JP2021060063A - Torsional vibration reduction device - Google Patents

Abstract

To provide a torsional vibration reduction device which can improve a yield of a material of the device as a whole.SOLUTION: In a torsional vibration reduction device 1 which comprises a planetary rotation mechanism 18 for performing a differential action by a center rotation element S, a ring rotation element R and a carrier rotation element C for holding a planetary rotation element P, and in which one of the rotation elements S, C and R is set as one of input elements S, C and R, the other one of the rotation elements S, C and R is set as one of output elements S, C and R, another one of the rotation elements S, C and R is set as one of inertia elements S, C and R, the input elements S, C and R and the output elements S, C and R are connected to each other via an elastic body 20, and an additional inertia body 19 is added to the inertial elements S, C and R, at least either of the inertia elements S, C and R and the additional inertial body 19 is formed of a plurality of split pieces 19s, Rs which are split in a circumferential direction, and the split pieces 19s, Rs are connected to each other in the circumferential direction, thus forming the annular bodies S, C, R and 19.SELECTED DRAWING: Figure 4

Description

The present invention relates to a torsional vibration reducing device configured to reduce torsional vibration caused by fluctuation (vibration) of input torque.

An example of this type of device is described in Patent Document 1. The device includes a planetary gear mechanism, the carrier of the planetary gear mechanism is an input element, the sun gear is an output element, and the ring gear is a reaction force element or a pendulum element integrated with an inertial mass body. The inertial mass is a ring-shaped side plate, which is arranged on both sides of the ring gear in the axial direction and is riveted to the ring gear. Further, a spring damper is provided in parallel with the planetary gear mechanism. The spring damper is an input member that rotates when torque is transmitted from a driving force source such as an engine, an output member that is provided concentrically with the input member and outputs torque to the output shaft, and inputs in the torque transmission direction. It has an intermediate member arranged between the member and the output member. The input member and the intermediate member are rotatably connected to each other via the first elastic body, and the intermediate member and the output member are rotatably connected to each other via the second elastic body. The input member and the carrier in this spring damper are connected, and the output member and the sun gear are connected. That is, the carrier and the sun gear are connected via a spring damper. Then, when torque is transmitted to the input member, a load is applied to the output member by a transmission, a drive wheel, or the like, so that a load for compressing the first elastic body and the second elastic body is generated, and the input member and the output member are output. The member rotates relative to each other. At the same time, relative rotation between the sun gear and the carrier occurs. In a state where the torque transmitted between the input member and the output member is stable, the input member and the output member are maintained in a twisted state of being rotated by a predetermined angle, and the sun gear and the carrier are rotated by a predetermined angle. Maintain a twisted state. When the input torque vibrates, the above-mentioned load changes and the first elastic body and the second elastic body expand and contract. That is, relative rotation occurs between the input member and the output member, and at the same time, relative rotation occurs between the carrier and the sun gear. Along with this, the ring gear is forcibly rotated, the inertial torque of the ring gear acts as a resistance to the vibration of the engine torque, and the vibration of the torque output from the torsional vibration reducing device is reduced.

International Publication No. 2016/208767

In the device described in Patent Document 1, since the side plate rotates integrally with the ring gear, it is a ring-shaped integrated product in order to avoid vibration due to the center of gravity of the side plate deviating from the rotation center axis of the planetary gear mechanism. Is preferable. In order to form the above-mentioned side plate into a ring-shaped integral product, for example, it is preferable to punch the side plate from a flat plate-shaped material. However, when the ring-shaped side plate is punched out from the flat plate-shaped material, the portion of the flat plate-shaped material other than the side plate becomes scrap, so that the yield of the material deteriorates.

The present invention has been made by paying attention to the above technical problems, and an object of the present invention is to provide a torsional vibration reducing device capable of improving the material yield of the device as a whole.

