WO2022191195A1 - Tendeur de chaîne - Google Patents

Tendeur de chaîne Download PDF

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Publication number
WO2022191195A1
WO2022191195A1 PCT/JP2022/010039 JP2022010039W WO2022191195A1 WO 2022191195 A1 WO2022191195 A1 WO 2022191195A1 JP 2022010039 W JP2022010039 W JP 2022010039W WO 2022191195 A1 WO2022191195 A1 WO 2022191195A1
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WO
WIPO (PCT)
Prior art keywords
sleeve
plunger
cylinder
pressure chamber
relief
Prior art date
Application number
PCT/JP2022/010039
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English (en)
Japanese (ja)
Inventor
好一 鬼丸
Original Assignee
Ntn株式会社
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Filing date
Publication date
Application filed by Ntn株式会社 filed Critical Ntn株式会社
Publication of WO2022191195A1 publication Critical patent/WO2022191195A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B67/00—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for
    • F02B67/04—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus
    • F02B67/06—Engines characterised by the arrangement of auxiliary apparatus not being otherwise provided for, e.g. the apparatus having different functions; Driving auxiliary apparatus from engines, not otherwise provided for of mechanically-driven auxiliary apparatus driven by means of chains, belts, or like endless members
    • 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

Definitions

  • the present invention relates to a chain tensioner used to hold the tension of the chain.
  • chain transmission devices used in automobile engines for example, those that transmit the rotation of the crankshaft to the camshaft, those that transmit the rotation of the crankshaft to auxiliary equipment such as oil pumps, water pumps, superchargers, etc. , to transmit the rotation of the crankshaft to the balancer shaft, and to connect the intake and exhaust cams of a twin-cam engine.
  • a chain tensioner is used to keep the tension of the chain in these chain drives in the proper range.
  • the chain tensioner of Patent Document 1 has a cylinder, a tubular plunger inserted into the cylinder so as to be slidable in the axial direction, and a sleeve inserted into the plunger.
  • a cylinder is a tubular member having one end in the axial direction as a closed end and the other end in the axial direction as an open end.
  • the plunger is a tubular member having an open end for insertion into the cylinder and a closed end for protruding from the cylinder.
  • the sleeve is inserted into the plunger so that one end in the axial direction is inserted into the plunger and the other end in the axial direction projects from the plunger, and the end of the sleeve protruding from the plunger serves as the closed end of the cylinder.
  • the outer circumference of the sleeve and the inner circumference of the plunger are axially slidably fitted together.
  • a return spring is installed between the insertion end of the sleeve into the plunger and the plunger to bias the plunger in the direction of protruding from the cylinder.
  • the chain tensioner of Patent Document 1 has a check valve at the insertion end of the sleeve into the plunger.
  • the check valve divides the internal region of the sleeve and plunger into a reservoir chamber on the sleeve side and a pressure chamber on the plunger side.
  • the check valve is a valve that allows oil to flow only from the reservoir chamber side to the pressure chamber side.
  • the cylinder is formed with an oil supply passage for introducing oil supplied from the outside of the cylinder into the reservoir chamber.
  • a cylindrical leak gap is formed between the outer circumference of the sleeve and the inner circumference of the plunger to allow oil to leak from the pressure chamber.
  • the check valve has a valve seat in which a valve hole communicating between the pressure chamber and the reservoir chamber is formed, and a valve body that opens and closes the end of the valve hole on the side of the pressure chamber.
  • the valve seat is seamlessly formed integrally with the sleeve at the end of the sleeve that is inserted into the plunger.
  • the urging force of the return spring and the hydraulic pressure in the pressure chamber move the plunger in the direction in which it protrudes from the cylinder (hereinafter referred to as the "protrusion direction"), thereby removing slack in the chain. Absorb.
  • the check valve opens and oil flows into the pressure chamber from the reservoir chamber, so the plunger moves quickly.
