure chamber increases rapidly.
  • the first check valve is closed, and after the first check valve is closed, the second check valve closes the communication path to block the communication between the pressure chamber and the first leak clearance.
  • two annular leak gaps with different clearances are provided between the sliding surfaces of the rod and the valve sleeve so that the leak gap with a small clearance is located on the pressure chamber side, and the clearance is set in the axial direction.
  • a large leak gap may be used as the first leak gap, and a small leak gap may be used as the second leak gap.
  • the rod is provided with a communication path that communicates the first leak clearance and the pressure chamber, and the second check valve is incorporated in the communication path.
  • the rod is provided with a leak passage having an axial hole opening at its lower end surface and a radial hole opening at the outer diameter surface of the rod in communication with the upper end of the axial hole, and a pressure chamber.
  • a cylindrical core is incorporated in the axial hole portion of the leak passage in communication with the reservoir chamber, and the annular leak gap formed between the outer diameter surface of the core and the inner diameter surface of the axial hole portion is One leak gap may be used, and an annular leak gap formed between the sliding surfaces of the valve sleeve and the rod may be used as the second leak gap.
  • the lower part of the axial hole portion is used as a communication path, and the second check valve is incorporated in the communication path.
  • the rod is provided with a leak passage having an axial hole opening at its lower end surface and a radial hole opening at the outer diameter surface of the rod in communication with the upper end of the axial hole, and a pressure chamber.
  • a cylindrical core is incorporated into the axial hole portion of the leak passage in communication with the reservoir chamber, a spiral orifice formed on the outer diameter surface of the core is used as the first leak clearance, and the valve sleeve and rod
  • An annular leak gap formed between the sliding surfaces may be used as the second leak gap.
  • the lower part of the axial hole portion is used as a communication path, and the second check valve is incorporated in the communication path.
  • the leak flow path for leaking the oil in the pressure chamber to the reservoir chamber is formed up to the first and second leak clearances having different flow path resistances. Since one of the first leak gaps with a small flow path resistance is opened and closed by the pressure fluctuation of the pressure chamber and can be opened and closed by the second check valve whose set pressure is higher than that of the first check valve, Appropriate tension can be applied to the belt during operation and when the engine is started with the starter generator.
  • FIG. 1 is a longitudinal sectional view showing an embodiment of a hydraulic auto tensioner according to the present invention.
  • Sectional drawing which expands and shows the formation site of the 1st leak clearance of FIG. 1, and the 2nd leak clearance Sectional drawing which shows the state in which the oil in a pressure chamber has leaked from the 1st leak clearance Sectional drawing which shows the state in which the oil in a pressure chamber has leaked from the 2nd leak clearance Sectional drawing which shows other embodiment of the hydraulic auto tensioner which concerns on this invention
  • Partial sectional view showing still another embodiment of the hydraulic auto tensioner according to the present invention 1 shows a belt transmission device of an engine equipped with an idle stop mechanism, (a) is a front view showing a normal operation state of the engine, and (b) is a front view showing a start state of the engine by a starter generator.
  • the cylinder 1 has a bottom portion, and a connecting piece 2 connected to a pulley arm 56 shown in FIG. 7A is provided on the bottom surface of the bottom portion.
  • the connecting piece 2 is provided with a shaft insertion hole 2a penetrating from one side surface to the other side surface, and a cylindrical fulcrum shaft 2b and a sliding bearing 2c for rotatably supporting the fulcrum shaft 2b in the shaft insertion hole 2a.
  • the fulcrum shaft 2b is fixed by tightening a bolt that is inserted into the fulcrum shaft 2b and threadedly engaged with the pulley arm 56, and the connecting piece 2 is attached to the pulley arm 56 so as to be rotatable.
  • a sleeve fitting hole 3 is provided on the bottom surface of the cylinder 1, and a lower end portion of a steel valve sleeve 4 is press-fitted into the sleeve fitting hole 3.
  • the lower portion of the rod 5 is slidably inserted into the valve sleeve 4, and a pressure chamber 6 is provided in the valve sleeve 4 below the rod 5 by the insertion of the rod 5.
