JP2015140920A - dynamic damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a dynamic damper that is easily and removably attached against a rotating shaft even after assembling a power transmission device and that can attenuate vibration of the rotating shaft in a superior manner while sufficiently avoiding its removal from the rotating shaft at the time of an actual vehicle runs.SOLUTION: A dynamic damper 10 has a first circular arc member 20A and a second circular arc member 20B including each of mass bodies 22A, 22B vibrated at a phase for attenuating vibration of a rotating shaft 14 and each of resilient bodies 24A, 24B for oscillatably supporting the mass bodies 2A, 22B. The first circular arc member 20A and the second circular arc member 20B are removably connected to each other by engaging the engaging parts arranged at end surfaces 26A, 28A, 26B and 28B at each of both circumferential sides so as to form a cylindrical shape enclosing the rotating shaft 14 in a circumferential direction.

Description

  The present invention relates to a dynamic damper that attenuates vibration of a rotating shaft.

  In an engine-driven automobile, power (rotational torque) is transmitted from the engine to the drive wheels via a power transmission device disposed between the reduction gear and the drive wheels. This power transmission device generally includes a constant velocity universal joint arranged at two intervals in the axial direction, and a power transmission shaft (rotary shaft) that transmits torque by connecting the constant velocity universal joints. And.

  A dynamic damper is known as a type of damping device that attenuates the vibration of the rotating shaft. The dynamic damper is a cylindrical body that surrounds a part of the rotation shaft in the circumferential direction, and includes a mass body that vibrates at a phase that attenuates vibration of the rotation shaft, and an elastic body that supports the mass body in a swingable manner. I have. That is, the natural frequency of the dynamic damper is adjusted so as to resonate in conformity with the frequency of the vibration of the rotating shaft to be suppressed. Thereby, the vibration energy of the rotating shaft can be converted into the vibration energy of the dynamic damper and absorbed, that is, the vibration of the rotating shaft can be attenuated.

  By the way, the natural frequency of the dynamic damper needs to be individually set according to the specification of the vehicle type on which the power transmission device is mounted. For this reason, when manufacturing a power transmission device, it is originally desirable that the step of mounting a dynamic damper on a rotating shaft is the final step from the viewpoint of improving production efficiency and reducing the number of stocks. In this case, the manufacturing process until the dynamic damper is attached is common regardless of the specifications of the installed vehicle type. And finally, it is considered that a power transmission device can be efficiently obtained by attaching a dynamic damper according to the specifications of each vehicle model to the rotating shaft.

  Moreover, it is preferable that only the dynamic damper can be easily removed and replaced even after the power transmission device is assembled or after the power transmission device is assembled to the vehicle body or the like. In this case, it is possible to cope with a sudden specification change or the like and to reduce the number of stocks. In addition, the dynamic damper can be easily maintained.

  However, it is not easy to install the dynamic damper on the rotating shaft as a final step and to remove and replace only the dynamic damper from the rotating shaft of the power transmission device. When the cylindrical dynamic damper is attached to the rotating shaft, the rotating shaft is inserted into the cylindrical through hole. In the power transmission device, a constant velocity universal joint is disposed at each of both ends of the rotating shaft while being covered with a boot. Since the outer diameter of these constant velocity universal joints or the like is larger than the inner diameter of the dynamic damper, the dynamic damper cannot be mounted on the rotating shaft after the constant velocity universal joint is assembled.

  Therefore, the step of attaching the dynamic damper to the rotating shaft needs to be performed before the step of connecting the constant velocity universal joint to both ends of the rotating shaft. Further, in the obtained power transmission device, when removing the dynamic damper from the rotating shaft, first, it is necessary to remove at least one of the constant velocity universal joints from the rotating shaft, which requires a large amount of work.

  Therefore, for example, in Patent Document 1, the dynamic damper includes a plurality of members that are detachably fixed to each other so as to be detachable from the rotating shaft even after the power transmission device is assembled. It has been proposed to do. That is, the dynamic damper includes a plurality of arc-shaped members whose mass bodies are covered with an elastic body. When the dynamic damper is mounted on the rotating shaft, a plurality of members are combined to form a cylindrical shape so as to surround the rotating shaft. Then, by covering all or part of the outer periphery of the plurality of members arranged in this way with a housing, a band, or the like, the plurality of members are fixed to the rotating shaft. In addition, tabs or receptacles are respectively formed on the elastic bodies in the adjacent portions of the plurality of members, and by aligning these, it is easy to align the plurality of members. On the other hand, when removing the dynamic damper from the rotating shaft, the above-described housing or the like is removed to release the fixing of the plurality of members to the rotating shaft.

JP 2003-74638 A

  In the dynamic damper composed of a plurality of members described above, since it is necessary to fix the plurality of members to the rotating shaft by the housing, the manufacturing cost increases and the manufacturing process becomes complicated as the housing is provided. Further, since the mass body and the elastic body are covered with the housing, the resonance of the mass body and the elastic body is hindered, and there is a concern that it is difficult to adjust the natural frequency according to the specifications of the mounted vehicle type. In this case, it becomes difficult to sufficiently attenuate the vibration of the rotating shaft to be suppressed.

  In this dynamic damper, the plurality of members are fixed only by the housing. However, since this housing is arranged on the outermost periphery of a plurality of members arranged in a cylindrical shape, it is affected by the centrifugal force due to the rotation of the rotating shaft and the impact caused by contact with stepping stones, fallen trees, etc. during actual vehicle travel. easy. That is, the fixing force by the housing tends to decrease. It is difficult to sufficiently fix a plurality of members only with such a housing, and the dynamic damper may be detached from the rotating shaft.

