WO2020032094A1 - Tendeur de chaîne - Google Patents

Tendeur de chaîne Download PDF

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Publication number
WO2020032094A1
WO2020032094A1 PCT/JP2019/031091 JP2019031091W WO2020032094A1 WO 2020032094 A1 WO2020032094 A1 WO 2020032094A1 JP 2019031091 W JP2019031091 W JP 2019031091W WO 2020032094 A1 WO2020032094 A1 WO 2020032094A1
Authority
WO
WIPO (PCT)
Prior art keywords
plunger
cylinder
pressure chamber
oil
leak
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.)
Ceased
Application number
PCT/JP2019/031091
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English (en)
Japanese (ja)
Inventor
唯久 田中
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.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
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 Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of WO2020032094A1 publication Critical patent/WO2020032094A1/fr
Anticipated expiration legal-status Critical
Ceased 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K15/00—Check valves
    • F16K15/02—Check valves with guided rigid valve members
    • F16K15/04—Check valves with guided rigid valve members shaped as balls

Definitions

  • the present invention relates to a chain tensioner mainly used for holding tension of a chain for driving a cam of an automobile engine or a chain for driving an oil pump.
  • chain transmission devices used in engines of automobiles for example, those that transmit the rotation of a crankshaft to a camshaft, those that transmit the rotation of a crankshaft to auxiliary equipment such as an oil pump, a water pump, and a supercharger,
  • auxiliary equipment such as an oil pump, a water pump, and a supercharger
  • a chain tensioner is used to keep the chain tension of these chain transmissions in an appropriate range.
  • a chain tensioner generates a hydraulic damper by supplying oil from an engine to keep the fluctuation of the chain tension constant.
  • a predetermined hydraulic damper may not be able to be generated after the engine is started until the pressure chamber inside the chain tensioner is filled with oil.
  • a chain tensioner 50 shown in FIG. 6 includes a cylindrical cylinder 9 having one end opened and another end closed, and a cylindrical plunger 10 supported on the inner periphery of the cylinder 9 so as to be slidable in the axial direction. And a return spring 33 for urging the plunger 10 in a direction to protrude from the cylinder 9 to one end, a reservoir chamber 27 formed inside the plunger 10, and formed at the other end of the plunger 10 in the cylinder 9.
  • a pressure chamber 18 whose volume changes with the axial movement of the plunger 10; and a check valve 20 provided at the insertion end of the plunger 10 into the cylinder 9 and which allows only the flow of oil from the reservoir chamber 27 to the pressure chamber 18.
  • the cylinder 9 has an oil supply passage 31 for introducing oil supplied by an engine oil pump or the like from the outside to the inside of the cylinder 9, and the end of the oil supply passage 31 inside the cylinder 9 is formed on the outer periphery of the plunger 10. And an oil supply space 28 formed between the cylinder and the inner periphery of the cylinder 9.
  • a leak gap 32 is formed between the outer circumference of the plunger 10 and the inner circumference of the cylinder 9.
  • the leak gap 32 is constituted by a minute gap, and extends from the pressure chamber 18 to the opening at one end of the cylinder 9 via the oil supply space 28. Further, the leak gap 32 and the oil supply space 28 communicate with the reservoir chamber 27 through the communication passage 30.
  • the tension of the chain causes the plunger 10 to move in a direction in which the plunger 10 is pushed into the other end of the cylinder 9 (hereinafter, referred to as a "pushing direction"), and absorbs the tension of the chain. I do.
  • the check valve 20 is closed by the increase in the pressure on the pressure chamber 18 side, and the oil flows out of the pressure chamber 18 to the oil supply space 28 through the leak gap 32. Since the damping force is generated by the viscous resistance of the oil passing through the leak gap 32, the plunger 10 moves slowly in the pushing direction.
  • part of the oil flows out of the chain tensioner 50 through the leak gap 32 on one end side of the oil supply space 28, and returns to the engine side.
  • the leak gap 32 is a minute gap and the resistance of the flow path is large, most of the oil is returned from the oil supply space 28 to the reservoir chamber 27 through the communication path 30.
  • the urging force of the return spring 33 causes the plunger 10 to move in a direction to protrude from the cylinder 9 to one end (hereinafter, referred to as a “protrusion direction”), and the chain becomes loose. Absorb.
