WO2000034685A1 - Tendeur destine a appliquer une tension a un element de transmission de force - Google Patents

Tendeur destine a appliquer une tension a un element de transmission de force Download PDF

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Publication number
WO2000034685A1
WO2000034685A1 PCT/JP1999/006882 JP9906882W WO0034685A1 WO 2000034685 A1 WO2000034685 A1 WO 2000034685A1 JP 9906882 W JP9906882 W JP 9906882W WO 0034685 A1 WO0034685 A1 WO 0034685A1
Authority
WO
WIPO (PCT)
Prior art keywords
tensioner
shaft member
shaft
load
case
Prior art date
Application number
PCT/JP1999/006882
Other languages
English (en)
Japanese (ja)
Inventor
Kazuo Ishii
Kenjiro Kawanabe
Shigemasa Takahashi
Takao Kobayashi
Original Assignee
Nhk Spring 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 Nhk Spring Co., Ltd. filed Critical Nhk Spring Co., Ltd.
Priority to AU16814/00A priority Critical patent/AU1681400A/en
Priority to JP2000587105A priority patent/JP4447786B2/ja
Publication of WO2000034685A1 publication Critical patent/WO2000034685A1/fr

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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
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/0806—Compression coil springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0802—Actuators for final output members
    • F16H2007/081—Torsion springs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H7/00—Gearings for conveying rotary motion by endless flexible members
    • F16H7/08—Means for varying tension of belts, ropes, or chains
    • F16H2007/0889—Path of movement of the finally actuated member
    • F16H2007/0891—Linear path
    • 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
    • F16H2007/0897—External to internal direction