  The present invention solves this type of problem, and can be easily attached to and detached from the rotating shaft even after the power transmission device is assembled, and is detached from the rotating shaft when the vehicle is running. An object of the present invention is to provide a dynamic damper capable of satisfactorily dampening vibrations of a rotating shaft while sufficiently avoiding this.

To achieve the above object, the present invention provides a dynamic damper for attenuating vibration of a rotating shaft,
An arc-shaped first arc member and a second arc member each including a mass body that vibrates at a phase that attenuates vibration of the rotating shaft and an elastic body that swingably supports the mass body;
The first arc member and the second arc member are cylindrically shaped so as to be detachably connected to each other and to surround the rotating shaft in the circumferential direction by engaging engagement portions provided on both end faces of the circumferential direction. It is characterized by forming.

  In the dynamic damper according to the present invention, a cylindrical shape surrounding the rotating shaft can be formed by bringing both end surfaces in the circumferential direction of the first arc member and the second arc member into contact with each other. At this time, since the meshing portions are provided on the end surfaces that are in contact with each other, the end surfaces are connected in a state where the first arc member and the second arc member are combined in a cylindrical shape, and the dynamic damper is connected to the rotating shaft. Can be worn. That is, the dynamic damper can be attached to the rotating shaft without inserting the rotating shaft through the through hole of the dynamic damper. For this reason, for example, the dynamic damper can be easily attached to the rotating shaft after the constant velocity universal joints and the like are attached to both ends.

  Therefore, for example, when manufacturing a power transmission device in which a dynamic damper is mounted on a rotating shaft, the step of mounting the dynamic damper on the rotating shaft can be a final step. As a result, the manufacturing process until the dynamic damper is attached can be performed in common regardless of the specification of the vehicle model on which the power transmission device is mounted. Then, a dynamic damper having its natural frequency adjusted for each specification of the mounted vehicle type can be mounted on the rotating shaft to obtain a power transmission device. As a result, it is possible to improve the manufacturing efficiency of the power transmission device and reduce useless inventory.

  Moreover, even after the power transmission device is assembled or after the power transmission device is assembled to the vehicle body or the like, only the dynamic damper can be easily removed and replaced with another dynamic damper. As a result, it is possible to cope with a sudden specification change of the vehicle type, and therefore it is possible to reduce the useless inventory of the power transmission device. In addition, the dynamic damper can be easily removed without disassembling the power transmission device attached to the vehicle body. For this reason, maintenance of a dynamic damper etc. can be performed easily.

  Furthermore, this dynamic damper can be mounted on the rotating shaft by connecting the first arc member and the second arc member by the connecting force of the meshing portion. That is, the manufacturing cost can be reduced and the manufacturing efficiency can be improved by simplifying the manufacturing process since the housing and the like can be omitted. Further, since the mass body and the elastic body are not covered with the housing, the natural frequency of the dynamic damper can be adjusted easily and with high accuracy according to the specifications of the mounted vehicle type. Therefore, it is possible to satisfactorily attenuate the vibration to be suppressed of the rotating shaft.

  Moreover, since the end surfaces of the first arc member and the second arc member are connected to each other by the meshing portion as described above, the first arc member and the second arc member exhibit a strong connection force even in the circumferential direction of the cylindrical shape. That is, this dynamic damper is not easily affected by the centrifugal force caused by the rotation of the rotating shaft. Further, since the meshing portion is provided on the end surfaces of the first arc member and the second arc member that are in contact with each other, for example, the outer periphery of the first arc member and the second arc member are compared with the outer periphery of the first arc member and the second arc member. There are few exposed parts on the side, and it is difficult to receive impact from contact objects. Therefore, it is possible to sufficiently suppress the dynamic damper from being detached from the rotating shaft when the vehicle is traveling.

  One of the meshing portions that mesh with each other is preferably a convex portion protruding from the end surface, and the other is a concave portion into which the convex portion is inserted. In this case, since the meshing portion can be easily formed with a simple configuration, the dynamic damper can be reduced in cost and size.

  It is preferable that each of the first arc member and the second arc member is provided with the convex portion on one end face and the concave portion on the other end face among circumferential ends. In this case, the first arc member and the second arc member can have the same shape. Therefore, the number of parts of the dynamic damper can be reduced, and the manufacturing cost can be reduced and the manufacturing process can be simplified.

The convex portion is a ridge extending along the axial direction of the rotating shaft,
The protrusion has a shape in which the width on the distal end side in the protruding direction is larger than that on the proximal end side or a shape in which at least one of both side surfaces along the extending direction is an acute angle with respect to the end surface,
The recess is a groove having a shape that extends along the axial direction starting from at least one of the axial ends of the end surface and meshes with the protrusion,
It is preferable that the protrusion can be inserted into the groove from the starting point by relatively moving the first arc member and the second arc member along the axial direction.

  In this case, the groove and the protrusion can be engaged with each other by inserting the protrusion along the extending direction of the groove. At this time, since the ridge and the groove are formed in the above-described shape, relative movement of the ridge in the depth direction of the groove is suppressed. In other words, relative movement of the second arc member relative to the first arc member in the cylindrical radial direction is suppressed. As a result, the first arc member and the second arc member can be firmly connected with a simple configuration, and the dynamic damper can be more effectively suppressed from being detached from the rotating shaft.