In order to achieve the above object, the present invention includes a central rotating element, a ring rotating element arranged concentrically with respect to the central rotating element, and an outer peripheral portion of the central rotating element and the ring rotating element. A differential action is performed by a carrier rotating element that is arranged between the peripheral portion and holds a plurality of planetary rotating elements that rotate and revolve as the central rotating element and the ring rotating element rotate relative to each other. A planetary rotation mechanism is provided, and any one of the center rotation element, the ring rotation element, and the carrier rotation element is an input element to which torque is input, and the center rotation element, the ring rotation element, and the carrier are used. Any other one of the rotating elements is an output element that outputs the torque, and any one of the central rotating element, the ring rotating element, and the carrier rotating element is the input element. The input element and the output element are connected to the output element via an elastic body so as to be relatively rotatable at a predetermined angle, and an additional inertial body is added to the inertial element. In the added torsional vibration reducing device, at least one of the inertial element and the additional inertial body is formed by a plurality of divided pieces divided in the circumferential direction of the planetary rotation mechanism, and the divided pieces are formed from each other. Are connected to each other in the circumferential direction to form an annular body.

In the present invention, the divided pieces are fitted to each other in the circumferential direction by at least one of the fitting of the ends of the divided pieces facing each other in the circumferential direction and the welding of the ends to each other. It may be connected.

In the present invention, the connecting portion between the divided pieces may be a portion deviating from the angular range in which the planetary rotating element reciprocates due to the vibration of the torque in the circumferential direction.

In the present invention, the additional inertial body is formed by a plurality of the divided pieces divided in the circumferential direction, and the planetary rotation mechanism is in a state where the divided pieces are connected to each other in the circumferential direction. It may be integrally attached to the side surface of the inertial element in the axial direction of the above by a fixing means.

In the present invention, the input element is one of the central rotating element and the carrier rotating element, and the output element is the other of the central rotating element and the carrier rotating element. The inertial element may be the ring rotating element.

In the present invention, in the planetary rotating mechanism, the central rotating element is composed of a sun gear, the ring rotating element is composed of a ring gear, the planet rotating element is composed of a pinion gear, and the carrier rotating element holds the pinion gear. It may be a planetary gear mechanism composed of the carriers.

According to the present invention, at least one of the inertial element and the additional inertial body is formed by being divided into a plurality of divided pieces in the circumferential direction of the planetary rotation mechanism, and the divided pieces are formed in the circumferential direction. They are connected to form an annular body. These divided pieces are formed by punching, for example, a flat material. Therefore, as compared with the case where a flat plate-shaped material is punched out to form an integral product of the inertial element of the annular body and the additional inertial body, the scrap portion can be reduced, and the yield of the material can be improved. Further, this can reduce the material cost.

It is a skeleton figure which shows typically an example of the torsional vibration reduction apparatus which concerns on 1st Embodiment of this invention. It is a front view which shows typically an example of the torsional vibration reduction apparatus shown in FIG. It is sectional drawing which shows a part of the torsional vibration reduction apparatus shown in FIG. 1 schematically. It is a figure which shows typically an example of the inertial mass body in 1st Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the inertial mass body in 2nd Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the inertial mass body in 3rd Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the inertial mass body in 4th Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the inertial mass body in 5th Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the inertial mass body in 6th Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the inertial mass body in 7th Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the inertial mass body in 8th Embodiment of this invention. It is a front view of the connecting part shown in FIG. It is sectional drawing which shows a part of the inertial mass body in the 9th Embodiment of this invention schematically. It is sectional drawing which shows typically a part of the inertial mass body in 10th Embodiment of this invention. It is a figure which shows typically an example of the ring gear in eleventh embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the ring gear in the twelfth embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the ring gear in 13th Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the ring gear in 14th Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the ring gear in 15th Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the ring gear in the 16th Embodiment of this invention. It is a figure which shows typically the connecting part of each division piece of the ring gear in 17th Embodiment of this invention. It is a skeleton figure which shows typically an example of the torsional vibration reduction apparatus which concerns on 18th Embodiment of this invention. It is sectional drawing which shows typically an example of the torsional vibration reduction apparatus which concerns on 19th Embodiment of this invention. It is sectional drawing which shows typically an example of the torsional vibration reduction apparatus which concerns on 20th Embodiment of this invention.