  • the chain tensioner of Patent Document 1 has a problem that the damping force changes greatly according to the temperature change. That is, in the chain tensioner of Patent Document 1, when the plunger moves in the pushing direction, the oil in the pressure chamber flows through the leak gap into the reservoir chamber. do. Here, since the viscosity of the oil increases as the temperature of the oil decreases, the viscous resistance of the oil flowing through the leak gap increases when the temperature of the oil is low, and the damping force increases. On the other hand, when the temperature of the oil is high, the viscous resistance of the oil flowing through the leak gap becomes low, and the damping force becomes small.
  • the size of the leak gap is set large, it is possible to prevent the damping force from becoming excessive at low temperatures, but there is a risk that the damping force at high temperatures will be too small, causing the chain to rattle.
  • the size of the leak gap is set small, it is possible to prevent the damping force from becoming too small at high temperatures, but there is a risk that the damping force at low temperatures will be excessive and the chain tension will be excessive. be.
  • the inventors of the present application proposed that the chain tensioner disclosed in Patent Document 1 be designed so that oil is supplied from the pressure chamber when the pressure in the pressure chamber exceeds a preset pressure.
  • a relief valve to let the air escape. If a relief valve is provided, the pressure rise in the pressure chamber can be suppressed by opening the relief valve at low temperatures, preventing the damper force from becoming excessive. It is possible to secure the magnitude of the damping force due to the viscous resistance of the chain and prevent the chain from fluttering.
  • the inventor of the present application considered providing the relief valve at the position of the check valve at the insertion end of the sleeve into the plunger. In this way, when the relief valve is opened, the oil that flows out from the pressure chamber through the relief valve can be collected in the reservoir chamber, so it is possible to reduce the amount of oil consumed by the chain tensioner. .
  • the inventors of the present application proposed a method for assembling a relief valve at the position of the check valve at the insertion end of the sleeve into the plunger. A method of press-fitting was investigated.
  • the problem to be solved by the present invention is to provide a chain tensioner capable of obtaining a damping force of stable magnitude.
  • the inventors of the present application have proposed that members corresponding to the sleeves of the chain tensioner disclosed in Patent Document 1 are divided into a first sleeve for forming a reservoir chamber and a second sleeve for forming a leak gap.
  • the inventors have come up with the idea of dividing the valve into two parts, incorporating the check valve into the second sleeve, and directly forming the seat surface of the relief valve on the second sleeve.
  • the present invention provides a chain tensioner having the following configuration. a cylinder having one end in the axial direction as a closed end and the other end in the axial direction as an open end; a cylindrical plunger that is axially slidably inserted into the cylinder, has an open end for insertion into the cylinder, and a closed end that protrudes from the cylinder; One end in the axial direction is inserted into the plunger, the other end in the axial direction is inserted into the plunger so as to protrude from the plunger, and the protruding end from the plunger is supported by the closed end of the cylinder.
  • first sleeve a first sleeve
  • second sleeve provided in connection with the insertion end of the first sleeve into the plunger and separate from the first sleeve
  • the inner region of the first sleeve and the plunger is incorporated into the second sleeve so as to partition the inner region into a reservoir chamber on the first sleeve side and a pressure chamber on the plunger side.
  • the check valve has a seat member in which a valve hole communicating between the pressure chamber and the reservoir chamber is formed, and a valve body that opens and closes an end portion of the valve hole on the side of the pressure chamber,
  • the sheet member is provided axially movably with respect to the second sleeve,
  • the first sleeve incorporates a relief spring that axially presses the sheet member from the reservoir chamber side toward the pressure chamber side,
  • the second sleeve is formed with an annular relief sheet
  • the relief seat surface of the relief valve is formed on the second sleeve which is separate from the first sleeve, the constituent members of the relief valve can be assembled while the first sleeve and the second sleeve are separated, It is possible to secure the assembling workability of the relief valve.