Definitions

  • the present invention relates to a tensioner for properly maintaining the tension of a force transmission member in a power transmission mechanism using a force transmission member such as an endless belt or an endless chain.
  • FIGS 14 and 15 show cross sections of conventional tensioners.
  • This tensioner has a case 31.
  • a first shaft member 32 and a cylindrical second shaft member 33 are inserted into the case 31.
  • the case 31 includes a flange portion 31b having a mounting hole 31a for fixing to a device such as an engine.
  • a male screw portion 32 a is formed on the outer surface of the first shaft member 32.
  • a female screw part 33 a is formed on the inner surface of the second shaft member 33.
  • the male screw part 32a and the female screw part 33a are screwed together.
  • the rear end 32 b of the first shaft member 32 is inserted into a fitting hole 39 formed inside the case 31.
  • the end surface 32 f of the rear end 32 b is in contact with the inner surface of the case 31.
  • a torsion spring is provided on the outer peripheral side of the first shaft member 32. 3 4 are provided.
  • One end 34 a of the torsion spring 34 is locked to the first shaft member 32, and the other end 34 b is locked to the case 31.
  • the spring 34 is twisted, a torque for rotating the first shaft member 32 is generated by the repulsive force of the spring 34.
  • the first shaft member 32 is rotatable with respect to the case 31.
  • the cylindrical second shaft member 33 passes through a sliding hole 35 a formed in the bearing 35.
  • the outer peripheral surface of the second shaft member 33 and the inner peripheral surface of the sliding hole 35a are both non-circular. Therefore, the second shaft member 33 is allowed to move in the axial direction with respect to the bearing 35, and the rotation is prevented. For this reason, when the first shaft member 32 rotates due to the repulsive force of the torsion spring 34, the second shaft member 33 does not rotate and generates a thrust in the axial direction.
  • the repulsive force of the spring 34 acts in a direction in which the second shaft member 33 projects from the case 31.
  • the conventional tensioner is a liner in which the input load F is proportional to the amount of movement of the second shaft member 33, as shown by the line segment L1 in FIG. Characteristics.
  • the tension of the force transmitting member such as a chain or a belt changes every moment depending on, for example, the operating conditions of the engine.
  • the conventional tensioner has a problem that it is difficult to cope with a wide range of change in input load because it has a linear (1 iner) characteristic.
  • the stiffness of the tensioner can be expressed by the amount of movement (ie, displacement amplitude) of the second shaft member with respect to the load received from the force transmitting member.
  • a tensioner with high thrust and high rigidity can withstand a large input load, but the displacement amplitude ⁇ is small.
  • the thrust of the tensioner is reduced, the displacement amplitude ⁇ can be increased, but it cannot respond to a large input load.
  • increasing the stiffness of the tensioner decreases the displacement amplitude.
  • tensioners with high rigidity had to be designed to function in a narrow range of displacement amplitude ⁇ , and there was a problem that the freedom of tensioner design was narrow.
  • An object of the present invention is to provide a tensioner capable of responding to a wide range of change in input load, such as a large displacement amplitude despite high rigidity. It is here. Disclosure of the invention
  • the tensioner of the present invention is a tensioner of the present invention.
  • a first shaft member It is rotatably inserted inside the case and has a first threaded part.
  • a second shaft member having a second screw portion to be screwed to the first screw portion and movable in the axial direction with respect to the case and restricted in rotation;
  • the load transmitting unit is allowed to be displaced in the axial direction with respect to the second shaft member according to the axial load input to the second shaft member via the load transmitting unit.
  • a buffer mechanism that allows the first shaft member to be displaced in the axial direction with respect to the case.
  • a compression coil spring, a disc spring, a rubber member, or a liquid pressurized to a predetermined pressure can be used (the elastic member typified by rubber or a spring is the first member).
  • the elastic member may be provided on at least one of the shaft member and the second shaft member, and the elastic member may be a load transmitting member provided on a tip end of the second shaft member. It may be interposed between the end member as a part and the second shaft member.
  • the load transmission unit when, for example, a small load is input to the second shaft from a force transmission member such as a belt chain, the load transmission unit is driven by the second transmission.
  • the first shaft member is axially displaced relative to the case, or the first shaft member is axially displaced relative to the case.
  • the first shaft member rotates via the first screw portion and the second screw portion.
  • the shock absorbing mechanism for example, when the input load is small, by mainly operating the shock absorbing mechanism, tension can be applied to the force transmitting member.
