JP5594464B2 - Torque fluctuation absorbing damper - Google Patents

Description

  The present invention relates to a torque fluctuation absorbing damper having a damper portion and a coupling portion. The torque fluctuation absorbing damper of the present invention is mounted on, for example, an engine crankshaft or mounted on another rotating shaft.

  Conventionally, as shown in FIG. 5, there is known a torque fluctuation absorbing damper 1 having a damper portion 11 for reducing vibration due to torsional resonance of a rotating shaft and a coupling portion 21 for reducing vibration transmission due to torque fluctuation of the rotating shaft. ing. The damper portion 11 has a configuration in which a vibration ring 15 is connected to the outer peripheral side of an outer peripheral cylindrical portion 12 d of the hub 12 fixed to the rotating shaft via a damper rubber 14, and the coupling portion 21 is an inner peripheral cylinder of the hub 12. The pulley 25 is connected to the outer peripheral side of the portion 12a via a coupling rubber 24, and a bearing 31 is interposed between the outer peripheral cylindrical portion 12d of the hub 12 and the pulley 25 (see Patent Document 1). ).

Japanese Patent No. 4006582 (FIG. 2)

  With regard to the conventional torque fluctuation absorbing damper 1 described above, it is conceivable to change the arrangement of each component. For example, as shown in FIG. 6, on the inner peripheral side of the outer peripheral cylindrical portion 12d of the hub 12 fixed to the rotating shaft. The damper portion 11 is configured by connecting the vibration ring 15 via the damper rubber 14, and the coupling portion is formed by connecting the pulley 25 to the outer peripheral side of the inner peripheral cylindrical portion 12 a of the hub 12 via the coupling rubber 24. In this case, since the pulley 25 is disposed on the inner peripheral side of the vibration ring 15, the bearing 31 is interposed between the vibration ring 15 and the pulley 25. The torque fluctuation absorbing damper 1 shown in FIG. 6 is not publicly known, and is therefore positioned as a comparative example rather than a conventional example with respect to the present invention.

  However, according to the damper 1 according to the comparative example of FIG. 6, the following disadvantages are pointed out.

  That is, since the damper 1 passes through the resonance region between the start and stop of the rotating shaft on which the damper 1 according to the comparative example is mounted and the idling speed, the relative amplitude of the coupling portion 21 is larger than the input amplitude during that period. Is bigger. On the other hand, if it exceeds the idling speed, it becomes a vibration-proof region, so that the relative amplitude of the coupling portion 21 becomes smaller than the input amplitude. Due to such characteristics, the damper 1 requires high attenuation during low-speed rotation in the resonance region and low attenuation during high-speed rotation in the vibration isolation region. I can't control (large or small).

  In view of the above points, the present invention can realize high attenuation during low-speed rotation, which is the resonance region, and low attenuation during high-speed rotation, which is the vibration isolation region. An object of the present invention is to provide a torque fluctuation absorbing damper capable of controlling the torque.

In order to achieve the above object, a torque fluctuation absorbing damper according to claim 1 of the present invention includes a damper portion in which a vibration ring is connected to a hub fixed to a rotating shaft via a damper rubber, and a coupling rubber to the hub. A coupling portion connected to a pulley, and the hub has an inner peripheral cylindrical portion, and an end surface portion is integrally formed radially outward from one axial end portion of the inner peripheral cylindrical portion, An outer peripheral cylindrical portion is integrally formed from the outer peripheral end portion of the end surface portion toward the other axial direction, and the damper portion is connected to the inner peripheral side of the outer peripheral cylindrical portion of the hub, and the inner peripheral side of the damper rubber The coupling ring is connected to the outer peripheral side of the inner peripheral cylindrical portion of the hub, the pulley is connected to the outer peripheral side of the coupling rubber, and the pulley is , Said coupling An inner peripheral cylindrical portion connected to the outer peripheral surface of the rubber band, and an end surface portion is integrally formed radially outward from the other axial end of the inner peripheral cylindrical portion, and the outer peripheral end portion of the end surface portion The outer peripheral cylindrical portion is integrally formed from one side to the other in the axial direction, a pulley groove is provided in the outer peripheral cylindrical portion, and the vibration ring is disposed in a non-contact manner on the outer peripheral side of the inner peripheral cylindrical portion of the pulley. And a vibration variation absorbing damper in which a bearing is interposed in a radial gap between the inner peripheral cylinder portion of the pulley and the vibration ring is divided into a plurality of divided bodies on the circumference, and each divided body is The vibration ring is displaceable in a radial direction, and the vibration ring generates a frictional damping force due to the sliding when the divided body is slidably contacted with the bearing during low-speed rotation, and the divided ring during high-speed rotation. The body is displaced radially outward by centrifugal force The frictional damping force is characterized by reduced or lost Ri.