(First Embodiment)
FIG. 1 is a skeleton diagram schematically showing an example of the torsional vibration reducing device according to the first embodiment of the present invention, and FIG. 2 is a front view schematically showing a part of the torsional vibration reducing apparatus shown in FIG. Yes, FIG. 3 is an enlarged cross-sectional view showing a part of the torsional vibration reducing device 1 shown in FIG. The torsional vibration reducing device 1 shown here is inside the torque converter 2 and is provided in a torque transmission path between the driving force source 3 and the driving target unit 4, and the torque generated by the driving force source 3 is provided. It is configured to reduce the vibration of the engine and transmit it to the drive target unit 4. The driving force source 3 is, for example, an internal combustion engine such as a gasoline engine or a diesel engine (hereinafter, simply referred to as an engine). Therefore, the output torque (hereinafter referred to as engine torque) inevitably vibrates. The drive target unit 4 is, for example, a transmission, and the transmission is conventionally known as a stepped transmission in which the gear ratio changes stepwise, or a continuously variable transmission in which the gear ratio continuously changes. It may be a transmission.

The torque converter 2 has the same configuration as that conventionally known, and the housing 5 of the torque converter 2 is integrated with the front cover 6 connected to the output shaft 3a of the engine 3 and the front cover 6. It is formed in a liquid-tight state by the pump shell 7 and the pump shell 7. A fluid (oil) that transmits torque is sealed inside the housing 5. A plurality of pump blades 8 are attached to the inner surface of the pump shell 7 to form a pump impeller 9. A turbine runner 10 that rotates in response to the fluid flow generated by the pump impeller 9 is arranged to face the pump impeller 9. The turbine runner 10 is connected to the input shaft 4a of the transmission 4 via the turbine hub 11.

A stator 12 is arranged between the pump impeller 9 and the turbine runner 10. The stator 12 is attached to a fixed shaft (not shown) in the torque converter 2 via a one-way clutch 13. When the speed ratio between the pump impeller 9 and the turbine runner 10 is small, the stator 12 changes the flow direction of the oil flowing out from the turbine runner 10 and supplies it to the pump impeller 9, and when the speed ratio is large, the stator 12 is supplied from the turbine runner 10. It is configured so that the flow direction of the oil is not changed by being pushed by the flowing oil and rotating.

The lockup clutch 14 is arranged so as to face the inner surface of the front cover 6. The lockup clutch 14 shown in FIG. 1 is a multi-plate clutch, and covers, for example, a plurality of clutch discs 15 spline-fitted to a clutch hub integrated with a front cover 6 and an outer peripheral side of the clutch hub. A plurality of clutch plates 17 that are spline-fitted to the inner peripheral surface of the clutch drum 16 arranged in the above and are alternately arranged with the clutch disc 15 are provided. These clutch discs 15 and clutch plates 17 are alternately arranged between a lockup piston (not shown) and a snap ring (not shown) attached to the clutch drum 16. Therefore, when the lockup piston advances and sandwiches the clutch disc 15 and the clutch plate 17 between the snap ring, the clutch disc 15 and the clutch plate 17 come into frictional contact with each other, and torque is transmitted between the two. .. That is, the lockup clutch 14 is in an engaged state in which torque is transmitted. A return spring (not shown) is arranged alongside at least a part of the lockup clutch 14 on the inner peripheral side of the lockup clutch 14 in the radial direction of the torque converter 2. The return spring presses the lockup piston in the direction of releasing the lockup clutch 14, that is, in the direction of separating the clutch disc 15 and the clutch plate 17.

The torsional vibration reducing device 1 is arranged adjacent to the lockup clutch 14 in the direction of the rotation center axis of the torque converter 2 (hereinafter, simply referred to as the axis direction). The torsional vibration reducing device 1 includes a planetary rotation mechanism and an elastic body according to the embodiment of the present invention. The planetary rotation mechanism is basically a mechanism that performs a differential action by three rotating elements such as a planetary gear mechanism and a planetary roller mechanism, and in the example shown here, it is composed of a single pinion type planetary gear mechanism 18. The planetary gear mechanism 18 includes a sun gear S, a ring gear R arranged concentrically with respect to the sun gear S, and a carrier C for rotatably holding a plurality of pinion gears P meshing with the sun gear S and the ring gear R as rotating elements. ing. In the example shown in FIG. 1, the carrier C is connected to the output shaft 3a of the engine 3 via the lockup clutch 14, and the sun gear S is connected to the drive target portion 4. An inertial mass body 19 is integrally attached to the ring gear R. Therefore, in the example shown in FIG. 1, the carrier C described above corresponds to the carrier rotating element and the input element in the embodiment of the present invention, and the sun gear S corresponds to the central rotating element and the output element in the embodiment of the present invention. , The ring gear R corresponds to the ring rotating element and the inertial element in the embodiment of the present invention, and the inertial mass body 19 corresponds to the additional inertial body in the embodiment of the present invention.