  • the check valve 20 is opened and the oil flows from the reservoir chamber 27 into the pressure chamber 18, so that the plunger 10 moves quickly in the protruding direction.
  • an object to be solved by the present invention is to provide a chain tensioner capable of setting an appropriate damping force according to an operating condition.
  • the present invention provides a cylindrical cylinder having one end opened and the other end closed, and an axially slidably supported inner end of the cylinder, and an insertion end into the cylinder having an open end.
  • a cylindrical plunger whose protruding end from the cylinder is closed, a return spring for urging the plunger in a direction to protrude from the cylinder, and the cylinder so that the volume changes with the axial movement of the plunger.
  • a pressure chamber formed therein, a valve seat having a valve hole, a valve body for opening and closing the valve hole, and a check valve for allowing only oil flow from the inside of the plunger to the pressure chamber.
  • An oil supply passage for introducing oil from the outside to the inside of the cylinder, and a first gap formed between an inner periphery of the plunger and an outer periphery of the valve seat.
  • the first leak portion connects the pressure chamber and the inside of the plunger, and may have a configuration including a communication passage communicating the second leak portion with the inside of the plunger.
  • a configuration including a sub-check valve that opens and closes the first leak portion between the plunger and the valve seat can be adopted.
  • the sub-check valve opens and closes the first leak portion by relative movement of the plunger and the valve seat in the axial direction, and moves the valve seat to the first leak portion with respect to the plunger.
  • a configuration including a damper switching spring that urges the open side of the spring can be adopted.
  • the sub-check valve in response to the pressure in the pressure chamber, the sub-check valve is opened to allow oil to leak from the first leak portion, and a low damper region against the urging force of the damper switching spring. It is possible to adopt a configuration in which a spring operating area for moving the valve seat to one end side and a high damper area for closing the sub-check valve and leaking oil only from the second leak portion can be switched.
  • the present invention includes a plurality of systems of a first leak portion and a second leak portion as an oil flow passage for generating a tensioner reaction force. Can be used properly. For this reason, it is possible to provide a chain tensioner capable of setting an appropriate damping force.
  • FIG. 2 is a longitudinal sectional view showing a chain tensioner according to an embodiment of the present invention.
  • FIG. 4 is a graph schematically showing damper characteristics of the chain tensioner according to the embodiment of the present invention.
  • FIG. 1 shows a chain transmission device incorporating the chain tensioner 1 according to the embodiment of the present invention.
  • a sprocket 3 fixed to a crankshaft 2 of an engine and a sprocket 5 fixed to two camshafts 4 are connected via a chain 6, and the chain 6 is connected to a crankshaft. 2 is transmitted to the camshaft 4 and the rotation of the camshaft 4 opens and closes the valve of the combustion chamber.
  • the rotation direction of the crankshaft 2 when the engine is operating is constant (right rotation in FIG. 1), and at this time, the chain 6 is pulled into the sprocket 3 with the rotation of the crankshaft 2 (see FIG. 1).
  • the portion on the right side is the tension side, and the portion on the side sent out from the sprocket 3 (the left side in FIG. 1) is the slack side.
  • a chain guide 8 supported swingably around a fulcrum shaft 7 is in contact with the slack side portion of the chain 6.
  • the chain tensioner 1 presses the chain 6 via the chain guide 8.
  • the chain tensioner 1 is supported by a cylindrical cylinder 9 having one end opened and the other end closed, and slidably in the axial direction on the inner periphery of the cylinder 9. Plunger 10. A protruding end 17 of the plunger 10 protruding from one end of the cylinder 9 presses the chain guide 8.
  • the cylinder 9 is integrally formed of metal (for example, aluminum alloy).
  • the cylinder 9 is fixed to an engine wall surface such as a cylinder block by tightening bolts 12 inserted into holes 11 a (see FIG. 2A) of a plurality of mounting pieces 11 integrally formed on the outer periphery of the cylinder 9. .
  • the cylinder 9 is mounted on the engine wall so that the direction in which the plunger 10 projects from the cylinder 9 is obliquely downward.