  The length of the protrusion and the groove is shorter than the length of the end surface in the axial direction, until the relative position of the first arc member and the second arc member reaches a connection position. When the protrusion is inserted into the groove, one end surface of the protrusion in the extending direction is preferably in contact with the inner wall surface at the end of the groove in the extending direction.

  In this case, the inner wall surface at the end of the extending direction of the groove serves as a stopper when the protrusion is inserted into the groove. That is, when the first arc member and the second arc member are combined by moving relative to each other in the axial direction, when they form a suitable cylindrical shape and reach a connection position where the fixing force with respect to the rotating shaft is well maintained, One end surface of the ridge contacts the inner wall surface of the groove. As a result, the dynamic damper can be easily and accurately mounted on the rotating shaft.

The first arc member and the second arc member pass through one end surface in the extending direction of the protrusion and the inner wall surface at the end in the extending direction of the groove, and the first arc member and the second arc member. A through hole is formed through each of the arc members in a straight line in the axial direction,
It is preferable to further have a pin that fixes the relative position of the first arc member and the second arc member by being inserted into the through hole.

  In this case, by inserting the pin into the through hole, the first arc member and the second arc member can be more firmly connected, and the relative position of each other can be effectively suppressed from shifting from the connection position. Can do. That is, since it becomes possible to maintain the fixing force with respect to a rotating shaft favorably, it can suppress effectively that a dynamic damper detaches | leaves from a rotating shaft.

  It is preferable that the meshing portion is provided on the mass body. In this case, for example, since the meshing portion is provided for the mass body made of metal and having a rigidity higher than that of the elastic body or the like, the first arc member and the second arc member are more firmly connected. Can do. Thereby, it is possible to more effectively suppress the dynamic damper from being detached from the rotating shaft.

  In this invention, a dynamic damper is comprised from the 1st circular arc member and the 2nd circular arc member in which the meshing part was each provided in the end surface of the circumferential direction. A dynamic damper can be attached to the rotating shaft by combining the first arc member and the second arc member so as to form a cylindrical shape surrounding the rotating shaft and connecting the end faces to each other via the meshing portion. Moreover, the dynamic damper can be removed from the rotating shaft by releasing the meshing of the meshing portion. Thereby, even after the power transmission device is assembled, the dynamic damper can be attached to and detached from the rotating shaft.

  In addition, since the dynamic damper can be fixed to the rotating shaft by the coupling force of the meshing portion, the vibration of the rotating shaft can be satisfactorily suppressed while sufficiently preventing the dynamic damper from detaching from the rotating shaft during actual vehicle travel. Can be attenuated.

It is a principal part schematic block diagram of a power transmission device provided with the dynamic damper which concerns on 1st Embodiment. It is the II-II sectional view taken on the line of FIG. FIG. 3 is an enlarged view of a main part in which a second arc member of the dynamic damper shown in FIG. 1 is omitted. 4A to 4E are enlarged views of main parts showing other examples of the structure of the meshing part. It is a transverse cross section of a power transmission device provided with a dynamic damper concerning a 2nd embodiment. 6A and 6B are flowcharts illustrating a process of mounting the dynamic damper shown in FIGS. 1 and 5 on the rotating shaft in combination with the first arc member and the second arc member. FIGS. 7A and 7B are flowcharts for explaining a process of mounting the dynamic damper according to the third embodiment on the rotating shaft in combination with the first arc member and the second arc member. It is a transverse cross section of a power transmission device provided with a dynamic damper concerning a 4th embodiment. It is the schematic block diagram which looked at the dynamic damper shown in FIG. 8 from radial direction. It is the principal part enlarged view which abbreviate | omitted the 2nd circular arc member of the dynamic damper which concerns on 5th Embodiment.

  Hereinafter, preferred embodiments of a dynamic damper according to the present invention will be described in detail with reference to the accompanying drawings.

  The dynamic damper according to the present invention can be suitably mounted on, for example, a power transmission shaft (rotary shaft) of a power transmission device disposed between a speed reduction device of an automobile and a drive wheel. Therefore, in the present embodiment, a dynamic damper that is detachably attached to the rotating shaft of the power transmission device will be described as an example. First, a schematic configuration of a power transmission device 12 including a dynamic damper 10 according to the first embodiment will be described with reference to FIG.

  The power transmission device 12 includes a rotary shaft 14 to which the dynamic damper 10 is mounted, first axial constant joints 18, which are respectively disposed at both axial ends of the rotary shaft 14 and covered with boots 16 and 17. And a second constant velocity universal joint 19. The dynamic damper 10 is detachably attached to an appropriate position of the rotary shaft 14 between the first constant velocity universal joint 18 and the second constant velocity universal joint 19 in order to attenuate the vibration to be suppressed of the rotary shaft 14. The

  Here, the dynamic damper 10 will be specifically described with reference to FIGS. 2 and 3. 2 is a cross-sectional view taken along the line II-II in FIG. 1, and FIG. 3 is a diagram showing the components of the dynamic damper 10 attached to the rotating shaft 14 with the second arc member omitted. FIG.

  As shown in FIG. 2, the dynamic damper 10 is configured by combining a first arc member 20 </ b> A and a second arc member 20 </ b> B having the same arc shape with each other in a cylindrical shape. The first arc member 20A has a mass body 22A and an elastic body 24A. The mass body 22A has a circular arc shape made of metal, and is vibrated at a phase that attenuates the vibration to be suppressed of the rotary shaft 14 by being supported by the elastic body 24A so as to be swingable. Further, end surfaces 26A and 28A on both sides in the circumferential direction of the mass body 22A are exposed from the elastic body 24A to form both end surfaces in the circumferential direction of the first arc member 20A.