  The torque fluctuation absorbing damper according to claim 2 of the present invention is the torque fluctuation absorbing damper according to claim 1, wherein the vibration ring is divided into three equal parts.

  The torque fluctuation absorbing damper according to claim 3 of the present invention is the torque fluctuation absorbing damper according to claim 1 or 2, wherein the circumferential end of the inner peripheral surface of each divided body of the vibration ring is A chamfered portion is provided so that each divided body does not cause galling (curling) with respect to the bearing.

  In the torque fluctuation absorbing damper having the above configuration, a pulley is disposed on the inner peripheral side of the vibration ring, a bearing is interposed between the vibration ring and the pulley, and the vibration ring is divided into a plurality of divided bodies on the circumference, Each divided body can be displaced in the radial direction. Further, the vibrating ring is in a state in which the divided body is slidably in contact with the bearing by the elasticity of the damper rubber in the initial motion posture, that is, the posture when the rotation is stopped.

  Therefore, at the time of low-speed rotation that is the resonance region, since the vibration ring is in contact with the pulley via the bearing, high friction damping can be obtained, and as a result, the damping by the coupling rubber is dominant as shown in FIG. As compared with the damper according to the comparative example, a large damping can be obtained, and the vibration transmissibility becomes low. In addition, since the vibration ring is divided, the vibration ring is displaced outward in the radial direction by a centrifugal force at the time of high-speed rotation that is the vibration isolation region. As a result, the frictional damping is reduced or eliminated, and a good anti-vibration effect can be obtained in the anti-vibration region. In addition, since friction damping is also added to the damper portion, it is possible to improve the durability of the damper rubber.

  Regarding the point at which the vibration ring is divided into a plurality of divided bodies on the circumference, it is desirable to divide the vibration ring in a uniform manner from the standpoint of balance accuracy of the entire damper. In this case, each divided body has the same shape and the same mass. The equal number is not particularly limited, but it is desirable that the number is equal to three in terms of function and handling work.

  In addition, when the vibration ring is divided into a plurality of divided bodies on the circumference, there is a concern that the circumferential end of the inner peripheral surface of the divided body may cause galling with respect to the outer peripheral surface of the bearing. By providing a chamfered portion on the surface, it becomes possible to prevent the occurrence of galling.

  The present invention has the following effects.

  That is, in the present invention, as described above, the pulley is disposed on the inner peripheral side of the vibration ring, the bearing is interposed between the vibration ring and the pulley, and the vibration ring is divided into a plurality of divided bodies on the circumference. Each divided body can be displaced in the radial direction. The vibrating ring is in a state in which the divided body is slidably in contact with the bearing in the initial motion posture, that is, the posture when rotation is stopped.

  During the low-speed rotation that is the resonance region, the state where the divided body is slidably contacted with the bearing is maintained, so that high damping is realized, and during the high-speed rotation that is the anti-vibration region, the divided body has a diameter due to centrifugal force. Since it is displaced outward in the direction, the contact state changes and low attenuation is realized. Accordingly, since the high attenuation and the low attenuation are automatically switched according to the situation in this way, it is possible to provide a torque fluctuation absorbing damper that exhibits an excellent attenuation function.

  Further, when the vibration ring is divided into three equal parts, the balance accuracy and handling workability of the damper as a whole can be ensured, and a chamfered portion is provided at the circumferential end of the inner peripheral surface of the divided body. In this case, it is possible to prevent the split body from galling with respect to the outer peripheral surface of the bearing.

Sectional drawing of the torque fluctuation absorption damper which concerns on the Example of this invention Side view of the damper part provided in the damper Perspective view of the damper part Sectional drawing of the torque fluctuation absorption damper which concerns on the other Example of this invention. Half cut sectional view of torque fluctuation absorbing damper according to conventional example Sectional view of torque fluctuation absorbing damper according to comparative example

The present invention includes the following embodiments.
(1) The present invention relates to a torque fluctuation absorbing damper (decoupled damper pulley).
(2) a damper portion having a hub fixed to a drive shaft (rotary shaft), an annular vibration ring connected to the hub via an elastic rubber (damper rubber), a sleeve fixed to the hub, Assuming a torque fluctuation absorbing damper comprising a coupling part having a pulley connected to the sleeve via an elastic rubber (coupling rubber), and a bearing (dry bearing) that supports the vibration ring and the pulley in the radial direction, This damper is used as a comparative example.
(3) In the damper according to the comparative example described above, the coupling relative amplitude becomes larger than the input amplitude during the period since it passes through the resonance region between the start and stop and the idle speed. Above the idle rotation speed, it is an anti-vibration region, and the coupling relative amplitude is smaller than the input amplitude. Due to the above characteristics, high attenuation is required in the resonance region and low attenuation is required in the vibration isolation region. However, the damper according to the comparative example cannot control attenuation.