  • a spring seat 7 is fixed to an upper end portion of the rod 5 located outside the cylinder 1, and a return spring 8 incorporated between the spring seat 7 and the bottom surface of the cylinder 1 extends relative to the cylinder 1 and the rod 5. It is energizing in the direction to do.
  • a connecting piece 9 connected to the engine block is provided at the upper end of the spring seat 7.
  • the connecting piece 9 is formed with a sleeve insertion hole 9a penetrating from one side surface to the other side surface, and a sleeve 9b and a slide bearing 9c for rotatably supporting the sleeve 9b are incorporated in the sleeve insertion hole 9a.
  • the connecting piece 9 is rotatably connected to the engine block by a bolt inserted into the sleeve 9b.
  • the spring seat 7 is formed of a molded product, and a cylindrical dust cover 10 that covers the upper outer periphery of the cylinder 1 and a cylindrical spring cover 11 that covers the upper portion of the return spring 8 are molded at the same time to form the spring seat 7. Is integrated.
  • the spring seat 7 may be an aluminum die-cast molded product, or may be a molded product of a resin such as a thermosetting resin.
  • the entire outer periphery of the spring cover 11 is covered with a cylindrical body 12 that is insert-molded when the spring seat 7 is molded.
  • the cylinder 12 is made of a press-formed product of a steel plate.
  • An oil seal 13 as a seal member is incorporated in the upper opening of the cylinder 1, and the inner periphery of the oil seal 13 is in elastic contact with the outer peripheral surface of the cylinder 12 to close the upper opening of the cylinder 1. This prevents the oil filled inside the tank from leaking to the outside and prevents dust from entering the inside.
  • a sealed reservoir chamber 14 is formed between the cylinder 1 and the valve sleeve 4.
  • the reservoir chamber 14 and the pressure chamber 6 are an oil reservoir comprising an oil passage 15 formed between the fitting surfaces of the sleeve fitting hole 3 and the valve sleeve 4 and a circular recess formed at the center of the bottom surface of the sleeve fitting hole 3. 16 to communicate with each other.
  • a first check valve 17 is incorporated in the lower end portion of the valve sleeve 4.
  • the first check valve 17 is closed when the pressure in the pressure chamber 6 becomes higher than the pressure in the reservoir chamber 14, and the communication between the pressure chamber 6 and the oil passage 15 is cut off. It is prevented from flowing through the reservoir chamber 14.
  • two large-diameter portions 5a and 5b are provided at the lower end portion of the rod 5 positioned in the valve sleeve 4, and the outer diameter of the upper large-diameter portion 5a is lower.
  • the outer diameter of the large diameter portion 5b is smaller.
  • an annular leak gap 21 is formed between the outer diameter surface of the upper large diameter portion 5a and the inner diameter surface of the valve sleeve 4, and the leak gap 21 is the first leak gap.
  • an annular leak gap 22 is formed between the sliding surface of the lower large diameter portion 5b and the valve sleeve 4, and the leak gap 22 is a second leak gap.
  • the first leak clearance 21 and the second leak clearance 22 are different in the amount of clearance, so that the flow resistance of the first leak clearance 21 is smaller than the flow resistance of the second leak clearance 22.
  • Each of the first leak gap 21 and the second leak gap 22 causes a hydraulic damper action in the pressure chamber 6 due to viscous resistance when oil in the pressure chamber 6 leaks along the leak gaps 21 and 22. It is like that.
  • the first leak gap 21 is set to a size that can absorb the tension fluctuation of the belt 54 during the normal operation of the engine shown in FIG. 7A by a hydraulic damper action caused by oil leak.
  • the second leak gap 22 is set to such a size that the rod 5 is not pushed suddenly when the engine is started by driving the starter / generator 52 shown in FIG.
  • a communication passage 23 is formed which communicates the pressure chamber 6 and the first leak gap 21.
  • the communication path 23 includes an axial hole 23a that extends in the axial direction from the lower end surface of the rod 5, and a radial hole 23b that intersects the axial hole 23a and opens at the lower outer diameter surface of the upper large-diameter portion 5a.
  • the second check valve 25 is incorporated in the axial hole 23a.
  • the second check valve 25 has a check ball 26 that can be freely contacted and separated from a tapered seat surface 24 formed in the axial hole 23a, and directs the check ball 26 away from the seat surface 24.
  • a stopper ring 28 that presses the check ball 26 in an open state is press-fitted into the lower end portion of the axial hole 23a.
  • the second check valve 25 is configured such that when the pressure in the pressure chamber 6 becomes high, the check ball 26 comes into contact with the seat surface 24 to close the communication path 23 and block the communication between the pressure chamber 6 and the first leak gap 21. It has become.