  • the original tension action by the first shaft member and the second shaft member can be performed.
  • FIG. 1A is a sectional view of a tensioner showing a first embodiment of the present invention
  • FIG. 1B is a cross-sectional view of a part of the engine showing an example of use of the tensioner shown in FIG. 1A.
  • Fig. 2A is a cross-sectional view of a part of the tensioner when a large load is applied to the tensioner shown in Fig. 1,
  • Fig. 2B is a cross-sectional view of a part of the tensioner when a small load is applied to the tensioner shown in Fig. 1,
  • FIG. 3A is a sectional view of a tensioner showing a second embodiment of the present invention
  • FIG. 3B is a sectional view of a tensioner showing a third embodiment of the present invention.
  • FIG. 3C is a cross-sectional view of a tensioner showing a fourth embodiment of the present invention.
  • FIG. 4A is a cross-sectional view of a tensioner showing a fifth embodiment of the present invention.
  • FIG. 4B is a cross-sectional view of the tensioner when a large load is applied to the tensioner shown in FIG. 4A.
  • FIG. 5 is a sectional view of a tensioner showing a sixth embodiment of the present invention.
  • FIG. 6 is a sectional view of a tensioner showing a seventh embodiment of the present invention.
  • FIG. 7 is a sectional view of an eighth embodiment of the present invention.
  • FIG. 8 is a cross-sectional view of a tensioner according to a ninth embodiment of the present invention.
  • FIG. 9 is a cross-sectional view of the tensioner according to a tenth embodiment of the present invention.
  • FIG. 10 is a sectional view of a tensioner showing a first embodiment of the present invention.
  • FIG. 11 is a cross-sectional view of a tensioner showing a 12th embodiment of the present invention.
  • FIG. 12 is a sectional view of a part of a tensioner showing a thirteenth embodiment of the present invention.
  • FIG. 13 is a diagram showing the relationship between the load input to the present invention and the conventional tensioner and the displacement of these tensioners.
  • Fig. 14 is a sectional view of a conventional tensioner.
  • FIG. 15 is a sectional view along the radial direction of the tensioner shown in FIG. BEST MODE FOR CARRYING OUT THE INVENTION
  • the tensioner A1 shown in FIG. 1A is used for, for example, a power transmission mechanism 101 of an automobile engine 100 shown in FIG. 1B.
  • the power transmission mechanism 101 transmits the rotational motion of the engine 100 to the cam shaft 103 via an endless force transmission member 102 such as a timing belt or a chain.
  • the tensioner A1 is attached to a predetermined position of the engine 100, and generates a thrust described later, thereby pushing the force transmitting member 102 in a direction indicated by an arrow V.
  • the tensioner A 1 includes a hollow case 1, a first shaft member 2, and a second shaft member 3.
  • the shaft assembly S is formed by screwing the shaft members 2 and 3 together at the screw portions 2a and 3a.
  • Shaft assembly S is included in Case 1.
  • the front end of the case 1 is open, and the second shaft member 3 advances and retreats through this opening.
  • a screw hole 19 is formed at the rear end of the case 1.
  • a bolt 19 a for sealing the inside of the case 1 is screwed into the screw hole 19.
  • An external thread 2 a is formed in the first shaft member 2.
  • the second shaft member 3 has a cylindrical shape, and has a female screw portion 3a formed on an inner peripheral surface thereof.
  • a shaft assembly S is formed by screwing the male screw portion 2a into the female screw portion 3a. It is customary for these threaded portions 2a and 3a to have a larger lead angle than a general thread, such as a triple-threaded thread. Multi-start thread (mu 11 ip 1 e thread) force S is adopted.
  • a torsion spring 4 is provided on the outer peripheral side of the shaft assembly S. The torsion spring 4 extends in the axial direction of the shaft members 2 and 3. One end 4 a of the torsion spring 4 is locked to the case 1. The other end 4 b of the torsion spring 4 is inserted into a slit 2 b formed at the rear end of the first shaft member 2.
  • the first shaft member 2 can be rotated.
  • the spring 4 moves the shaft member 2 in the second direction (eg, counterclockwise). It stores the elastic energy (initial torque) that rotates.
  • a bearing member 1a is fixed to a front end of the case 1 by a retaining ring 1b.
  • the bearing member 1a has a non-circular sliding hole 1c through which the second shaft member 3 is inserted.
  • the radial cross section of the second shaft member 3 is non-circular corresponding to the sliding hole 1c. For this reason, the second shaft member 3 can move in the axial direction with respect to the case 1, but is prevented from rotating.
  • a bearing member 1 e is fixed to a concave portion formed at the bottom of the case 1.
  • the end of the first shaft member 2 is rotatably inserted into the bearing member 1e.
  • the first shaft member 2 generates friction torque by rotating with the end surface 2f subsequently in contact with the end surface 1f of the case 1.
  • the end of the first shaft member 2 may be directly inserted into the recess formed in the case 1 without using the bearing member 1e. This point can be applied to each embodiment described below.
  • the force opposing this torque is the friction torque generated between the end face 2 f of the first shaft member 2 and the end face 1 f of the case 1, the repulsive force of the torsion spring 4, and the like.