  • the plunger 10 is formed in a tubular shape in which the other end inserted into the cylinder 9 is open, and the protruding end 17 from the one end of the cylinder 9 is closed.
  • the material of the plunger 10 is an iron-based material (for example, a steel material such as SCM (chrome molybdenum steel) or SCr (chrome steel)).
  • a pressure chamber 18 whose volume changes with the axial movement of the plunger 10.
  • the volume of the pressure chamber 18 increases when the plunger 10 moves in the protruding direction, and decreases when the plunger 10 moves in the pushing direction.
  • a check valve that allows only the flow of oil from the inside of the plunger 10 to the pressure chamber 18 side and restricts the flow of oil from the pressure chamber 18 to the inside of the plunger 10 at the insertion end of the plunger 10 into the cylinder 9. 20 are provided.
  • the check valve 20 includes a valve seat 21 provided at an insertion end of the plunger 10 into the cylinder 9, a valve hole 21 a provided in the valve seat 21, and a spherical opening and closing the valve hole 21 a from the pressure chamber 18 side.
  • a check ball (hereinafter, referred to as a check ball 25), which is a valve element 25, and a retainer 26 for restricting a moving range of the check ball 25.
  • the inside of the plunger 10 is a reservoir chamber 27 having a diameter larger than the diameter of the valve hole 21 a of the check valve 20.
  • the valve seat 21 of the check valve 20 is attached to the other end of the reservoir chamber 27.
  • the valve seat 21 has a columnar shape, and the valve hole 21a is formed so as to penetrate the axis of the valve seat 21 at one end and the other end.
  • a first leak portion 19 for leaking oil from inside the pressure chamber 18 to outside the pressure chamber 18 is provided between the inner periphery 41 of the plunger 10 and the outer periphery 21b of the valve seat 21, a first leak portion 19 for leaking oil from inside the pressure chamber 18 to outside the pressure chamber 18 is provided.
  • a second leak portion 29 is provided between the outer periphery 15 of the plunger 10 and the inner periphery 14 of the cylinder 9 to leak oil from inside the pressure chamber 18 to outside the pressure chamber 18.
  • the first leak portion 19 is constituted by a minute gap interposed between the outer periphery 21b of the valve seat 21 and the inner periphery 41 of the plunger 10, and this minute gap is referred to as a first gap w1 (see FIG. 4C).
  • the inner periphery 41 of the plunger 10 is a cylindrical surface
  • the outer periphery 21b of the valve seat 21 is also a cylindrical surface.
  • the size of the first gap w1 is set in the range of 0.005 to 0.100 mm as the radius difference between the inner circumference 41 of the plunger 10 and the outer circumference 21b of the valve seat 21.
  • a sub-check valve 42 is provided in the first leak portion 19.
  • the sub-check valve 42 is provided between the plunger 10 and the valve seat 21, and opens and closes the first leak portion 19 to leak oil through the first gap w ⁇ b> 1 and stop oil leak. You can switch to
  • the sub-check valve 42 has a structure that opens and closes the other end of the first gap w1 by relative movement of the plunger 10 and the valve seat 21 in the axial direction. Since the first leak portion 19 can be opened and closed by moving the valve seat 21 with respect to the plunger 10, the structure of the sub-check valve 42 can be simplified.
  • the valve seat 21c is provided at the other end of the valve seat 21 so as to protrude toward the outer diameter side.
  • the valve body portion 21c has a structure having an inclined surface approaching the outer diameter side from one end side to the other end side.
  • the inclined surface of the valve body portion 21c is an arc-shaped surface that is convex toward the outer diameter side in a vertical section passing through the axis.
  • a valve seat portion 44 is provided at the other end of the plunger 10 so that the valve body portion 21c can contact and separate therefrom.
  • the valve seat portion 44 has an inclined surface approaching the outer diameter side from one end to the other end.
  • the inclined surface of the valve seat portion 44 is linear in a vertical section passing through the axis.
  • a damper switching spring 23 is incorporated between the plunger 10 and the valve seat 21.
  • One end of the damper switching spring 23 is supported by the inner end surface 24 on the protruding end 17 side of the plunger 10, and the other end presses the valve seat 21, and the pressing causes the valve seat 21 to move toward the other end with respect to the plunger 10. That is, it is urged toward the open side of the first leak portion 19.