  • the fitting cylindrical surface that is axially slidably fitted to the inner periphery of the plunger is formed directly on the outer periphery of the second sleeve having the relief seat surface, the member having the relief seat surface is press-fitted. It is possible to prevent the dimension of the fitting cylindrical surface from changing due to such factors as the above, and it is possible to control the dimension of the fitting cylindrical surface with high accuracy and constant. Therefore, the size of the leakage gap between the fitting cylindrical surface and the inner circumference of the plunger can be controlled with high dimensional accuracy, and a stable damping force can be obtained.
  • the first sleeve is formed with an oil passage for returning oil leaked from the pressure chamber through the leak gap to the reservoir chamber.
  • the outer circumference of the portion of the first sleeve inserted into the plunger is preferably formed to have a smaller diameter than the fitting cylindrical surface.
  • the gap between the outer circumference of the first sleeve and the inner circumference of the plunger becomes relatively large, and the viscous resistance of the oil flowing through the gap can be kept small.
  • the magnitude of the damping force is less likely to change, and a stable damping force can be obtained.
  • the contact surface of the sheet member with the relief sheet surface or the relief sheet surface is provided with an air release groove for releasing air in the second sleeve to the reservoir chamber while the sheet member is in contact with the relief sheet surface. preferably formed.
  • an air valve for discharging air in the second sleeve to the valve hole in a state where the valve body closes the end of the valve hole on the side of the pressure chamber is provided on the contact surface of the seat member with the valve body. It is preferable to form a draft groove.
  • the air existing in the second sleeve is discharged to the reservoir chamber through the air release groove and the valve hole in order, so that a more stable damping force can be obtained.
  • the second sleeve can be slidably supported at an insertion end of the first sleeve into the plunger so as to allow radial movement of the second sleeve relative to the first sleeve.
  • An annular projection is formed at the end of the first sleeve inserted into the plunger,
  • a configuration may be adopted in which the second sleeve is formed with an annular recess that fits into the annular protrusion to radially position the second sleeve with respect to the first sleeve.
  • the protruding end of the first sleeve from the plunger has an annular partial spherical surface supported in axial contact with the closed end of the cylinder, It is preferable that the closed end of the cylinder has a concave tapered surface or a concave spherical surface that slidably supports the partial spherical surface so as to allow tilting of the first sleeve.
  • the first sleeve tilts with respect to the cylinder in accordance with the misalignment. 2
  • the size of the leakage gap between the fitting cylindrical surface of the outer circumference of the sleeve and the inner circumference of the plunger is made uniform in the axial direction. Therefore, it is possible to obtain a stable damper force.
  • the second sleeve is pressed against the first sleeve by the reaction force of the force of the return spring that urges the plunger, thereby preventing the separation of the first and second sleeves due to vibrations of the engine or the like. can be done.
  • the relief seat surface of the relief valve is formed on the second sleeve, which is separate from the first sleeve. can be assembled, and it is possible to secure the assembling workability of the relief valve.
  • the fitting cylindrical surface that is axially slidably fitted to the inner periphery of the plunger is formed directly on the outer periphery of the second sleeve having the relief seat surface, the member having the relief seat surface is press-fitted. It is possible to prevent the dimension of the fitting cylindrical surface from changing due to such factors as the above, and it is possible to control the dimension of the fitting cylindrical surface with high accuracy and constant. Therefore, the size of the leakage gap between the fitting cylindrical surface and the inner circumference of the plunger can be controlled with high dimensional accuracy, and a stable damping force can be obtained.