The inertial mass body 19 rotates integrally with the ring gear R to increase the inertial torque generated by the ring gear R. In the example shown here, as shown in FIG. 3, the inertial mass body 19 is configured in a ring shape having substantially the same outer diameter as the ring gear R, and is configured as a separate product from the ring gear R. Inertial mass bodies 19 are arranged on both sides of the ring gear R in the axial direction, and are riveted to the ring gear R so as to rotate integrally with the ring gear R. That is, rivet holes (not shown) for riveting the inertial mass body 19 are formed at regular intervals in the circumferential direction of the ring gear R. In the example shown here, the ring gear R may be a so-called integrated product formed by punching a flat plate-shaped material into a ring shape. Alternatively, a so-called rack in which teeth are formed on a strip-shaped or flat plate-shaped member may be curved in a ring shape, and both ends of the rack may be connected to each other by welding. The configuration of the inertial mass body 19 will be described later.

In the example shown here, a spring damper 20 corresponding to an elastic body according to the embodiment of the present invention is provided in parallel with the planetary gear mechanism 18. Further, as shown in FIGS. 2 and 3, the spring damper 20 is arranged on the inner peripheral side of the planetary gear mechanism 18 in the radial direction of the torsional vibration reducing device 1 so as to be concentrically aligned with the planetary gear mechanism 18. .. Here, "side by side" means a state in which at least a part of each of the spring damper 20 and the planetary gear mechanism 18 overlaps in the radial direction. As shown in FIG. 1, the spring damper 20 has a drive plate 21 arranged on the upstream side in the engine torque transmission direction, a driven plate 22 arranged on the downstream side of the drive plate 21 in the engine torque transmission direction, and a drive. A coil spring 23 that connects the plate 21 and the driven plate 22 so as to be relatively rotatable is provided. The carrier C of the planetary gear mechanism 18 is connected to the drive plate 21, and the sun gear S is connected to the driven plate 22. Therefore, the drive plate 21 described above also serves as the carrier C.

As shown in FIG. 3, the drive plate 21 is composed of an annular first drive plate 21A having substantially the same outer diameter and an annular second drive plate 21B. Further, the drive plates 21A and 21B are arranged at predetermined intervals in the axial direction. The first drive plate 21A is arranged on the engine 3 side in the axial direction, and the second drive plate 21B is arranged on the drive target portion 4 side. A planetary gear mechanism 18 and a driven plate 22 are arranged between the drive plates 21A and 21B in the axial direction. The drive plates 21A and 21B are symmetrically formed with the driven plate 22 interposed therebetween. Pinion pins 24 are attached to the outer portions of the drive plates 21A and 21B in the radial direction, and pinion gears P are rotatably attached to the outer peripheral side of the pinion pins 24 via bearings 25 such as needle bearings. Further, thrust washers 26 having an outer diameter slightly larger than the pitch circle diameter of the pinion gear P are provided on both sides of the pinion gear P in the axial direction.

Driven plates 22 are arranged downstream of the drive plates 21A and 21B in the engine torque transmission direction and between the drive plates 21A and 21B in the axial direction. The driven plate 22 is formed in an annular shape as a whole. External teeth are formed on the outer peripheral surface of the driven plate 22, and the external teeth are the sun gear S of the planetary gear mechanism 18. The inner peripheral portion of the driven plate 22 is connected to the turbine hub 11 described above.

Further, as shown in FIGS. 2 and 3, the window hole portion 27 in which the coil spring 23 is arranged at the same radial position in the inner portion of the drive plates 21A and 21B and the inner portion of the driven plate 22 in the radial direction. Are formed respectively. The coil spring 23 is arranged inside each window hole 27 in a state where the window hole 27 of the drive plates 21A and 21B and the window hole 27 of the driven plate 22 are overlapped with each other. The coil springs 23 expand and contract in the circumferential direction of the torsional vibration reducing device 1 due to the relative rotation of the drive plates 21A and 21B and the driven plates 22.