  • an appropriate tension can be applied to the force transmission member 102.
  • the tension is applied to the force transmitting member 102 by the axial movement of the second shaft member 3 while the first shaft member 2 rotates. In the following, it is referred to as the "principal tension effect.”
  • the tensioner A 1 has a buffer mechanism 5.
  • the buffer mechanism 5 has a disc spring 9 as an example of an elastic member.
  • the disc spring 9 is provided with a cap 6 provided on the second shaft member 3. It is provided between the edge part 7 and the end member 8.
  • the end member 8 functioning as a load transmitting portion is urged in a direction protruding from the cap 6 due to a repulsive load generated when the disc spring 9 is compressed in the axial direction. Is done.
  • the cap 6 has a leg 6 a which is inserted into and fixed to an opening 3 c formed at the end of the second shaft 3, and a slide groove formed in the leg 6 a. 23 and the flange portion 7 etc.
  • the end member 8 has a shaft portion 8a that is inserted into the slide groove 23 so as to be movable in the axial direction.
  • a slide hole 21 is formed in the shaft portion 8a along the axial direction.
  • the roller 20 is attached to the leg 6 a of the cap 6.
  • the roller 20 is inserted into the slide hole 21.
  • a horn is provided at the end of the shaft part 8a of the end member 8.
  • Pin 22 is installed at the end of the shaft part 8a of the end member 8. Therefore, the end member 8 is provided with the roller 20 and the horn, with respect to the cap 6.
  • a predetermined stroke regulated by the pin 22 can be moved in the axial direction.
  • a circlip may be used instead of the stop pin 22.
  • Pins may be used instead of rollers 20.
  • the disc spring 9 is deformed into a flat shape when the load F input to the end member 8 exceeds a predetermined value, and cannot be further deformed. . In this state, the plate 9 becomes substantially rigid.
  • the maximum deformation of the elastic member (for example, the disc spring 9) due to the large load F is referred to as "reached the deformation limit”.
  • this tensioner A 1 is configured so that the above-mentioned “main tensioning action” can be performed before the disc spring 9 reaches the deformation limit, that is, in a load range where the disc spring 9 can be deformed. It may be. This is the same for the tensioners of all the embodiments described below.
  • the end member 8 when the input load F is small, the end member 8 is elastically supported by the cap 6 by the disc spring 9. In this case, the disc spring 9 bends in the axial direction of the cap 6 according to the input load F, so that the displacement of the end member 8 is absorbed. For example, when the input load F increases, the end member 8 moves in a direction approaching the cap 6, and when the input load F decreases, the end member 8 moves in a direction away from the cap 6.
  • the disc spring 9 When the input load F exceeds a predetermined value, the disc spring 9 reaches the deformation limit as shown in FIG. 2A, so that the second shaft is integrally formed with the end member 8 functioning as a load transmitting portion. Member 3 moves in the axial direction. In this case, the first shaft member 2 is rotated. Therefore, the main tensioning action is performed. Depending on various conditions such as the spring constant of the disc spring 9 and the friction torque when the shaft member 2 rotates, the main tension is shifted to the load range before the disc spring 9 reaches the deformation limit. It can be done.
  • the endless running of the force transmission member 102 stops, so that a constant static load acts on the second shaft member 3.
  • the tensioner A1 usually does not respond to such a slow decrease in tension (change in static load), and the second shaft member 3 remains stopped.
  • the second shaft member 3 protrudes from the case 1 by an amount corresponding to the slack of the force transmitting member 102.
  • the first shaft member 2 rotates according to the amount of movement. If the engine 100 after the start is kept in the idling state, the temperature of the engine gradually increases, so that the tension of the force transmitting member 102 increases.
  • the second shaft member 33 does not follow the input load F in a conventional tensioner (for example, the tensioner shown in FIG. 14). Sometimes. As a result, in the conventional tensioner, an operation delay may occur with respect to an increase in the tension of the force transmission member 102.
  • the disc spring 9 deforms to the extension side as shown in FIG. 2B.
  • the end member 8 Only the force moves toward the force transmitting member 102.
  • the disc spring 9 is compressed according to the input load F, so that the force transmitting Excessive tension of the member 102 is avoided.
  • the engine 100 returns to the normal operating state, and when the input load F increases, the disc spring 9 is compressed to the deformation limit as shown in Fig. 2A.
  • the second shaft member 3 moves in the axial direction integrally with the end member 8.
  • the tensioner A 1 performs the main tension action.
  • the tensioner A1 of the present embodiment provided with such a buffering mechanism 5 is capable of properly maintaining the tension of the force transmitting member 102 caused by the temperature change of the engine 100. I can do it. Moreover, the tensioner A 1 can keep the tension of the force transmitting member 102 properly even when the input load F is small.