  • a movement restricting means 40 is incorporated between the plunger 10 and the valve seat 21, a movement restricting means 40 is incorporated.
  • the movement restricting means 40 restricts the relative movement of the valve seat 21 to the other end with respect to the plunger 10 at a predetermined position.
  • the movement restricting means 40 includes a concave groove 22 formed on the outer periphery on one end side of the valve seat 21, a retaining ring 43 housed in the concave groove 22, and a step formed on the plunger 10 and in which the retaining ring 43 contacts. A portion 41a.
  • the concave groove 22 has an inclined surface 22 a approaching the outer diameter side from the other end side to the one end side, and is smoothly connected to one end side of the inclined surface 22 a to the outer diameter side. It has a jaw portion 22b formed of a rising arc-shaped surface, and an end wall portion 22c provided on the other end side of the inclined surface 22a and rising to the outer diameter side. The end wall 22c and the inclined surface 22a are smoothly connected via an arc-shaped surface.
  • the stepped portion 41a is connected to the other end of the inner periphery 41 of the plunger 10 constituting the first leak portion 19, and has a configuration having an inclined surface approaching the outer diameter side toward one end.
  • a C-shaped circlip in which one portion in the circumferential direction of the annular member is open can be adopted.
  • the retaining ring 43 is housed in the groove 22 and the sub-check valve 42 is closed as shown in FIG. 4B, the retaining ring 43 is apart from the stepped portion 41a.
  • the retaining ring 43 is in contact with the jaw 22b of the concave groove 22, but the retaining ring 43 may be in a state of contacting the inclined surface 22a and the end wall 22c in the concave groove 22.
  • the second leak portion 29 is constituted by a minute gap interposed between the outer periphery 15 of the plunger 10 and the inner periphery 14 of the cylinder 9, and this minute gap is referred to as a second gap w2 (see FIG. 4C).
  • the outer periphery 15 of the largest diameter portion of the plunger 10 is a cylindrical surface
  • the inner periphery 14 of the cylinder 9 is also a cylindrical surface.
  • the second gap w2 is a radius difference between the outer circumference 15 of the plunger 10 and the inner circumference 14 of the cylinder 9, and is set in a range of 0.005 to 0.100 mm.
  • the size of the first gap w1 is set to be larger than that of the second gap w2.
  • an oil supply space 28 communicating with the second leak portion 29 is formed between the outer periphery of the plunger 10 and the inner periphery 14 of the cylinder 9.
  • the oil supply space 28 is formed annularly between the concave portion 16 formed on the entire outer periphery of the plunger 10 and the inner periphery 14 of the cylinder 9.
  • the concave portion 16 for forming the oil supply space 28 is provided at the axial center of the plunger 10, and the outer periphery of the largest diameter portion of the plunger 10 exists at one end and the other end with the concave portion 16 interposed therebetween. For this reason, the second leak portion 29 exists at one end side and the other end side with the concave portion 16 interposed therebetween, and communicates with the oil supply space 28, respectively.
  • a return spring 33 is incorporated in the pressure chamber 18. The other end of the return spring 33 is supported by the bottom 13 of the cylinder 9, and one end presses the plunger 10, and the pressing urges the plunger 10 in the direction in which the plunger 10 protrudes from the cylinder 9.
  • the plunger 10 is provided with a communication passage 30 that communicates between the oil supply space 28 and the reservoir chamber 27.
  • the communication passage 30 also communicates with the second leak portion 29 through the oil supply space 28.
  • the communication passage 30 is provided so as to be located on the upper half circumference of the plunger 10 with the mounting piece 11 of the cylinder 9 fixed to the engine wall surface. Specifically, the communication passage 30 is provided in an upper portion in the radial direction of the plunger 10 and within a range corresponding to a half of the outer peripheral dimension of the plunger 10. In particular, in this embodiment, the communication passage 30 is It is provided so as to be located on the top of the outer circumference of the ten. Therefore, when air exists inside the reservoir chamber 27, the air can be smoothly discharged from the communication passage 30.
  • the cylinder 9 is provided with an oil supply passage 31 for introducing oil from outside to inside of the cylinder 9.
  • the oil supply passage 31 is a through hole that penetrates the cylinder 9 in the radial direction.