  • the set pressure of the second check valve 25 is higher than the set pressure of the first check valve 17 and is activated when the pressure in the pressure chamber 6 further increases after the first check valve 17 is closed.
  • An annular groove 29 is formed at the upper end of the inner diameter surface of the valve sleeve 4, and a retaining ring 30 is incorporated in the annular groove 29.
  • the inner peripheral portion of the retaining ring 30 is positioned inward from the inner diameter surface of the valve sleeve 4, and the rod 5 comes out of the valve sleeve 4 by contact of the upper end surface of the upper large diameter portion 5 a with the inner peripheral portion of the retaining ring 30. Is prevented.
  • the hydraulic auto-tensioner shown in the embodiment has the above-described configuration, and when the engine equipped with the idle stop mechanism shown in FIG.
  • the connecting piece 2 provided on the connecting portion 2 is connected to the pulley arm 56, and the connecting piece 9 of the spring seat 7 is connected to the engine block to apply an adjusting force to the pulley arm 56.
  • check ball 26 of the second check valve 25 moves upward due to the pressure increase in the pressure chamber 6 after the first check valve 17 is completely closed, and separates from the stopper ring 28. It does not move up to the contact position and is kept open.
  • the first leak clearance 21 is set to a size that can absorb the tension fluctuation of the belt 54 during the normal operation of the engine, the tension of the belt 54 during the normal operation of the engine will not be too high. And is maintained at an appropriate tension.
  • the communication passage 23 is in a state of blocking the communication between the pressure chamber 6 and the first leak gap 21, so that the oil in the pressure chamber 6 is second as shown by the arrow in FIG. It flows from the leak gap 22 into the first leak gap 21 and leaks into the reservoir chamber 14.
  • FIG. 5 shows another embodiment of the hydraulic auto tensioner according to the present invention.
  • the rod 5 is provided with a leak passage 31 that allows the pressure chamber 6 and the reservoir chamber 14 to communicate with each other.
  • the leak passage 31 includes an axial hole portion 32 formed of a stepped hole and an axial hole portion 32 thereof.
  • the cylindrical core 34 is incorporated in the intermediate hole 32 a of the axial hole 32, and communicates with the upper end of the rod 5.
  • An annular leak gap 21 formed between the radial face and the inner face of the intermediate hole portion 32a is defined as a first leak gap.
  • the second check valve 25 is incorporated in the lower large-diameter hole portion 32b as the communication passage of the axial hole portion 32, and the second check valve 25 is formed in a cylindrical shape with a valve hole 36 formed on the shaft center.
  • a check ball 38 which is provided so as to be in contact with and away from the tapered seat surface 37 formed at the lower end of the valve hole 36, and the check ball 38 in a direction away from the seat surface 37.
  • the check ball 38 is held in an open state by a cap-like retainer 40 having a communication hole 41 press-fitted into the lower large-diameter hole portion 32b of the rod 5.
  • the rod 5 is formed into a cylindrical shape having the same outer diameter over the entire length in the axial direction, and the cylindrical rod 5 is slidably inserted into a small diameter hole portion 4a formed at the inner peripheral upper end portion of the valve sleeve 4, An annular leak gap 22 formed between the sliding surfaces is defined as a second leak gap.
  • annular groove 42 is provided on the outer periphery of the lower end portion of the rod 5, a retaining ring 43 is attached to the annular groove 42, and the rod 5 is prevented from being pulled out by contact of the retaining ring 43 with the lower end surface of the small diameter hole portion 4a. ing.
  • the second check valve 25 is closed by a large pushing force applied to the rod 5 from the belt 54, so that the oil in the pressure chamber 6 is closed. Is leaked from the second leak gap 22 having a large flow path resistance to the reservoir chamber 14, the viscosity resistance of the oil flowing through the second leak gap 22 is suppressed, and a sudden pressure drop in the pressure chamber 6 is suppressed, and the rod 5 is pushed in greatly.
  • the belt 54 is held at the belt tension necessary to drive the crankshaft 51.
  • the annular leak gap 21 formed between the outer diameter surface of the core 34 and the inner diameter surface of the intermediate hole portion 32 a is used as the first leak gap.
  • a spiral orifice 21 may be formed on the surface, and the orifice 21 may be used as the first leak clearance.