(4) Therefore, the following configuration is adopted (added).
(4-1) The vibration ring is divided with respect to the damper according to the comparative example in which the vibration ring is integrated (annular).
(4-2) With respect to the damper according to the comparative example in which a part of the inner diameter of the vibration ring is in contact with the bearing due to the tension of the belt wound around the pulley, the inner diameter of the vibration ring is entirely increased by the elastic force of the elastic rubber (damper rubber). The circumference makes contact with the bearing.
(5) With the above-described configuration, high vibration damping can be obtained because the vibration ring is in contact with the pulley via the bearing at the time of low rotation that is the resonance region. As a result, a large damping can be obtained as compared with the damper according to the comparative example in which the damping by the elastic rubber (coupling rubber) is dominant, and the vibration transmission rate is lowered. Further, since the vibration ring is divided, the vibration ring moves to the outer peripheral side by centrifugal force in the middle / high rotation vibration-proof region. As a result, frictional damping is reduced, and a good vibration isolation effect can be obtained in the vibration isolation region. Further, since friction damping is also added to the damper portion, it is advantageous for the durability of the elastic rubber (damper rubber).

  Next, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 shows a torque fluctuation absorbing damper 1 according to an embodiment of the present invention, and the damper 1 according to this embodiment is configured as follows.

  That is, the damper 1 includes a damper portion (dynamic damper portion / dynamic vibration absorption portion) in which a vibration ring (inertial mass body) 15 is connected to a hub 12 fixed to a rotating shaft (a crankshaft, not shown) via a damper rubber 14. ) 11, and a coupling portion 21 in which a pulley 25 is coupled to the hub 12 via a coupling rubber 24. The pulley 25 is disposed on the inner peripheral side of the vibration ring 15, and the vibration ring 15 and the pulley 25 are A bearing (radial bearing) 31 is interposed therebetween.

  The hub 12 has an inner peripheral cylindrical portion 12a which is a boss portion at the time of attachment, in which a key groove 12b is provided at one place on the circumference of the inner peripheral surface, and one axial direction of the inner peripheral cylindrical portion 12a (in the figure, The end surface portion 12c is integrally formed from the left end to the outer side in the radial direction, and the outer peripheral cylinder portion 12d is integrally formed from the outer peripheral end of the end surface portion 12c to the other axial direction (to the right in the drawing). ing. Although the inner peripheral cylinder part 12a also serves as a boss part at the time of attachment, these may be provided separately.

  The damper portion 11 has a sleeve 13 fitted to the inner peripheral side of the outer peripheral cylindrical portion 12 d of the hub 12, a damper rubber 14 is connected to the inner peripheral side of the sleeve 13, and a vibration ring is connected to the inner peripheral side of the damper rubber 14. 15 are connected. The damper rubber 14 is connected to the sleeve 13, but may be directly connected to the outer peripheral cylindrical portion 12 d of the hub 12.

  The coupling portion 21 has a sleeve 23 fitted to the outer peripheral side of the inner peripheral cylindrical portion 12 a of the hub 12, and a coupling rubber 24 is connected to the outer peripheral side of the sleeve 23, and the outer peripheral side of the coupling rubber 24. A pulley 25 is connected to the shaft. A seal lip 24a is integrally formed on the outer periphery of the coupling rubber 24 in one axial direction, and the seal lip 24a is slidably brought into contact with the end surface portion 12c of the hub 12 (the cup (cup)). Between the ring part 21 and the end surface part 12c of the hub 12) is sealed.