  On one end surface 26A of the mass body 22A, a protrusion 30A protruding from the end surface 26A is formed. As shown in FIG. 2, the protrusion 30A is formed in a shape in which the width W1 on the distal end side in the protruding direction Y is larger than the width W2 on the proximal end side. Further, as shown in FIG. 3, the protrusion 30 </ b> A extends along the axial direction X of the rotating shaft 14 and vertically cuts the end surface 26 </ b> A.

  On the other end face 28A of the mass body 22A, a groove 32A that is recessed from the end face 28A is formed. As shown in FIG. 2, in the groove 32A, the width W3 on the bottom side in the depth direction Y is substantially equal to the width W1 of the protrusion 30A, and the width W4 on the opening side in the depth direction Y of the groove 32A is as described above. It is formed in a shape substantially equal to the width W2 of the protrusion 30A. Further, as shown in FIG. 3, the groove 32 </ b> A extends along the axial direction X so as to longitudinally cut the end surface 28 </ b> A. That is, the groove 32A is formed in a shape that meshes with the protrusion 30A.

  The elastic body 24A is made of rubber or the like, and includes a main body portion 34A, a protruding portion 36A, and a support portion 38A. The main body portion 34A has an arc shape along the outer peripheral surface of the rotating shaft 14, extends longer to one side in the axial direction X than the support portion 38A, and extends to cover a part of the outer peripheral surface of the rotating shaft 14. 35A.

  The protruding portion 36A includes a plurality of protruding portions from the main body portion 34A, and a support portion 38A is formed on the distal end side. The support portion 38A includes the mass body 22A so as to cover the surfaces of the mass body 22A except for the end faces 26A and 28A.

  The second arc member 20B is configured in the same manner as the first arc member 20A. Therefore, each constituent element of the second arc member 20B is denoted by a reference numeral obtained by replacing the end A of the reference numeral attached to the corresponding constituent element of the first arc member 20A with B, and the description thereof is omitted.

  As described above, in the first arc member 20A and the second arc member 20B, the protrusion 30A and the groove 32B mesh with each other, and the protrusion 30B and the groove 32A mesh with each other. That is, there is a meshing portion between the end surface 26A of the first arc member 20A and the end surface 28B of the second arc member 20B, and between the end surface 28A of the first arc member 20A and the end surface 26B of the second arc member 20B. Is formed. By the meshing of these meshing portions, the first arc member 20A and the second arc member 20B are detachably connected to each other to form a cylindrical shape surrounding the rotating shaft 14 in the circumferential direction.

  Further, since the widths W1 to W4 are set as described above in the meshing portion of the dynamic damper 10, the protrusions extend in the depth direction Y (cylindrical radial direction Y) with respect to the grooves 32B and 32A. The relative movement of 30A and 30B is suppressed. That is, the relative movement in the radial direction Y of the first arc member 20A and the second arc member 20B is suppressed, and is prevented from coming off. Accordingly, the first arc member 20A and the second arc member 20B can be firmly connected to each other so as to maintain a cylindrical shape.

  The meshing portion is not limited to the protrusions 30A and 30B and the grooves 32A and 32B as long as it is formed in a shape that can connect the first arc member 20A and the second arc member 20B. For example, as the meshing portion, a convex portion and a concave portion illustrated in the enlarged views of the main part in FIGS. 4A to 4E can be employed. 4A to 4E may be formed on any of the end surfaces 26A, 28A, 26B, and 28B. However, in the following, a convex portion is formed on the end surface 28B, and the end surface 26A. A case where a recess is formed in the case will be described as an example. The directions of the X, Y, and Z axes shown in FIG. 4A are common to FIGS. 4B to 4E.

  In the meshing portion 40 shown in FIG. 4A, a protrusion 42 extending along the axial direction X is provided as a convex portion protruding from the end face 28B. The protrusion 42 is formed in a shape in which the side surface 44 of the both side surfaces 44 and 46 along the extending direction (axial direction X) has an acute angle with respect to the end surface 28B. On the other hand, a groove 48 shaped to mesh with the protrusion 42 is provided as a recess recessed from the end face 26A. In the meshing portion 40, the protrusion 42 and the groove 48 are formed in the above-described shape, so that the relative movement with respect to the radial direction Y is suppressed.

  In the meshing part 50 shown in FIG. 4B, a protrusion 52 extending along the axial direction X is provided as a convex part. As for the protrusion 52, the width | variety of the front end side of the protrusion direction Y is larger than the width | variety of the base end side, and the surrounding surface is formed from the curved surface. On the other hand, a groove 54 having a shape that meshes with the protrusion 52 is provided as a recess. Also in the meshing part 50, the protrusion 52 and the groove | channel 54 are formed in said shape, The relative movement with respect to mutual radial direction Y is suppressed.

  In the meshing part 56 shown in FIG. 4C, a protrusion 58 extending along the axial direction X is provided as a convex part. The ridge 58 is formed in a shape in which the peripheral surface of the ridge 42 in the meshing portion 40 is a curved surface. On the other hand, a groove 59 having a shape that meshes with the protrusion 58 is provided as a recess. Also in the meshing part 56, the protrusion 58 and the groove 59 are formed in the above-described shape, so that relative movement with respect to the radial direction Y is suppressed.