  • An inlet 34 (see FIG. 2B) of the oil supply passage 31 is connected to an oil supply port on the engine wall side.
  • the outlet of the oil supply passage 31 opens to the cylindrical surface on the inner periphery of the cylinder 9 and faces the oil supply space 28. The oil supplied from the oil pump of the engine is introduced into the cylinder 9 from outside through the oil supply passage 31.
  • valve seat 21 is urged by the damper switching spring 23 in a direction to escape from the plunger 10 toward the pressure chamber 18. Further, the movement of the valve seat 21 toward the pressure chamber 18 is further restricted by the movement restricting means 40 with the sub-check valve 42 opened at a fixed opening.
  • the size of the first gap w1 of the first leak portion 19 is set to be larger than that of the second gap w2 of the second leak portion 29, most of the oil flowing out of the pressure chamber 18 is As shown by an arrow X in FIG. 4A, it returns to the reservoir chamber 27 through the first leak portion 19.
  • a damper region in which oil leaks through the first leak portion 19 is referred to as a low damper region A. Since the size of the first gap w1 of the first leak portion 19 is larger than the size of the second gap w2 of the second leak portion 29, a relatively low damping force can be exerted in the low damper region A.
  • FIG. 5 is a graph schematically showing the damper characteristics of the chain tensioner 1.
  • the low damper area A is located in the left area in the figure where the amplitude of the plunger 10 shown on the horizontal axis in the graph, that is, the amount of movement of the plunger 10 in the pushing direction is relatively small.
  • an arrow a in the figure as the amount of movement of the plunger 10 in the pushing direction toward the other end increases, the tensioner reaction force gradually increases.
  • a damper region in which the valve seat 21 moves to one end side against the urging force of the damper switching spring 23 is referred to as a spring operation region B.
  • the spring operation region B is located in a region where the amplitude of the plunger 10 is larger than the low damper region A.
  • the tensioner reaction force is constant.
  • the valve seat 21 moves to the reservoir chamber 27 side, and the sub-check valve 42 is closed. Thereby, the oil in the pressure chamber 18 thereafter flows out through the second leak portion 29 as shown by an arrow Y in FIG. 4B, and returns to the reservoir chamber 27 through the oil supply space 28 and the communication passage 30. .
  • the damper region in which oil leaks only from the second leak portion 29 is referred to as a high damper region C.
  • the high damper region C is located in the region on the right side in the figure where the amplitude of the plunger 10 is relatively large.
  • the tensioner reaction force gradually increases as the amplitude of the plunger 10 increases. Since the size of the second gap w2 of the second leak portion 29 is smaller than that of the first gap w1 of the first leak portion 19, a relatively high damping force can be exerted in the high damper region C.
  • an appropriate damping force can be set in accordance with an operation condition.
  • the chain tensioner 1 is possible.
  • the chain 6 is prevented from being over-tensioned by setting the low damper region A by the first leak portion 19, and is set by setting the high damper region C by the second leak portion 29 at engine startup.
  • a variable damper mechanism for preventing the plunger 10 from being excessively pushed in on the high damper region side can be provided.
  • the plunger 10 moves in the projecting direction by the urging force of the return spring 33, and absorbs the slack of the chain 6.
  • the pressure of the pressure chamber 18 becomes lower than the pressure of the reservoir chamber 27, and the check valve 20 opens.
  • the oil flows from the reservoir chamber 27 into the pressure chamber 18 through the valve hole 21a of the check valve 20, so that the plunger 10 moves quickly.
  • oil is introduced into the reservoir chamber 27 from the outside of the cylinder 9 through the oil supply passage 31, the oil supply space 28, and the communication passage 30 by the pressure of the oil pump. For this reason, the pressure in the reservoir chamber 27 does not easily drop, and the chain 6 is excellent in following up the slack.
  • the reservoir chamber 27 having a diameter larger than the diameter of the valve hole 21a of the check valve 20 is formed inside the plunger 10, the amount of oil stored in the plunger 10 is increased. Can be secured. For this reason, even when the oil is not supplied from the engine to the chain tensioner 1 immediately after the start of the engine, the damper force can be generated using the oil stored in the reservoir chamber 27.