  The pulley 25 has an inner peripheral cylindrical portion 25a connected to the outer peripheral surface of the coupling rubber 24, and the end surface portion 25b is integrally formed radially outward from the other axial end of the inner peripheral cylindrical portion 25a. The outer peripheral cylindrical portion 25c is integrally formed from the outer peripheral end portion of the end surface portion 25b toward the axial direction, and an endless belt (not shown) for various auxiliary machines is wound around the outer peripheral cylindrical portion 25c. A pulley groove 25d is provided. The end surface portion 25b is disposed in a non-contact manner on the outer peripheral cylindrical portion 12d of the hub 12 and the other axial side of the damper portion 11, and the outer peripheral cylindrical portion 25c provided with the pulley groove 25d is further provided on the outer peripheral cylindrical portion 12d of the hub 12. The damper portion 11 is disposed in a non-contact manner on the outer peripheral side. Therefore, the damper portion 11 is surrounded by the end surface portion 12c and the outer peripheral cylindrical portion 12d of the hub 12 and the inner peripheral cylindrical portion 25a and the end surface portion 25b of the pulley 25, thereby providing a damper rubber. Even if 14 is broken, the vibration ring 15 does not jump out of the damper 1 and the dust outside the damper 1 does not easily enter the periphery of the damper portion 11.

  In addition, regarding the positional relationship between the damper portion 11 and the coupling portion 21 (except for the end surface portion 25b of the pulley 25 disposed outside and the outer peripheral cylindrical portion 25c provided with the pulley groove 25d), the damper portion 11 has a cup The coupling portion 21 is disposed in a non-contact manner on the inner peripheral side of the damper portion 11. Further, the vibration ring 15 is arranged in a non-contact manner on the outer peripheral side of the inner peripheral cylinder portion 25a of the pulley 25, and conversely, the inner peripheral cylinder portion 25a of the pulley 25 is arranged in a non-contact manner on the inner peripheral side of the vibration ring 15. Since a radial gap is formed between the vibration ring 15 and the inner peripheral cylinder portion 25a of the pulley 25, an annular or cylindrical bearing (dry bearing, radial bearing) 31 made of a material such as resin is formed in the gap. It is intervened. The vibration ring 15 and the inner peripheral cylindrical portion 25a of the pulley 25 are slidably contacted with the bearing 31 over the entire circumference, but the inner peripheral cylindrical portion 25a of the latter pulley 25 is tensioned by the endless belt. If the pulley 25 is eccentric, the inner peripheral cylindrical portion 25a may come into contact with the bearing 31 partly on the circumference.

  The above configuration is the same as that of the damper 1 according to the comparative example of FIG. 6. Therefore, according to the above configuration, as described above, the level of damping (the magnitude of damping force) cannot be controlled. Therefore, the following configuration is further added to the damper 1 according to this embodiment.

  That is, as shown in FIGS. 2 and 3, the vibration ring 15 is divided into a plurality of divided bodies 15A on the circumference, and specifically, is divided into three divided bodies 15A in three equal parts. A circumferential gap 16 is formed between the adjacent divided bodies 15A. Each of the divided bodies 15A can be displaced in the radial direction while elastically deforming the damper rubber 14. Further, due to the elasticity of the damper rubber 14, each of the divided bodies 15 </ b> A has a structure in which an inner peripheral surface thereof slidably contacts the outer peripheral surface of the bearing 31 over the entire length in the circumferential direction. In addition, an arc-shaped chamfered portion 17 extends over the entire width in the axial direction so that each divided body 15A does not galling the bearing 31 at the circumferential end of the inner peripheral surface of each divided body 15A. Is provided. Although the damper rubber 14 is similarly divided as the vibration ring 15 is divided as described above, the damper rubber 14 may remain annular.

  In the damper 1 to which the above configuration is added, as described above, the inner peripheral cylindrical portion 25a of the pulley 25 is disposed on the inner peripheral side of the vibration ring 15, and between the vibration ring 15 and the inner peripheral cylindrical portion 25a of the pulley 25. The bearing 31 is interposed, and the vibration ring 15 is divided into three divided bodies 15A in a three-dimensional arrangement, and the divided bodies 15A can be displaced in the radial direction while elastically deforming the damper rubber 14, respectively. Further, the vibration ring 15 has a structure in which the divided body 15A is slidably in contact with the outer peripheral surface of the bearing 31 over the entire length in the circumferential direction by the elasticity of the damper rubber 14 in the initial movement posture, that is, the posture when rotation is stopped. Has been.