  In the meshing portion 60 shown in FIG. 4D, a protrusion 62 that extends along the axial direction X is provided as a convex portion at the end on the outer peripheral surface side of the mass body 22B. Of both side surfaces along the extending direction of the protrusion 62, the side surface 64 on the outer peripheral surface side is formed integrally with the outer peripheral surface of the mass body 22B. Further, the side surface 66 on the inner peripheral surface side is formed in a shape having an acute angle with respect to the end surface 28B. On the other hand, a groove 68 having a shape that meshes with the protrusion 62 is provided as a recess. That is, the groove 68 has a shape in which the outer peripheral surface of the mass body 22A is cut out. Also in the meshing part 60, the protrusion 62 and the groove 68 are formed in the above-described shape, so that relative movement with respect to the radial direction Y is suppressed. Further, as described above, the side surface 64 of the protrusion 62 can be integrated with the outer peripheral surface of the mass body 22B, and the groove 68 can be formed in a notch shape, so that the configuration of the meshing portion 60 can be further simplified. Is possible.

  In the meshing portion 70 shown in FIG. 4E, a protrusion 72 that extends along the axial direction X is provided as a convex portion at the end on the outer peripheral surface side of the mass body 22B. The ridge 72 is formed in a shape in which the side surface 66 of the ridge 62 in the meshing portion 60 is curved in an S shape. On the other hand, a groove 74 having a shape that meshes with the protrusion 72 is provided as a recess. Also in the meshing portion 70, the protrusion 72 and the groove 74 are formed in the above-described shape, so that relative movement with respect to the radial direction Y is suppressed. Further, the side surface 76 on the outer peripheral side of the protrusion 72 can be integrated with the outer peripheral surface of the mass body 22B, and the groove 74 can be formed in a notch shape, so that the configuration of the meshing portion 70 can be further simplified. It is.

  In the dynamic damper 10 described above, the mass bodies 22A and 22B are formed in the same shape. As a result, the number of parts of the dynamic damper 10 can be reduced, and the manufacturing cost can be reduced and the manufacturing process can be simplified.

  However, for example, like the dynamic damper 78 according to the second embodiment shown in FIG. 5, the mass body 80 of the first arc member 20A and the mass body 82 of the second arc member 20B may have different shapes. . 5 that have the same or similar functions and effects as those shown in FIGS. 1 to 4E among the components shown in FIG. .

  In the mass body 80, the groove 68 is provided as a recess on both of the circumferential end faces 26A, 28A. In the mass body 82, the protrusions 62 are formed as convex portions on both circumferential end surfaces 26B and 28B. Thereby, it is possible to mesh the meshing portions of each other by combining the first arc member 20A and the second arc member 20B.

  In addition, the shape of the convex part and recessed part provided in the mass bodies 80 and 82 is not restricted to said protrusion 62 and the groove | channel 68, It can form in the various shape which can mutually mesh | engage.

  Next, with reference to FIG. 6A and FIG. 6B, a process of attaching the dynamic dampers 10 and 78 to the rotating shaft 14 and its operation and effects will be described. Note that the directions of the X, Y, and Z axes shown in FIG. 6A are common to FIG. 6B. In the following, the process of mounting the dynamic damper 10 on the rotary shaft 14 will be described as an example. However, the dynamic dampers 10 and 78 can be mounted by the same process, and the same operational effects can be obtained. .

  First, as shown in FIG. 6A, the first arc member 20A is approached from one side in the radial direction Y and the second arc member 20B is approached from the other side in the radial direction Y with respect to the rotating shaft 14, The inner peripheral surfaces of the main body portions 34A and 34B are aligned with the outer peripheral surface of the rotary shaft 14. At this time, the ridges 30A and grooves 32A of the first arc member 20A and the grooves 32B and ridges 30B (see FIG. 2) of the second arc member 20B are shifted in relative position with respect to the axial direction X.

  Next, the first arc member 20A and the second arc member 20B are relatively moved along the direction of the arrow shown in FIG. 6A. Accordingly, the ridge 30B can be inserted from one end side in the extending direction (axial direction X) of the groove 32A, and the ridge 30A can be inserted from one end side in the extending direction of the groove 32B.

  Then, as shown in FIG. 6B, until the relative positions of the first arc member 20A and the second arc member 20B in the axial direction X are aligned, that is, by relatively moving each other to the coupling position, the rotating shaft 14 is moved in the circumferential direction. A cylindrical shape is formed to surround. At this time, since the protrusion 30A and the groove 32B are engaged with each other and the groove 32A and the protrusion 30B are engaged with each other, the end surfaces 26A and 28A of the first arc member 20A and the end surfaces 26B and 28B of the second arc member 20B are respectively connected. Can be linked. That is, the first arc member 20A and the second arc member 20B can be fixed to the rotating shaft 14 in a state where the first arc member 20A and the second arc member 20B are combined in a cylindrical shape. In other words, the dynamic damper 10 can be attached to the rotating shaft 14.

  As described above, the dynamic damper 10 can be mounted by moving the first arc member 20A and the second arc member 20B from the radial direction Y relative to the rotating shaft 14 and then relatively moving each of them in the axial direction X. It has become. Thereby, for example, the dynamic damper 10 can be easily mounted on the rotary shaft 14 after the first constant velocity universal joint 18 and the second constant velocity universal joint 19 are attached to both ends.