  • FIG. 3A shows a tensioner A 2 according to a second embodiment of the present invention.
  • the cushioning mechanism 5 a of the tensioner A 2 includes a compression coil spring 10 as an example of an elastic member between the flange portion 7 of the cap 6 and the end member 8.
  • the tensioner A2 of the second embodiment is common to the tensioner A1 of the first embodiment.
  • the compression coil spring 10 urges the end member 8 in a direction to protrude from the cap 6 to lay.
  • the coil spring 10 elastically supports the end member 8 under an input load of a predetermined value or less, and receives a load of a predetermined value or more as in the case of the disc spring 9 of the first embodiment. Then the deformation limit is reached.
  • FIG. 3B shows a tensioner A 2 according to a third embodiment of the present invention.
  • the cushioning mechanism 5b of the tensioner A2 includes a cylindrical rubber member 11 as an example of an elastic member between the flange portion 7 of the cap 6 and the end member 8. I have.
  • the tensioner A2 of the third embodiment is common to the tensioner A1 of the first embodiment.
  • the rubber member 11 urges the end member 8 in a direction to protrude from the cap 6. Similar to the disc spring 9 of the first embodiment, the rubber member 11 elastically supports the end member 8 with an input load equal to or less than a predetermined value, and has a deformation limit when a load exceeding the predetermined value is input.
  • the transition to the “main tension action” may occur. Yes.
  • FIG. 3C shows a tensioner A 2 according to a fourth embodiment of the present invention.
  • the cushioning mechanism 5c of the tensioner A2 includes a compression coil spring 15 as an example of the elastic member.
  • a cup-shaped thrust bearing 13 is provided between the compression coil spring 15 and the first shaft member 2. Bottom of thrust bearing 13 The friction torque is generated by the contact between 13 a and the end face 2 f of the shaft member 2.
  • the thrust bearing 13 and the coil spring 15 are housed in a housing 14 formed inside the case 1.
  • the coil spring 15 presses the shaft assembly S in the axial direction via the thrust bearing 13.
  • the tensioner A2 of the fourth embodiment is common to the tensioner A1 of the first embodiment.
  • the coil spring 15 when the load F input to the second shaft member 3 is larger than a predetermined value, the coil spring 15 is compressed. As a result, the thrust bearing 13 comes into contact with the step 18 of the case 1. When the bearing 13 comes into contact with the step 18, the coil spring 15 reaches the deformation limit, so that “the main tensioner action” is performed by the shaft members 2 and 3.
  • the cushioning mechanism 5 c is formed by a simple operation of merely attaching the coil spring 15 and the bearing 13 to the housing 14 formed in the case 1. Can be configured.
  • the tensioner A2 of the fourth embodiment can improve the assemblability of the buffer mechanism 5c in addition to the effect of the first embodiment.
  • the repulsive load of the coil spring 15 is changed by changing the screwing amount of the bolt 19a screwed into the screw hole 19. You can force. That is, it is possible to adjust the magnitude of the input load F until the coil spring 15 reaches the deformation limit. Also in the fourth embodiment, the coil spring 15 is moved before reaching the deformation limit. In the load range, the shift to the “main tension action” by the shaft members 2 and 3 may occur.
  • the tensioner A 3 includes a case 31, a first shaft member 32, a cylindrical second shaft member 33, a torsion spring 34, and an end member 3. 6 and a buffer mechanism 40.
  • the case 31 has a flange portion 31b having a mounting hole 31a for fixing to a device such as an engine.
  • a thread portion 32 a is formed on the outer surface of the first shaft member 32.
  • a female screw 33 a is formed on the inner surface of the second shaft member 33.
  • the male screw part 32a and the female screw part 33a force S are screwed together.
  • the rear end of the first shaft member 32 is inserted into a cup-shaped shaft receiving member 38 fixed inside the case 31. When the end surface 32 f of the first shaft member 32 contacts the bottom surface 38 a of the shaft receiving member 38, friction torque is generated during rotation.
  • the outer cylinder member 41 is fixed to the tip of the second shaft member 33 by pins 33b.
  • One end 34 a of the torsion spring 34 is locked to the first shaft member 32, and the other end 34 b is locked to the case 31.
  • the spring 34 is twisted, a torque for rotating the first shaft member 32 is generated by the repulsive force of the spring 34.
  • the first shaft member 32 is rotatable with respect to the case 31.
  • the cylindrical second shaft member 33 is inserted through a sliding hole 35 a formed in the bearing 35.
  • the second shaft member 33 is It is allowed to move in the axial direction with respect to the bearing 35, and the rotation is prevented. Therefore, when the first shaft member 32 rotates due to the repulsive force of the torsion spring 34, the second shaft member 33 does not rotate and generates a thrust in the axial direction.
  • the repulsive force of the spring 34 acts in a direction in which the second shaft member 33 projects from the case 31.