Here, the configuration of the inertial mass body 19 described above will be described. FIG. 4 is a diagram schematically showing an example of the inertial mass body 19. The inertial mass body 19 shown in FIG. 4 includes a plurality of divided pieces 19s having an arc shape having a constant curvature and having the same shape, and in a state where the divided pieces 19s are aligned in the circumferential direction, the divided pieces 19s adjacent to each other The ends are connected to each other to form a ring. In the example shown in FIG. 4, the inertial mass body 19 is composed of three divided pieces 19s. The divided pieces 19s can be formed by punching a flat plate-like material (hereinafter referred to as a work) (hereinafter referred to as press molding). When the divided pieces 19s are formed by press molding, the shape of each divided piece 19s may be an arc shape having substantially the same curvature as the curvature of the inertial mass body 19, or may be a strip shape or a flat plate shape. When the shape of the divided pieces 19s formed by press molding is strip-shaped or flat plate-shaped, the strip-shaped or flat-plate-shaped split pieces 19s are curved to have substantially the same curvature as the curvature of the inertial mass body 19.

The divided pieces 19s in the example shown in FIG. 4 are formed in an arc shape having substantially the same curvature as the curvature of the inertial mass body 19, and both end faces of the divided pieces 19s in the length direction are the normal of the inertial mass body 19. It is formed in a plane parallel to the plane containing the line. Then, as described above, when the divided pieces 19s are aligned in the circumferential direction, the end faces of the divided pieces 19s adjacent to each other are brought into contact with each other. In this way, with the end faces facing each other in contact with each other, the joint portion is welded to integrate the divided pieces 19s into a ring shape. The welding method between the divided pieces 19s may be a conventionally known welding method such as arc welding, laser welding, pressure welding, or brazing. Further, in each of the divided pieces 19s, a rivet hole 28 is formed so as to penetrate in the plate thickness direction of the divided piece 19s. Each of the rivet holes 28 is divided so as to be formed at regular intervals in the circumferential direction of the inertial mass body 19 in a state where the divided pieces 19s are connected in the circumferential direction to form the inertial mass body 19. It is formed on a piece 19s. Then, the rivet holes formed in the ring gear R and the rivet holes 28 formed in the inertial mass body 19 are overlapped with each other, and the rivets 29 inserted into the rivet holes 28 are crimped to cause the inertial mass body with respect to the ring gear R. 19 is attached integrally. The inertial mass body 19 described above corresponds to the annular body in the embodiment of the present invention, and the rivet hole 28 and the rivet 29 correspond to the fixing means in the embodiment of the present invention.

Further, the position of the connecting portion between the divided pieces 19s with respect to the position of the pinion gear P on the circumference of the ring gear R will be described. First, the position of the pinion gear P on the circumference of the ring gear R will be described. Since the spring damper 20 is provided in the torque transmission path between the engine 3 and the drive target portion 4, the engine torque and the drive target portion 4 are provided. A load for compressing the coil spring 23 of the spring damper 20 is generated by the torsional torque due to the torque for rotating 4, and the coil spring 23 is elastically deformed according to the load. As a result, the sun gear S and the carrier C rotate relative to each other. When the engine torque is large, the torsion torque is large, so that the carrier C and the sun gear S are greatly twisted and the rotation angle of the carrier C with respect to the sun gear S is large. On the contrary, when the engine torque is small, the torsion torque is small, so that the above rotation angle is small. That is, the position of the pinion gear P on the circumference of the sun gear S and the ring gear R and the region α that reciprocates in the circumferential direction change according to the magnitude of the torsional torque. Therefore, in the normal range of engine torque, the position of the pinion gear P on the circumference of the ring gear R, specifically, the rotation angle of the pinion gear P from the assembly position P0 of the pinion gear P, and the pinion gear P in the circumferential direction. The region α in which is reciprocated is almost fixed. The assembly position P0 is when there is no relative twist between the carrier C, which is an input element, and the sun gear S, which is an output element, that is, the carrier C and the sun gear S rotate together. This is the position of the pinion gear P when the pinion gear P is present. Further, the position of the pinion gear P on the circumference of the ring gear R in the normal range of the engine torque and the region α in which the pinion gear P reciprocates in the circumferential direction are mainly in the forward rotation direction of the carrier C. It is on the front side from the assembly position P0. The forward rotation direction described above is the same direction as the rotation direction of the engine 3. Further, the above-mentioned region α corresponds to the angle range in which the planetary rotating element reciprocates in the embodiment of the present invention.