  Therefore, for example, when the power transmission device 12 is manufactured, the process of mounting the dynamic damper 10 on the rotating shaft 14 can be the final process. As a result, the manufacturing process until the dynamic damper 10 is attached can be performed in common regardless of the specifications of the vehicle model on which the power transmission device 12 is mounted. Then, the power transmission device 12 can be obtained by mounting the dynamic damper 10 whose natural frequency and the like are adjusted for each specification of the mounted vehicle model on the rotating shaft 14. As a result, it is possible to improve the manufacturing efficiency of the power transmission device 12 and reduce wasteful inventory.

  Further, in the dynamic damper 10 mounted on the rotary shaft 14 as described above, the first arc member 20A and the second arc member 20B are moved relative to each other along the axial direction X in the direction away from each other. The meshing of the meshing part can be released. Thereby, the dynamic damper 10 can be easily detached from the rotating shaft 14.

  Thus, even after the power transmission device 12 is assembled or after the power transmission device 12 is assembled to the vehicle body or the like, only the dynamic damper 10 can be easily removed and replaced with another dynamic damper 10. . Therefore, since it is possible to cope with a sudden change in the specifications of the vehicle type, it is possible to reduce the useless inventory of the power transmission device 12. Further, the dynamic damper 10 can be easily removed without attaching the power transmission device 12 to the vehicle body and without disassembling. For this reason, it becomes possible to perform maintenance etc. of the dynamic damper 10 easily.

  Since this dynamic damper 10 can connect the first arc member 20A and the second arc member 20B by the connecting force of the meshing portion, it can be mounted on the rotary shaft 14 without using a housing or the like. . Accordingly, the manufacturing cost can be reduced and the manufacturing process can be simplified and the manufacturing efficiency can be improved by the amount that the housing or the like can be omitted. Further, since the mass bodies 22A and 22B and the elastic bodies 24A and 24B are not covered with the housing, the natural frequency of the dynamic damper 10 can be easily and accurately adjusted according to the specifications of the mounted vehicle type. Therefore, it is possible to satisfactorily attenuate the vibration to be suppressed of the rotating shaft 14.

  The first arc member 20A and the second arc member 20B are connected to each other in the circumferential direction of the cylindrical shape of the dynamic damper 10 because the end surfaces 26A and 28B and the end surfaces 28A and 26B are connected to each other by meshing portions. Demonstrates a strong connection. That is, the dynamic damper 10 is not easily affected by the centrifugal force due to the rotation of the rotating shaft 14.

  As described above, the meshing portion is provided on the end surfaces 26A, 28A, 26B, and 28B of the first arc member 20A and the second arc member 20B that contact each other. For this reason, compared with the housing etc. which are provided in the outermost periphery of the 1st circular arc member 20A and the 2nd circular arc member 20B, for example, there are few parts exposed to an outer peripheral side and it is hard to receive the impact by a contact thing. Accordingly, it is possible to sufficiently suppress the dynamic damper 10 from being detached from the rotating shaft 14 when the vehicle is traveling.

  Further, since the protrusions 30A and 30B and the grooves 32A and 32B are formed in the above-described shape, the second arc member 20B is prevented from moving relative to the first arc member 20A in the cylindrical radial direction Y. Has been. Accordingly, the first arc member 20A and the second arc member 20B can be firmly connected with a simple configuration, and the dynamic damper 10 can be more effectively suppressed from being detached from the rotating shaft 14.

  Furthermore, as described above, the end surfaces 26A, 28A, 26B, and 28B of the mass bodies 22A and 22B are exposed from the elastic bodies 24A and 24B to form the circumferential end surfaces of the first arc member 20A and the second arc member 20B. ing. The end surfaces 26A, 28A, 26B, and 28B are provided with meshing portions. Thus, since the first arc member 20A and the second arc member 20B are connected by the meshing portions provided on the mass bodies 22A and 22B made of metal having relatively high rigidity, the mutual connecting force is improved. be able to. Accordingly, it is possible to more effectively suppress the dynamic damper 10 from being detached from the rotating shaft 14.

  Next, the dynamic damper 84 according to the third embodiment will be described with reference to FIGS. 7A and 7B. 7A and 7B are flowcharts for explaining a process of mounting the dynamic damper 84 on the rotating shaft 14 by combining the first arc member 20A and the second arc member 20B. Of the components shown in FIGS. 7A and 7B, those having the same or similar functions and effects as the components shown in FIGS. Is omitted. In addition, the directions of the X, Y, and Z axes shown in FIG. 7A are common to FIG. 7B.

  In the dynamic damper 84, the mass body 22A of the first arc member 20A among the constituent elements of the dynamic damper 10 includes a protrusion 86A and a groove (not shown) instead of the protrusion 30A and the groove 32A. Further, the mass body 22B of the second arc member 20B includes a not-shown protrusion and groove 88B in place of the protrusion 30B and the groove 32B. The groove (not shown) is configured in the same manner as the groove 88B provided in the mass body 22B, and the protrusion (not shown) is configured in the same manner as the protrusion 86A provided in the mass body 22A. These descriptions are omitted.

  The groove 88B is configured in the same manner as the groove 32B, except that the extending length is shorter than the groove 32B that longitudinally cuts the end face 28B along the axial direction X. That is, the groove 88B extends from one end of the end face 28B in the axial direction X as a starting point, and has a position that does not reach the other end of the end face 28B as an end point. For this reason, the inner wall surface 90B faces the end of the groove 88B in the extending direction.

  On the other hand, the protrusion 86A is configured in the same manner as the protrusion 30A and meshes with the groove 88B except that the extending length is shorter than the protrusion 30A that vertically cuts the end face 26A along the axial direction X. Is formed. Further, the extending length of the protrusion 86A is substantially equal to the extending length of the groove 88B.