  • FIG. 1 is a diagram showing a chain transmission incorporating a chain tensioner according to a first embodiment of the present invention
  • FIG. 3 is an enlarged cross-sectional view of the vicinity of the sheet member in FIG. 2
  • FIG. 4 is an enlarged cross-sectional view of the vicinity of the seat member showing the state in which the relief valve of FIG. 3 is opened
  • FIG. 6 4 is a perspective view of a seat member showing a modification in which air vent grooves are formed in the contact surface of the seat member in FIG. 3 with the relief sheet surface;
  • FIG. FIG. 9 is an enlarged cross-sectional view of the vicinity of the seat member of the chain tensioner incorporating the seat member shown in FIG. 8 ;
  • FIG. 4 is an enlarged cross-sectional view of the vicinity of the seat member in FIG. 3, showing a modification in which an air vent groove is formed on the contact surface of the seat member with the valve body;
  • Enlargement of the vicinity of the seat member showing a modified example in which an air release groove is formed on the contact surface of the seat member with the relief seat surface of FIG. 3 and an air release groove is also formed on the contact surface of the seat member with the valve body cross section FIG.
  • FIG. 2 is a cross-sectional view of a main part showing a chain tensioner according to a second embodiment of the invention
  • FIG. 12 is an enlarged cross-sectional view of the vicinity of the second sleeve in FIG. 12
  • FIG. 13 is an enlarged cross-sectional view of the vicinity of the projecting end from the plunger of the first sleeve in FIG. 12;
  • Fig. 1 shows a chain transmission incorporating a chain tensioner 1 of the first embodiment of the invention.
  • a sprocket 3 fixed to a crankshaft 2 of an engine and a sprocket 5 fixed to a camshaft 4 are connected via a chain 6, and the chain 6 drives the rotation of the crankshaft 2. It is transmitted to the camshaft 4, and the rotation of the camshaft 4 opens and closes a valve (not shown) of the combustion chamber.
  • the chain tensioner 1 includes a tubular cylinder 9 having one end in the axial direction closed and the other end in the axial direction open, and is axially slidably inserted into the cylinder 9. and a plunger 10. A projecting end of the plunger 10 from the cylinder 9 presses the chain guide 8 .
  • the cylinder 9 is integrally formed of an aluminum alloy.
  • the cylinder 9 is fixed to an engine block (not shown) by fastening bolts 12 to a plurality of mounting pieces 11 integrally formed on the outer circumference of the cylinder 9 .
  • the cylinder 9 is attached so that the direction in which the plunger 10 protrudes from the cylinder 9 is inclined downward from the horizontal.
  • the plunger 10 is formed in a tubular shape with an open end inserted into the cylinder 9 of the plunger 10 and a closed end protruding from the cylinder 9 of the plunger 10 .
  • the material of the plunger 10 is a ferrous material (for example, a steel material such as SCM (chromium molybdenum steel) or SCr (chromium steel)).
  • a first sleeve 13 is inserted into the plunger 10 so that one end in the axial direction is inserted into the plunger 10 and the other end in the axial direction protrudes from the plunger 10 .
  • the first sleeve 13 is a cylindrical member with both ends in the axial direction open.
  • the first sleeve 13, like the plunger 10, is made of a ferrous material. A protruding end of the first sleeve 13 from the plunger 10 is supported by the closed end of the cylinder 9 .
  • a second sleeve 14 that is separate from the first sleeve 13 is connected to the insertion end of the first sleeve 13 into the plunger 10 .
  • the second sleeve 14 is a cylindrical member that is arranged in line with the first sleeve 13 in the axial direction.
  • the axial length of the second sleeve 14 is shorter than the axial length of the first sleeve 13 , and can be set to, for example, 1 ⁇ 3 or less of the axial length of the first sleeve 13 .
  • the second sleeve 14, like the plunger 10, is made of a ferrous material.
  • a check valve 15 is incorporated in the second sleeve 14 .
  • the check valve 15 divides the internal region of the first sleeve 13 and the plunger 10 into a reservoir chamber 16 on the first sleeve 13 side and a pressure chamber 17 on the plunger 10 side.
  • the volume of the reservoir chamber 16 is constant and does not change even when the plunger 10 moves in the axial direction.
  • the volume of the pressure chamber 17 expands when the plunger 10 axially moves in the direction of protruding from the cylinder 9 and contracts when the plunger 10 axially moves in the direction of being pushed into the cylinder 9 .