  • the cushioning mechanism 40 of the tensioner A3 includes an end member 36 functioning as a load transmitting portion, and a flange portion 36a of the end member 36 and the outer cylindrical member 41.
  • a ring-shaped rubber member 42 and a coil spring 43 are provided therebetween.
  • a shaft 36 b is formed at the center of the end member 36.
  • the shaft portion 36 b is inserted into a through hole formed in the outer cylinder member 41 so as to be movable in the axial direction.
  • a convex portion 36c is formed along the circumferential direction.
  • the projection 36 c can be brought into contact with a locking portion 41 a formed on the inner periphery of the outer cylinder member 41.
  • the compression coil spring 43 constantly urges the end member 36 in the direction in which it protrudes from the outer cylinder member 41. As shown in FIG. 4A, when the end member 36 protrudes from the outer cylinder member 41 to the maximum, a gap G1 of a predetermined distance is secured between the rubber member 42 and the flange portion 36a. Is done.
  • the rubber member 42 alleviates the collision between the flange portion 36a and the outer cylinder member 41 when the flange portion 36a is pushed toward the outer cylinder member 41 (an abnormal noise). To prevent occurrence) Function and the function of pushing back the flange member 36a. Note that, instead of the coil spring 43, a cylindrical rubber-like elastic member may be used.
  • the line segment L 2 shown in FIG. 13 represents the relationship between the load F and the displacement ⁇ of the tensioner A 3. From when the input load F is zero to the bending point 1, the repulsive load of the coil spring 43 mainly acts. Therefore, the force for pushing back the end member 36 is weak, but the displacement ⁇ per load is relatively large.
  • the input load F increases and the rubber member 42 and the coil spring 43 cooperate, the characteristic between the bending point 1 and the bending point 2 is obtained, and the end member 36 is pushed. The returning force increases, and the displacement ⁇ per load decreases. If the input load F is further increased, the rubber member 42 and the coil spring 43 will reach the deformation limit, resulting in a characteristic exceeding the bending point 2 (the same inclination as the line segment L1). . In other words, under a large load, the tensioner A 3 is mainly driven by the shaft members 32 and 33. The effect will be performed.
  • the displacement ⁇ when a small load is input can be increased, so that the shaft members 32, 33 can be attached to the same. Even if the pressing force of the main tension action is set to be high, the ability to follow a weak load is improved.
  • FIG. 5 shows a tensioner 4 according to a sixth embodiment of the present invention.
  • This tensioner A4 has a buffer mechanism using hydraulic pressure.
  • This buffer mechanism includes a first oil chamber 46 filled with oil 45 at the leading end of the second shaft member 33.
  • a cap-shaped end member 36 is inserted into the oil channel 46 so as to be movable in the axial direction.
  • a rubber member 48 is attached to a partition wall 47 that forms the bottom of the first oil chamber 46.
  • a second oil channel / column 49 is formed on the opposite surface of the partition wall 47. Second oil chamber 4
  • Second oil chamber 4 communicates with the first vorciano 46 via a circulation section 50 formed in the partition wall 47. Second oil chamber 4
  • the tensioner A4 of the sixth embodiment is substantially common to the tensioner A3 of the fifth embodiment.
  • the end member 36 When the load F is input to the end portion 6, the end member 36 is pressed, so that the oil in the first oil chamber 46 flows through the flow portions 50, 5. It is returned to the engine body side through 1. Since this oil is pressurized to a predetermined pressure, the end member 36 exerts a buffering action against the input load F. When the input load F decreases, oil at a predetermined pressure is again supplied to the first oil chamber 46 through the circulation sections 50 and 51.
  • FIG. 6 shows a tensioner A5 according to a seventh embodiment of the present invention.
  • the basic configuration of the tensioner A5 is the same as that of the tensioner A3 of the fifth embodiment shown in FIG. 4A, but the shape of the coil spring 43 constituting the buffer mechanism 40 is described. However, this is different from the fifth embodiment.
  • the coil spring 43 of the seventh embodiment has a wide pitch portion 43a and a narrow pitch portion 43b.
  • the coil Hey 4 3 is compressed.
  • the narrow pitch portion 4 3 b causes close contact between the strands, so the spring constant of the coil spring 4 3 starts at the bending point 1 of the line segment 3 shown in Fig. 13.
  • the force for pushing back the end member 36 increases.
  • the end member 36 comes into contact with the rubber member 42, so that the coil spring 43 and the rubber member 42 cooperate with each other.
  • FIG. 7 shows a tensioner A6 according to an eighth embodiment of the present invention.
  • the buffer mechanism 40 of the tensioner A 6 includes a rubber member 42, a first coil spring 43, and a second coil spring 43 c.
  • the end member 36 has a flange portion 36a and a cylindrical outer peripheral portion 36d.
  • a second coil spring 43c is provided outside the outer periphery 36d.
  • the spring constant of 43 c is smaller than that of the first coil spring 43.