  In the illustration of FIGS. 7A and 7B, the groove 88B and the protrusion 86A extend from one end of the end surfaces 26A and 28B on the right side in the X-axis direction, but the end surfaces 26A and 28B extend in the X-axis direction. The other end on the left side of the page may be the starting point.

  When the dynamic damper 84 configured as described above is mounted on the rotating shaft 14, first, the inner peripheral surfaces of the main body portions 34 </ b> A and 34 </ b> B are made to run along the outer peripheral surface of the rotating shaft 14 as shown in FIG. 7A. Under the present circumstances, it arrange | positions so that the one end surface 92A of the extending direction of 86 A of protrusions may oppose the starting point side of the groove | channel 88B. Then, the first arc member 20A and the second arc member 20B are relatively moved along the axial direction X in a direction approaching each other. Thereby, the ridge 86A can be inserted from the starting point side of the groove 88B.

  Then, as shown in FIG. 7B, when the protrusion 86A is inserted into the groove 88B until the relative position of the first arc member 20A and the second arc member 20B reaches the coupling position, the extending direction of the protrusion 86A One end surface 92A of the first end surface abuts against the inner wall surface 90B at the end in the extending direction of the groove 88B. That is, the inner wall surface 90B serves as a stopper when the protrusion 86A is inserted into the groove. Accordingly, the first arc member 20A and the second arc member 20B can be easily aligned so as to form a cylindrical shape surrounding the rotation shaft 14 in the circumferential direction. Accordingly, the dynamic damper 84 can be easily and accurately mounted on the rotating shaft 14.

  In the dynamic damper 84, among the constituent elements of the dynamic damper 78 (see FIG. 5), the mass body 80 includes a groove 88B instead of the groove 68, and the mass body 82 replaces the protrusion 62 and the protrusion 86A. It is good also as a structure provided with.

  Next, a dynamic damper 94 according to the fourth embodiment will be described with reference to FIGS. 8 and 9. FIG. 8 is a cross-sectional view taken along the line II-II of FIG. 1 in the power transmission device 12 provided with a dynamic damper 94 instead of the dynamic damper 10. FIG. 9 is a schematic configuration diagram of the dynamic damper 94 mounted on the rotating shaft 14 as viewed from the radial direction Z. 8 and FIG. 9 that have the same or similar functions and effects as those shown in FIG. 1 to FIG. 7B are given the same reference numerals and are described in detail. Is omitted.

  In the dynamic damper 94, among the components of the dynamic damper 78 described above, the mass body 80 includes a protrusion 96 instead of the groove 68, and the mass 82 includes a groove 98 instead of the protrusion 62.

  The protrusion 96 is configured in the same manner as the protrusion 86A described above except that the through hole 100 is formed along the axial direction X. The groove 98 is configured in the same manner as the groove 88B.

  The through hole 100 further passes through the second arc member 20B through the inner wall surface 90B facing the end of the groove 98 in the extending direction. That is, the through-hole 100 passes through the end surface 92A in the extending direction of the protrusion 96 and the inner wall surface 90B at the end in the extending direction of the groove 98, and passes through each of the first arc member 20A and the second arc member 20B. It penetrates in a straight line in the axial direction X. As will be described later, a split pin (pin) 102 (see FIG. 9) is inserted into the through hole 100.

  In the illustration of FIG. 9, the groove 88B and the ridge 86A extend from one end of the end surfaces 26A and 28B on the left side in the X-axis direction, but the right side of the end surfaces 26A and 28B on the right side in the X-axis direction. The other end may be the starting point.

  The dynamic damper 94 configured in this manner is first formed into a cylindrical shape surrounding the rotating shaft 14 by combining the first arc member 20A and the second arc member 20B, as with the dynamic damper 84 described above. That is, the protrusion 86A is inserted from the start point side of the groove 88B, and the one end surface 92A is brought into contact with the inner wall surface 90B, whereby the relative position between the first arc member 20A and the second arc member 20B is set as the connection position.

  Next, as shown in FIG. 9, with the split pin 102 inserted through the through hole 100, the tip end side of the split pin 102 is bent in a direction substantially orthogonal to the extending direction of the through hole 100. Accordingly, the first arc member 20A and the second arc member 20B can be more firmly connected, and the relative positions of each other can be effectively suppressed from shifting from the connection position. That is, since it becomes possible to maintain the fixing force with respect to the rotating shaft 14 favorably, it is possible to effectively suppress the dynamic damper 94 from being detached from the rotating shaft 14.

  The dynamic damper 94 has a configuration in which the mass bodies 22A and 22B include the protrusions 86A and the grooves 88B instead of the protrusions 30A and 30B and the grooves 32A and 32B among the components of the dynamic damper 10 described above. Also good.

  In the illustration of FIG. 8, in the dynamic damper 94, the through holes 100 are formed at both circumferential ends of the first arc member 20 </ b> A and the second arc member 20 </ b> B, and the split pins 102 are inserted. However, the through hole 100 may be formed only on one end side in the circumferential direction of the first arc member 20A and the second arc member 20B, and the split pin 102 may be inserted.

  In the above dynamic dampers 10, 78, 84, 94, it is possible to fix the rotating shaft 14 sufficiently firmly by meshing of the meshing portions provided in the mass bodies 22A, 22B, 80, 82. In order to further improve the fixing force with respect to 14, a band (not shown) may be attached to the extending portions 35A and 35B.