  • a return spring 18 is incorporated in the pressure chamber 17 .
  • the return spring 18 is a compression coil spring formed by spirally winding a metal wire.
  • One end of the return spring 18 is supported by the second sleeve 14 , and the other end presses the plunger 10 in the axial direction.
  • the check valve 15 has a seat member 21 in which a valve hole 20 is formed, and a spherical valve body 22 that opens and closes the end of the valve hole 20 on the pressure chamber 17 side.
  • the valve hole 20 is an axial through hole formed in the seat member 21 so as to communicate between the pressure chamber 17 and the reservoir chamber 16 .
  • the valve body 22 is a steel ball.
  • the axial movement range of the valve body 22 is limited by an end plate 23 formed on the second sleeve 14 .
  • a plurality of through holes 24 are formed in the end plate 23 so that oil can pass through the end plate 23 .
  • the check valve 15 restricts the flow of oil from the pressure chamber 17 side to the reservoir chamber 16 side and allows oil to flow only from the reservoir chamber 16 side to the pressure chamber 17 side.
  • the outer periphery of the second sleeve 14 is formed with a fitting cylindrical surface 25 that is axially slidably fitted to the inner periphery of the plunger 10 .
  • the fitting cylindrical surface 25 is a cylindrical surface whose outer diameter does not change along the axial direction.
  • the inner circumference of the plunger 10 is also a constant cylindrical surface whose inner diameter does not change along the axial direction.
  • a leak gap 26 is formed between the fitting cylindrical surface 25 and the inner circumference of the plunger 10 to allow oil to leak from the pressure chamber 17 when the volume of the pressure chamber 17 is reduced.
  • the leak gap 26 is a cylindrical minute gap with a radial width set in the range of 0.010 to 0.050 mm.
  • the outer circumference of the portion of the first sleeve 13 inserted into the plunger 10 is a cylindrical surface with a constant outer diameter that does not change along the axial direction. It is formed to have a smaller diameter than the fitting cylindrical surface 25 on the outer periphery of the. Further, the outer circumference of the portion where the plunger 10 is inserted into the cylinder 9 is also a constant cylindrical surface whose outer diameter does not change along the axial direction. A portion of the inner circumference of the cylinder 9 that axially slidably supports the outer circumference of the plunger 10 is also a cylindrical surface whose inner diameter does not change along the axial direction.
  • a cylindrical guide gap 27 is formed between the inner circumference of the cylinder 9 and the outer circumference of the plunger 10 .
  • the radial width of the guide gap 27 is set larger than the radial width of the leak gap 26, and can be set in the range of 0.015 to 0.065 mm, for example.
  • the cylinder 9 and the first sleeve 13 are provided with an oil supply passage 30 for introducing oil supplied from an oil pump (not shown) outside the cylinder 9 into the reservoir chamber 16 .
  • the oil supply passage 30 is formed between a cylinder-side oil passage 31 formed in the cylinder 9 so as to introduce oil from the outer circumference to the inner circumference of the cylinder 9 and between the inner circumference of the cylinder 9 and the outer circumference of the first sleeve 13 . and an oil passage 33 provided in a projecting portion of the first sleeve 13 from the plunger 10 .
  • the cylindrical space 32 is radially sandwiched between the inner periphery of the cylinder 9 and the outer periphery of the first sleeve 13 on the side closer to the closed end of the cylinder 9 than the insertion end of the plunger 10 into the cylinder 9 . area.
  • An end portion of the cylinder-side oil passage 31 on the inner peripheral side of the cylinder 9 opens at a position connected to the cylindrical space 32 .
  • the oil passage 33 is a through hole formed through the first sleeve 13 in the radial direction.
  • the oil passage 33 is also a part of the oil supply passage 30, and is an oil recovery hole for returning the oil that has leaked from the pressure chamber 17 to the tubular space 32 through the leak gap 26 from the tubular space 32 to the reservoir chamber 16. But also.