  • the end member 36 is constantly urged by the second coil spring 43 c in a direction protruding from the outer cylinder member 41. End member When the load F is applied to the load 36, the gap G2 having a predetermined distance exists between the end surface of the first coil spring 43 and the inner surface of the end member 36.
  • FIG. 8 shows a tensioner A7 according to a ninth embodiment of the present invention.
  • This embodiment is a tensioner in which the rubber member 42 is omitted from the tensioner A3 shown in FIG. 4A. Otherwise, the configuration of the tensioner A7 of this embodiment is the same as that of the tensioner A3 in FIG. 4A.
  • FIG. 9 shows a tensioner A8 according to a tenth embodiment of the present invention.
  • the cushioning mechanism 40 of the tensioner A 8 includes a base 55 fixed to a distal end of the second shaft member 33 by a connecting member 54, and a rubber member mounted on the base 55. 5 and a compression coil spring 43 provided on the outer peripheral side of the cylindrical portion 55 a of the base 55.
  • the end member 36 is constantly urged by the compression coil spring 43 in a direction protruding from the base 55.
  • the end member 36 is formed with a cylindrical outer peripheral portion 36 d.
  • the outer peripheral portion 36 d covers the coin spring 43, the base 55, and the rubber member 56.
  • FIG. 10 shows a tensioner A 9 according to the eleventh embodiment of the present invention. Show and review.
  • the torsion spring 34 of the tensioner A 9 has a length that reaches the second shaft member 33 inside the case 31.
  • the configuration and operation of the buffer mechanism 40 of the tensioner A9 are the same as those of the tensioner A8 of the tenth embodiment shown in FIG.
  • FIG. 11 shows a tensioner A 10 according to a twelfth embodiment of the present invention.
  • This tensioner A 10 has a shock absorbing mechanism using hydraulic pressure.
  • This cushioning mechanism includes a piston-like shaft receiving member 57 accommodated in the case 31, a compression coil spring 60 for elastically supporting the shaft receiving member 57, and It includes a first oil chamber 58 filled with oil and a second oil chamber 59, and the like.
  • the shaft receiving member 57 can move in the axial direction of the case 31.
  • the inner volume of the first oil channel 58 is defined by the inner surface of the case 31 and the shaft receiving member 57, and accommodates a compression coil spring 60 therein.
  • the first oil chamber 58 communicates with the second oil chamber 59 via a circulation section 61 formed in the case 31. Oil of a predetermined pressure is supplied to the second oil chamber 59 from an engine body (not shown).
  • the load F input to the end member 36 is equal to the second shaft member 33, the first shaft member 32, and the shaft receiving member 57. And are pressed in the axial direction. As a result, the shaft receiving member 57 moves in the direction of compressing the coil spring 60, thereby causing the The oil is returned to the second oil chamber 59 through the circulation section 61. Since the oil in the oil reservoirs 58 and 59 is pressurized to a predetermined pressure, a buffer effect is exerted corresponding to the input load F. Further, when the shaft receiving member 57 comes into contact with the coil spring 60 and the coil spring 60 is compressed, a force is generated that pushes the receiving member 57 back in accordance with the amount of compression.
  • the end member 36 is pushed back by the force.
  • oil at a predetermined pressure is again supplied to the first oil chamber 58 through the circulation part 61.
  • the shaft receiving members 57 and the shaft members 32 and 33 are pushed back.
  • FIG. 12 shows a buffer mechanism 40 according to a thirteenth embodiment of the present invention.
  • the coil spring 43 of the buffer mechanism 40 is covered by an elastic member 65 such as rubber.
  • the rubber referred to in this specification is a concept that includes not only natural rubber but also synthetic rubber or elastomer of synthetic resin such as urethane.
  • the cushioning mechanism 40 of the thirteenth embodiment when the load F is input, the coil spring 43 and the elastic member 65 cooperate to push the end member 36 back. Since the elastic member 65 is interposed between the strands of the coil spring 43, the coil spring 43 is compressed until the strands come into close contact. In the event of noise, noise caused by contact between the wires can be prevented.
  • the tensioner of the thirteenth embodiment is common to the ninth embodiment (FIG. 8).
  • each of the tensioners of the above-described embodiments is configured such that the buffer mechanism operates with a small input load.
  • the present invention is configured such that the "primary tension action" is performed by the first and second shaft members in a small load range, and the buffer mechanism operates when the input load increases. You may do it.
  • each of the torsion springs urges the second shaft member in a direction of pushing the second shaft member out of the case.
  • the repulsive force of the torsion spring may be configured to urge the second shaft member in a direction of drawing into the case.
  • the tensioner of the present invention can be suitably used for a power transmission mechanism using an endless belt, an endless chain, or the like, for example, in an automobile engine. .