In the embodiment of the present invention, the inertial mass body 19 is attached to the ring gear R so that the connecting portion between the divided pieces 19s is located at a position deviated from the above-mentioned region α in which the pinion gear P reciprocates in the circumferential direction. This is because the inertial mass body 19 is deformed due to the deformation of the ring gear R due to the pinion gear P being pressed against the ring gear R by the centrifugal force, and the load due to the deformation of the inertial mass body 19 is the connecting portion between the divided pieces 19s. This is to avoid the possibility of deteriorating the durability of the connecting portion by acting on the above. Specifically, the inertial mass body 19 is placed on the ring gear R so that the connecting portion between the divided pieces 19s is located on the side opposite to the above-mentioned region α with the assembly position P0 of the pinion gear P sandwiched in the circumferential direction. Install.

Next, the operation of the torsional vibration reducing device 1 according to the first embodiment will be described. The engine 3 is driven, and the torque generated by the engine 3 is input to the carrier C. On the other hand, a torque for rotating the drive target portion 4 acts on the sun gear S. These torques generate a load that compresses the coil spring 23 of the spring damper 20, and elastic deformation corresponding to the load is generated in the coil spring 23. Then, the sun gear S and the carrier C rotate in a twisted state at an angle corresponding to the magnitude of the torsional torque.

The compression force acting on the coil spring 23, that is, the torsional torque, changes due to the vibration of the engine torque, and the torsional rotation of the carrier C and the sun gear S repeatedly occurs. The pinion gear P reciprocates in the circumferential direction within an angle range corresponding to the vibration of the engine torque. That is, the pinion gear P mainly reciprocates in the above region α. Further, the ring gear R is rotated relative to the carrier C and the sun gear S, and vibration is generated in the rotation of the ring gear R. In the above configuration, since the rotation speed of the ring gear R is increased according to the gear ratio with respect to the rotation speed of the sun gear S, the angular acceleration of the ring gear R is increased and the inertial torque of the ring gear R and the inertial mass body 19 is increased. Becomes larger. Further, since there is a phase shift between the vibration of the engine torque input to the carrier C and the vibration of the ring gear R, the above inertial torque acts as a vibration damping torque with respect to the vibration of the engine torque and is input to the carrier C. The generated engine torque is reduced by the inertial torque to be smooth, and is transmitted to the drive target unit 4.

Then, in the torsional vibration reducing device 1 having the above configuration, as described above, a plurality of divided pieces 19s are punched out from the work, and the divided pieces 19s are connected in the circumferential direction to form a ring-shaped inertial mass body 19. To do. Therefore, as compared with the case where the ring-shaped inertial mass body 19 is punched out from the work as an integral product, the scrap portion can be reduced, so that the material yield can be improved and the material cost can be reduced. Further, since the end faces parallel to each other are brought together and their joints are welded, the assembling property is not particularly impaired even if there is a deviation due to the shape tolerance of each of the divided pieces 19s. Further, a connecting portion between the divided pieces 19s is located at a position outside the region α in which the pinion gear P reciprocates. Therefore, as described above, the inertial mass body 19 is deformed due to the deformation of the ring gear R due to the pinion gear P being pressed against the ring gear R by the centrifugal force, and the load due to the deformation of the inertial mass body 19 is applied to the divided pieces 19s. It is possible to avoid or suppress deterioration of the durability of the connecting portion by acting on the connecting portion between the two. Further, the divided pieces 19s are welded to each other, and it is possible to prevent the divided pieces 19s from moving outward in the radial direction due to centrifugal force and exerting an excessive shearing force on the rivet 29. Further, even if a tensile load that separates the divided pieces 19s from each other in the circumferential direction acts on the connecting portion due to centrifugal force, the connected state of the divided pieces 19s can be maintained. That is, the inertial mass body 19 can be regarded as an integral product in terms of strength. Therefore, it is possible to avoid or suppress the deterioration of the durability of the device as a whole.