  • the seat member 21 of the check valve 15 is a member formed separately from the second sleeve 14 and is provided axially movably with respect to the second sleeve 14 .
  • the first sleeve 13 incorporates a relief spring 34 that axially presses the sheet member 21 from the reservoir chamber 16 side toward the pressure chamber 17 side.
  • the relief spring 34 is a compression coil spring formed by spirally winding a metal wire.
  • One end of the relief spring 34 is supported by a stepped portion 35 (see FIG. 2) formed on the inner circumference of the first sleeve 13, and the other end of the relief spring 34 presses the seat member 21 in the axial direction.
  • the seat member 21 is pressed against the relief seat surface 36 formed on the second sleeve 14 by the pressing force of the relief spring 34 .
  • the relief seat surface 36 is an annular surface having a convex arcuate cross section that contacts and supports the seat member 21 from the pressure chamber 17 side (right side in the figure).
  • a contact surface 37 of the sheet member 21 with the relief sheet surface 36 is a tapered surface that makes line contact with the relief sheet surface 36 at an annular portion.
  • the seat member 21, the relief spring 34, and the relief seat surface 36 constitute a relief valve 38 that releases oil from the pressure chamber 17 to the reservoir chamber 16 when the pressure in the pressure chamber 17 exceeds a preset pressure. is doing. That is, when the pressure in the pressure chamber 17 becomes higher than the preset pressure, the pressure in the pressure chamber 17 causes the seat member 21 to move against the biasing force of the relief spring 34 as shown in FIG. side (right side in the figure) toward the reservoir chamber 16 side (left side in the figure) and separates from the relief sheet surface 36 . Then, the oil in the pressure chamber 17 escapes to the reservoir chamber 16 through the gap between the sheet member 21 and the relief sheet surface 36, and the pressure rise in the pressure chamber 17 is suppressed.
  • the second sleeve 14 is slidably supported at the insertion end of the first sleeve 13 into the plunger 10 to allow radial movement of the second sleeve 14 relative to the first sleeve 13 .
  • a flat surface 39 perpendicular to the axial direction is formed at the insertion end of the first sleeve 13 into the plunger 10, and the axial end surface 40 of the second sleeve 14 abuts on the flat surface 39 in the axial direction. 39 and the axial end surface 40 are in contact with each other so as to be slidable in the radial direction.
  • the viscosity of the oil increases as the temperature of the oil decreases.
  • the leak gap 26 since each member contracts at low temperatures, the leak gap 26 also becomes smaller. Therefore, when the temperature is low, the viscosity resistance of the oil flowing through the leak gap 26 increases, and the pressure in the pressure chamber 17 tends to increase.
  • the pressure in the pressure chamber 17 becomes greater than the preset pressure, the pressure in the pressure chamber 17 causes the sheet member 21 to move away from the relief sheet surface 36 (see FIG. 4).
  • the oil in the pressure chamber 17 is released to the reservoir chamber 16 through the gap between . Therefore, an increase in pressure in the pressure chamber 17 is suppressed, and an excessive damping force can be prevented.
  • the oil level in the oil passage (not shown) outside the cylinder 9 is once lowered. It takes time before the oil supply to the tensioner 1 starts. In this case, from the time the engine is restarted until the oil supply is started, as shown in FIG. Thus, the pressure chamber 17 is kept filled with oil. Therefore, it is possible to generate a damping force immediately after the engine is restarted, and it is possible to suppress the chain 6 from fluttering.
  • the chain tensioner 1 is formed with the fitting cylindrical surface 25 that fits directly on the outer periphery of the second sleeve 14 having the relief seat surface 36 and on the inner periphery of the plunger 10 so as to be slidable in the axial direction. Also, it is possible to prevent the dimension of the fitting cylindrical surface 25 from being changed due to press-fitting of the member forming the relief seat surface 36, etc., and the dimension of the fitting cylindrical surface 25 can be managed accurately and constantly. Therefore, the size of the leakage gap 26 between the fitting cylindrical surface 25 and the inner circumference of the plunger 10 can be controlled with high dimensional accuracy, and a stable damping force can be obtained.