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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)

Abstract

L'invention concerne un tendeur (A1) comprenant des éléments d'axe (2 et 3) vissés l'un à l'autre par des parties filetées (2a et 3a), dans lequel un premier élément d'axe (2) est formé rotatif par rapport à un logement (1) et son mouvement axial est limité, un second élément d'axe (3) peut être déplacé axialement bien qu'il soit limité en rotation par rapport au logement (1), un premier couple directionnel est fourni au premier élément d'axe (2) par un ressort à torsion (4), et un mécanisme tampon (5) est installé entre le second élément d'axe (3) et un élément terminal (8), le mécanisme tampon (5) étant doté d'un ressort (9) se déformant axialement selon une charge d'entrée (F) appliquée à l'élément terminal (8).
PCT/JP1999/006882 1998-12-08 1999-12-08 Tendeur destine a appliquer une tension a un element de transmission de force WO2000034685A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
AU16814/00A AU1681400A (en) 1998-12-08 1999-12-08 Tensioner for applying tension to force transmission member
JP2000587105A JP4447786B2 (ja) 1998-12-08 1999-12-08 力伝達部材に張力を与えるためのテンショナ

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP10/348607 1998-12-08
JP34860798 1998-12-08
JP33684399 1999-11-26
JP11/336843 1999-11-26

Publications (1)

Publication Number Publication Date
WO2000034685A1 true WO2000034685A1 (fr) 2000-06-15

Family

ID=26575592

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1999/006882 WO2000034685A1 (fr) 1998-12-08 1999-12-08 Tendeur destine a appliquer une tension a un element de transmission de force

Country Status (3)

Country Link
JP (1) JP4447786B2 (fr)
AU (1) AU1681400A (fr)
WO (1) WO2000034685A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002048201A (ja) * 2000-07-31 2002-02-15 Nhk Spring Co Ltd 推進ユニット及びテンショナー
WO2003048605A1 (fr) * 2001-12-03 2003-06-12 Nhk Spring Co., Ltd. Appareil a tension
JP2010230056A (ja) * 2009-03-26 2010-10-14 Ntn Corp オートテンショナ
JP2016038036A (ja) * 2014-08-08 2016-03-22 日本発條株式会社 荷重付加装置
JP2022051339A (ja) * 2020-09-18 2022-03-31 トヨタ自動車株式会社 ベルト余寿命診断装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63295820A (ja) * 1987-05-26 1988-12-02 Honda Motor Co Ltd 自動テンショナ
JPH0187353U (fr) * 1987-12-02 1989-06-09
JPH10213194A (ja) * 1997-01-31 1998-08-11 Koyo Seiko Co Ltd オートテンショナ

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63295820A (ja) * 1987-05-26 1988-12-02 Honda Motor Co Ltd 自動テンショナ
JPH0187353U (fr) * 1987-12-02 1989-06-09
JPH10213194A (ja) * 1997-01-31 1998-08-11 Koyo Seiko Co Ltd オートテンショナ

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2002048201A (ja) * 2000-07-31 2002-02-15 Nhk Spring Co Ltd 推進ユニット及びテンショナー
WO2003048605A1 (fr) * 2001-12-03 2003-06-12 Nhk Spring Co., Ltd. Appareil a tension
CN100501191C (zh) * 2001-12-03 2009-06-17 日本发条株式会社 张紧装置
JP2010230056A (ja) * 2009-03-26 2010-10-14 Ntn Corp オートテンショナ
JP2016038036A (ja) * 2014-08-08 2016-03-22 日本発條株式会社 荷重付加装置
JP2022051339A (ja) * 2020-09-18 2022-03-31 トヨタ自動車株式会社 ベルト余寿命診断装置
JP7392615B2 (ja) 2020-09-18 2023-12-06 トヨタ自動車株式会社 ベルト余寿命診断装置

Also Published As

Publication number Publication date
JP4447786B2 (ja) 2010-04-07
AU1681400A (en) 2000-06-26

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