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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)
  • Check Valves (AREA)

Abstract

L'invention concerne un tendeur de chaîne comprenant : un cylindre tubulaire (9), une extrémité dudit cylindre étant ouverte et l'autre extrémité étant fermée ; un piston plongeur tubulaire (10) ; un ressort de rappel (33) ; une chambre de pression (18) formée à l'intérieur du cylindre (9) de sorte que son volume varie conjointement avec le déplacement du piston plongeur (10) dans la direction axiale ; une soupape de retenue (20) dotée d'un corps de soupape (25) et d'un siège de soupape (21) comportant un trou (21a) de soupape ; un passage (31) d'alimentation en huile destiné à relier l'extérieur et l'intérieur du cylindre (9) ; une première section de fuite (19) formée entre la circonférence interne (41) du piston plongeur (10) et la circonférence externe (21b) du siège de soupape (21) et permettant les fuites d'huile à partir de la chambre de pression (18) ; et une seconde section de fuite (29) formée entre la circonférence externe (15) du piston plongeur (10) et la circonférence interne (14) du cylindre (9) et permettant les fuites d'huile à partir de la chambre de pression (18).
PCT/JP2019/031091 2018-08-10 2019-08-07 Tendeur de chaîne Ceased WO2020032094A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2018-151464 2018-08-10
JP2018151464A JP7178207B2 (ja) 2018-08-10 2018-08-10 チェーンテンショナ

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WO2020032094A1 true WO2020032094A1 (fr) 2020-02-13

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PCT/JP2019/031091 Ceased WO2020032094A1 (fr) 2018-08-10 2019-08-07 Tendeur de chaîne

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112709791A (zh) * 2020-12-04 2021-04-27 浙江吉利控股集团有限公司 用于汽车发动机的张紧器油压调节系统以及油压调节方法
US11242916B2 (en) * 2019-02-13 2022-02-08 Tsubakimoto Chain Co. Tensioner
CN115076312A (zh) * 2022-06-23 2022-09-20 杭州东华汽车动力科技有限公司 一种内循环结构的液压张紧器
CN118815968A (zh) * 2023-12-25 2024-10-22 比亚迪股份有限公司 单向阀、张紧装置、发动机、动力总成及车辆

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016089854A (ja) * 2014-10-29 2016-05-23 株式会社椿本チエイン テンショナ
JP2018040399A (ja) * 2016-09-06 2018-03-15 Ntn株式会社 油圧式オートテンショナ

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6307319B2 (ja) * 2014-03-24 2018-04-04 株式会社椿本チエイン チェーンテンショナ

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2016089854A (ja) * 2014-10-29 2016-05-23 株式会社椿本チエイン テンショナ
JP2018040399A (ja) * 2016-09-06 2018-03-15 Ntn株式会社 油圧式オートテンショナ

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11242916B2 (en) * 2019-02-13 2022-02-08 Tsubakimoto Chain Co. Tensioner
CN112709791A (zh) * 2020-12-04 2021-04-27 浙江吉利控股集团有限公司 用于汽车发动机的张紧器油压调节系统以及油压调节方法
CN115076312A (zh) * 2022-06-23 2022-09-20 杭州东华汽车动力科技有限公司 一种内循环结构的液压张紧器
CN118815968A (zh) * 2023-12-25 2024-10-22 比亚迪股份有限公司 单向阀、张紧装置、发动机、动力总成及车辆

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