  • the outer circumference of the portion of the first sleeve 13 inserted into the plunger 10 is formed to have a smaller diameter than the fitting cylindrical surface 25 of the outer circumference of the second sleeve 14. Therefore, the gap between the outer circumference of the first sleeve 13 and the inner circumference of the plunger 10 is relatively large, and the viscous resistance of oil flowing through the gap is small. Therefore, when the insertion length of the first sleeve 13 into the plunger 10 changes due to the movement of the plunger 10, the magnitude of the damping force is less likely to change, and a stable damping force can be obtained.
  • the second sleeve 14 is supported so as to allow radial movement of the second sleeve 14 with respect to the first sleeve 13. and the axis of the plunger 10 inserted into the cylinder 9, the second sleeve 14 moves radially with respect to the first sleeve 13 according to the deviation,
  • the size of the leakage gap 26 between the fitting cylindrical surface 25 on the outer circumference of the second sleeve 14 and the inner circumference of the plunger 10 is made uniform in the radial direction. Therefore, it is possible to obtain a stable damper force.
  • the chain tensioner 1 supports the return spring 18 with the second sleeve 14, so that the reaction force of the return spring 18 urging the plunger 10 (see FIG. 2) A second sleeve 14 is pressed against the first sleeve 13 . Therefore, it is possible to prevent the first sleeve 13 and the second sleeve 14 from separating due to engine vibration or the like.
  • the relief sheet surface 36 formed on the second sleeve 14 is an annular surface having a convex arcuate cross section
  • the contact surface 37 of the sheet member 21 with the relief sheet surface 36 is a tapered surface.
  • the relief seat surface 36 formed on the second sleeve 14 may be a tapered surface
  • the contact surface 37 of the sheet member 21 with the relief seat surface 36 may be an annular surface having a convex arcuate cross section. good.
  • the sheet member 21 is axially movable on the inner periphery of the first sleeve 13 or the second sleeve 14 to the reservoir chamber 16 side (left side in the figure) from the contact position with the relief sheet surface 36.
  • An outer cylindrical surface 41 to be guided and an oil passage groove 42 axially penetrating the outer cylindrical surface 41 are formed so as to divide the outer cylindrical surface 41 in the circumferential direction.
  • a plurality of oil passage grooves 42 are provided at intervals in the circumferential direction.
  • the posture of the seat member 21 when the seat member 21 is separated from the relief seat surface 36 is stabilized by the outer cylindrical surface 41, and the oil flows when the seat member 21 is separated from the relief seat surface 36.
  • the passage can be secured by the oil passage groove 42 .
  • an air vent groove 43 may be formed in the contact surface 37 of the sheet member 21 with the relief sheet surface 36 .
  • the air vent groove 43 is a groove extending across an annular portion where the seat member 21 and the relief seat surface 36 are in contact with each other.
  • an air vent groove 44 may be formed in the contact surface of the seat member 21 with the valve body 22 (that is, the seat surface of the check valve 15).
  • the air vent groove 44 is a groove that extends across an annular portion where the valve body 22 and the seat member 21 contact each other.
  • an air release groove 43 is formed in the contact surface 37 of the seat member 21 with the relief seat surface 36, and an air release groove 44 is formed in the contact surface of the seat member 21 with the valve body 22. is also possible.
  • annular projection 50 is formed at the insertion end of the first sleeve 13 into the plunger 10 .
  • the annular projection 50 is an annular axial projection around the axis of the first sleeve 13 .
  • the second sleeve 14 is formed with an annular recess 51 that fits into the annular protrusion 50 .
  • the annular recess 51 is an annular axial recess around the axis of the second sleeve 14 .
  • the second sleeve 14 is radially positioned with respect to the first sleeve 13 by fitting the annular projection 50 and the annular recess 51 .