  Therefore, at the time of low-speed rotation that is the resonance region of the damper 1, the divided bodies 15 </ b> A of the vibration ring 15 are in contact with the inner peripheral cylindrical portion 25 a of the pulley 25 via the bearings 31, so that high friction damping can be obtained. As a result, a large damping can be obtained as compared with the damper according to the comparative example of FIG. 6 in which the damping by the coupling rubber 24 is dominant, and the vibration transmissibility becomes low. Further, since the vibration ring 15 is divided, the divided bodies 15A of the vibration ring 15 are displaced radially outward by centrifugal force at the time of high-speed rotation that is the vibration isolation region of the damper 1, and as a result, friction Attenuation decreases or disappears, and a good vibration isolation effect can be obtained in the vibration isolation region. The frictional damping decreases when the divided body 15A continues to contact the bearing 31 while reducing the contact surface pressure. On the other hand, the contact surface pressure becomes zero or the divided body 15A moves away from the bearing 31. If this happens, the frictional damping temporarily disappears. Therefore, since the high attenuation and the low attenuation are automatically switched according to the situation in this way, it is possible to provide the torque fluctuation absorbing damper 1 that exhibits an excellent attenuation function.

  Further, since the vibration ring 15 is divided into three equal parts, the balance accuracy and handling workability of the damper 1 as a whole can be secured, and the circumferential end of the inner peripheral surface of the divided body 15A is chamfered. Since the portion 17 is provided, the split body 15 </ b> A can be prevented from being galling with respect to the outer peripheral surface of the bearing 31.

  In the above embodiment, a radial bearing is interposed as the bearing 31 between the inner peripheral cylindrical portion 25a of the pulley 25 and the vibration ring 15, but in addition, the thrust bearing is vibrated with the end face portion 25b of the pulley 25. In the example of FIG. 4, a bearing 31 having an L-shaped cross section integrally including a radial bearing portion 31 a and a thrust bearing portion 31 b is provided between the pulley 25 and the vibration ring 15. Intervened in between.

DESCRIPTION OF SYMBOLS 1 Torque fluctuation | variation absorption damper 11 Damper part 12 Hub 12a, 25a Inner peripheral cylinder part 12b Key groove 12c, 25b End surface part 12d, 25c Outer cylinder part 13, 23 Sleeve 14 Damper rubber 15 Vibration ring 15A Divided body 16 Circumferential direction gap 17 Chamfering Part 21 Coupling part 24 Coupling rubber 24a Seal lip 25 Pulley 25d Pulley groove 31 Bearing 31a Radial bearing part 31b Thrust bearing part

Claims (3)

A damper portion in which a vibration ring is connected to a hub fixed to the rotating shaft via a damper rubber; and a coupling portion in which a pulley is connected to the hub via a coupling rubber.
The hub has an inner peripheral cylindrical portion, an end surface portion is integrally formed radially outward from one axial end portion of the inner peripheral cylindrical portion, and the other axial end portion from the outer peripheral end portion of the end surface portion. The outer peripheral cylinder part is integrally molded toward
The damper portion is connected to the damper rubber on the inner peripheral side of the outer peripheral cylindrical portion of the hub, and the vibration ring is connected to the inner peripheral side of the damper rubber,
The coupling part has the coupling rubber connected to the outer peripheral side of the inner peripheral cylindrical part of the hub, and the pulley connected to the outer peripheral side of the coupling rubber,
The pulley has an inner peripheral cylindrical portion connected to the outer peripheral surface of the coupling rubber, and an end surface portion is integrally molded from the other axial end of the inner peripheral cylindrical portion toward the radially outer side, An outer peripheral cylindrical portion is integrally formed from the outer peripheral end portion of the end surface portion toward the one axial direction, and a pulley groove is provided in the outer peripheral cylindrical portion,
The vibration ring is arranged in a non-contact manner on the outer peripheral side of the inner peripheral cylindrical portion of the pulley, and a torque fluctuation absorbing damper in which a bearing is interposed in a radial gap between the vibration ring and the inner peripheral cylindrical portion of the pulley. Because
The vibration ring is divided into a plurality of divided bodies on the circumference, and each divided body is displaceable in a radial direction.
In addition, when the vibration ring is rotated at a low speed, the divided body is slidably contacted with the bearing to generate a frictional damping force due to the sliding. At a high speed rotation, the divided body is out of the radial direction by a centrifugal force. The torque fluctuation absorbing damper is characterized in that the friction damping force is reduced or eliminated by displacing in the direction. The torque fluctuation absorbing damper according to claim 1,
The vibration fluctuation absorbing damper, wherein the vibration ring is divided into three equal parts. The torque fluctuation absorbing damper according to claim 1 or 2,
Torque, characterized in that chamfered portions are provided at circumferential ends of the inner peripheral surface of each divided body of the vibration ring so that each divided body does not cause galling with respect to the bearing. Fluctuation absorbing damper.

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