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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)
PCT/JP2014/069307 2013-08-07 2014-07-22 油圧式オートテンショナ WO2015019838A1 (ja)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013-163921 2013-08-07
JP2013163921A JP6257950B2 (ja) 2013-08-07 2013-08-07 油圧式オートテンショナ

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WO2015019838A1 true WO2015019838A1 (ja) 2015-02-12

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PCT/JP2014/069307 WO2015019838A1 (ja) 2013-08-07 2014-07-22 油圧式オートテンショナ

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JP (1) JP6257950B2 (enrdf_load_stackoverflow)
WO (1) WO2015019838A1 (enrdf_load_stackoverflow)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014223229A1 (de) * 2014-11-13 2016-05-19 Schaeffler Technologies AG & Co. KG Hydraulischer Riemenspanner

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6463998B2 (ja) * 2015-03-11 2019-02-06 Ntn株式会社 油圧式オートテンショナ
JP6513523B2 (ja) * 2015-07-28 2019-05-15 Ntn株式会社 油圧式オートテンショナ
JP6599165B2 (ja) * 2015-08-11 2019-10-30 Ｎｔｎ株式会社 油圧式オートテンショナ

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11201245A (ja) * 1998-01-12 1999-07-27 Ntn Corp チェーンテンショナ
JP2002054701A (ja) * 2000-08-09 2002-02-20 Ntn Corp 油圧式チェーンテンショナ
JP2009264419A (ja) * 2008-04-22 2009-11-12 Ntn Corp 油圧式オートテンショナ
DE102010034290A1 (de) * 2010-08-13 2012-02-16 Schaeffler Technologies Gmbh & Co. Kg Druckbegrenztes hydraulisch gedämpftes Spannsystem

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH11201245A (ja) * 1998-01-12 1999-07-27 Ntn Corp チェーンテンショナ
JP2002054701A (ja) * 2000-08-09 2002-02-20 Ntn Corp 油圧式チェーンテンショナ
JP2009264419A (ja) * 2008-04-22 2009-11-12 Ntn Corp 油圧式オートテンショナ
DE102010034290A1 (de) * 2010-08-13 2012-02-16 Schaeffler Technologies Gmbh & Co. Kg Druckbegrenztes hydraulisch gedämpftes Spannsystem

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014223229A1 (de) * 2014-11-13 2016-05-19 Schaeffler Technologies AG & Co. KG Hydraulischer Riemenspanner
DE102014223229B4 (de) * 2014-11-13 2016-07-21 Schaeffler Technologies AG & Co. KG Hydraulischer Riemenspanner

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JP2015031392A (ja) 2015-02-16

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