  • the protruding end of the first sleeve 13 from the plunger 10 has an annular partial spherical surface 52 axially abutted against and supported by the closed end of the cylinder 9 .
  • the partial spherical surface 52 is a portion of a spherical surface centered on the axis of the first sleeve 13 .
  • the closed end of the cylinder 9 has a concave tapered surface 53 that slidably supports a partial spherical surface 52 to allow tilting of the first sleeve 13 .
  • the chain tensioner 1 of this embodiment can align the axial center of the first sleeve 13 and the axial center of the second sleeve 14 by fitting the annular projection 50 and the annular recess 51 together. Therefore, it is possible to stabilize the oil flow in the leak gap 26 .
  • the end of the first sleeve 13 protruding from the plunger 10 is supported by the closed end of the cylinder 9 so as to be tiltable.
  • the first sleeve 13 tilts with respect to the cylinder 9 according to the deviation, and the fitting cylindrical surface 25 of the outer circumference of the second sleeve 14 and the inner circumference of the plunger 10, the size of the leak gap 26 is made uniform in the axial direction. Therefore, it is possible to obtain a stable damper force.
  • the second sleeve 14 is fixed to the first sleeve 13 by the interference, so that the first sleeve 13, the second sleeve 14, the relief spring 34, the seat member 21, and the valve body 22 are integrated. It can be handled as an assembly (assie), and the assembling workability of the chain tensioner 1 can be improved.
  • the annular protrusion 50 and the annular recess 51 are separated from each other as shown in FIG.
  • the axial length of the portion to be fitted is set short (for example, less than the radial thickness of the second sleeve 14 shown in FIG. 13), and the portion to which the annular convex portion 50 and the annular concave portion 51 are fitted is shortened. , preferably arranged so as not to radially overlap the fitting cylindrical surface 25 .
  • FIG. 14 shows an example in which the closed end of the cylinder 9 is formed with a concave tapered surface 53
  • the closed end of the cylinder 9 may be formed with a concave spherical surface 54 as shown in FIG.
  • the partial spherical surface 52 of the protruding end of the first sleeve 13 from the plunger 10 is slidably supported by the concave spherical surface 54 formed at the closed end of the cylinder 9, and the sliding causes the first sleeve 13 to move. It is designed to allow tilting.
  • the chain tensioner 1 is incorporated in a chain transmission device that transmits the rotation of the crankshaft 2 to the camshaft 4.
  • a chain transmission that transmits power to accessories such as a water pump and a supercharger
  • a chain transmission that transmits the rotation of a crankshaft to a balancer shaft, or a chain transmission that connects intake and exhaust cams of a twin-cam engine. is also possible.

Abstract

Ce tendeur de chaîne comprend : un premier manchon (13) inséré dans un piston (10) ; un second manchon (14) relié au premier manchon (13) ; un clapet anti-retour (15) intégré au second manchon (14) ; et une surface cylindrique d'accouplement (25) formée sur la périphérie externe du second manchon (14). Le premier manchon (13) a un ressort de décharge (34) qui presse un élément feuille (21) qui y est intégré et une surface de feuille de décharge (36) est formée sur le second manchon (14). L'élément feuille (21), le ressort de décharge (34) et la surface de feuille de décharge (36) constituent une soupape de décharge (38).
PCT/JP2022/010039 2021-03-11 2022-03-08 Tendeur de chaîne WO2022191195A1 (fr)

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Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018076878A (ja) * 2016-11-07 2018-05-17 株式会社椿本チエイン テンショナ
JP2019078299A (ja) * 2017-10-20 2019-05-23 株式会社椿本チエイン テンショナ及びリリーフバルブユニット

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018076878A (ja) * 2016-11-07 2018-05-17 株式会社椿本チエイン テンショナ
JP2019078299A (ja) * 2017-10-20 2019-05-23 株式会社椿本チエイン テンショナ及びリリーフバルブユニット

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