  Next, a dynamic damper 104 according to the fifth embodiment will be described with reference to FIG. FIG. 10 is an enlarged view of a main part in which the second arc member 20B of the dynamic damper 104 is omitted. 10 that have the same or similar functions and effects as those shown in FIG. 1 to FIG. 9 are given the same reference numerals, and detailed descriptions thereof are omitted. .

  The dynamic damper 104 includes elastic bodies 106A and 106B in place of the elastic bodies 24A and 24B among the components of the dynamic dampers 10, 78, 84, and 94 described above. The elastic body 106B has the same configuration as that of the elastic body 106A, and thus the description thereof is omitted.

  The elastic body 106A includes a main body portion 108A instead of the main body portion 34A of the elastic body 24A. The main body portion 108A has an arc shape along the outer peripheral surface of the rotating shaft 14, and the length in the axial direction X is formed in substantially the same manner as the support portion 38A. The fixing member 110A is included so as to cover the surfaces excluding the end faces 112A and 114A on both sides in the circumferential direction of the arc-shaped fixing member 110A made of metal.

  Engaging portions are formed on the end surfaces 112A and 114A of the fixing member 110A in the same manner as the end surfaces 26A and 28A of the mass body 22A. That is, for example, a protrusion 116A is formed on the end surface 112A similarly to the protrusion 30A, and a groove 118A is formed on the end surface 114A similarly to the groove 32A.

  With the configuration as described above, the dynamic damper 104 can fix the first arc member 20A and the second arc member 20B by the fixing members 110A and 110B in addition to the mass bodies 22A and 22B. Become. As a result, the dynamic damper 104 can be more firmly attached to the rotating shaft 14 without providing the band.

  The present invention is not particularly limited to the above-described embodiment, and various modifications can be made without departing from the scope of the invention.

  For example, the periphery of the through hole 100 after the split pin 102 is inserted may be covered with a small piece sheet body or the like. In this case, since water or the like can be prevented from entering the elastic bodies 24A, 24B, 106A, and 106B, corrosion of the mass bodies 22A, 22B, 80, and 82 is prevented, and the durability of the dynamic damper 94 is increased. Can be improved.

DESCRIPTION OF SYMBOLS 10, 78, 84, 94, 104 ... Dynamic damper 12 ... Power transmission device 14 ... Rotating shaft 16, 17 ... Boot 18 ... 1st constant velocity universal joint 19 ... 2nd constant velocity universal joint 20A ... 1st circular arc member 20B ... Second arc member 22A, 22B, 80, 82 ... Mass bodies 24A, 24B, 106A, 106B ... Elastic bodies 26A, 26B, 28A, 28B, 112A, 114A ... End faces 30A, 30B, 42, 52, 58, 62, 72 , 86A, 96, 116A ... Projections 32A, 32B, 48, 54, 59, 68, 74, 88B, 98, 118A ... Grooves 34A, 34B, 108A ... Body portions 35A, 35B ... Extension portions 36A, 36B ... Projections Part 38A, 38B ... support part 40, 50, 56, 60, 70 ... meshing part 44, 46, 64, 66, 76 ... side face 90B ... inner wall surface 92A ... one end face 10 ... through holes 102 ... split pins 110A, 110B ... fixing member

Claims (7)

A dynamic damper that attenuates vibration of the rotating shaft,
An arc-shaped first arc member and a second arc member each including a mass body that vibrates at a phase that attenuates vibration of the rotating shaft and an elastic body that swingably supports the mass body;
The first arc member and the second arc member are cylindrically shaped so as to be detachably connected to each other and to surround the rotating shaft in the circumferential direction by engaging engagement portions provided on both end faces of the circumferential direction. Dynamic damper characterized by forming The dynamic damper according to claim 1,
One of the meshing portions that mesh with each other is a convex portion protruding from the end face, and the other is a concave portion into which the convex portion is inserted. The dynamic damper according to claim 2,
Each of the first arc member and the second arc member is characterized in that the convex portion is provided on one end face and the concave portion is provided on the other end face of both ends in the circumferential direction. Dynamic damper. The dynamic damper according to claim 2 or 3,
The convex portion is a ridge extending along the axial direction of the rotating shaft,
The protrusion has a shape in which the width on the distal end side in the protruding direction is larger than that on the proximal end side or a shape in which at least one of both side surfaces along the extending direction is an acute angle with respect to the end surface,
The recess is a groove having a shape that extends along the axial direction starting from at least one of the axial ends of the end surface and meshes with the protrusion,
The dynamic damper, wherein the protrusion can be inserted into the groove from the starting point by relatively moving the first arc member and the second arc member along the axial direction. The dynamic damper according to claim 4, wherein
The length of the protrusion and the groove extending is shorter than the axial length of the end surface, until the relative position of the first arc member and the second arc member reaches the connection position, When the ridge is inserted into the groove, one end surface of the ridge in the extending direction comes into contact with an inner wall surface at the end of the groove in the extending direction. The dynamic damper according to claim 5,
The first arc member and the second arc member pass through one end surface in the extending direction of the protrusion and the inner wall surface at the end in the extending direction of the groove, and the first arc member and the second arc member. A through hole is formed through each of the arc members in a straight line in the axial direction,
The dynamic damper further comprising a pin that fixes the relative position of the first arc member and the second arc member by being inserted into the through hole. In the dynamic damper according to any one of claims 1 to 6,
The dynamic damper, wherein the meshing portion is provided on the mass body.

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