By the way, in press molding, warpage deformation (curvature) inevitably occurs. That is, in the process of punching the ring-shaped inertial mass body 19 from the work as an integral product, the punch or die bites into the work, and the inertial mass body 19 is in a state of being warped with respect to the work. Then, in that state, the inertial mass body 19 is punched out from the work. Therefore, when the ring-shaped inertial mass body 19 is press-molded as an integral product, the warp deformation of the inertial mass body 19 generated as described above in the press molding process remains in the inertial mass body 19 even after the press molding. there is a possibility. On the other hand, in the torsional vibration reducing device 1 according to the embodiment of the present invention, it is assumed that in the process of punching the divided piece 19s from the work, a punch or a die bites into the work and the divided piece 19s is warped and deformed with respect to the work. However, since the warp deformation is the warp deformation of the split piece 19s with respect to the work, the warp deformation is unlikely to remain in the split piece 19s after press molding. As a result, when a plurality of divided pieces 19s are connected in the circumferential direction to form the inertial mass body 19, warpage deformation of the inertial mass body 19 as a whole can be avoided or suppressed.

(Second Embodiment)
The above-mentioned divided pieces 19s may be connected to each other to such an extent that the inertial mass body 19 can be regarded as an integral product in terms of strength. FIG. 5 is a diagram schematically showing a connecting portion of the divided pieces 19s of the inertial mass body 19 according to the second embodiment of the present invention. The example shown in FIG. 5 is an example in which at least a part of the ends of the divided pieces 19s adjacent to each other in the circumferential direction are overlapped in the radial direction and the joint portions thereof are welded. That is, as shown in FIG. 5, one end surface of the divided piece 19s in the length direction is formed in a plane having an acute angle with the plane including the tangent line of the outer peripheral surface of the inertial mass body 19. The other end face of the split piece 19s in the length direction is formed as an end face parallel to one end face of the above-mentioned split piece 19s. Then, in the same manner as described above, the divided pieces 19s are aligned in the circumferential direction, the end faces of the divided pieces 19s adjacent to each other are brought into contact with each other, and the joint portions thereof are welded and integrated into a ring shape. The inertial mass body 19 is placed on the ring gear R so that the connecting portion between the divided pieces 19s is located on the side opposite to the region α in which the pinion gear P reciprocates with the assembly position P0 of the pinion gear P in the circumferential direction. To install.

In such a configuration, since the seam portion extends in a direction inclined with respect to the radial direction of the inertial mass body 19, the length of the seam portion becomes longer as compared with the first embodiment, and the welding length becomes longer. Becomes longer. Further, even if there is a deviation due to the shape tolerance of each of the divided pieces 19s, the assembling property is not particularly impaired. Therefore, the strength at the connecting portion can be improved as compared with the first embodiment. Further, even in the second embodiment, the same actions and effects as those in the first embodiment can be obtained.

(Third Embodiment)
FIG. 6 is a diagram schematically showing a connecting portion of the divided pieces 19s of the inertial mass body 19 according to the third embodiment of the present invention. The example shown in FIG. 6 is an example in which the ends of the divided pieces 19s adjacent to each other are joined by so-called notched joints and the joints thereof are welded. That is, as shown in FIG. 6, an outer protruding portion 19a protruding in the circumferential direction is formed on the outer portion in the radial direction at one end portion in the length direction of the divided piece 19s. In the radial direction, the inner surface of the outer protrusion 19a, that is, the lower surface of the outer protrusion 19a in FIG. 6, is a plane parallel to the plane including the tangent to the outer peripheral surface of the divided piece 19s. Further, the tip surface of the outer protrusion 19a in the circumferential direction is a plane orthogonal to the plane including the tangent line. An inner protruding portion 19b protruding in the circumferential direction is formed in the inner portion in the radial direction at the other end portion in the length direction of the divided piece 19s. In the radial direction, the outer surface of the inner protrusion 19b, that is, the upper surface of the inner protrusion 19b in FIG. 6, is a plane parallel to the plane including the tangent to the outer peripheral surface of the divided piece 19s. Further, the tip surface of the inner protrusion 19b in the circumferential direction is a plane orthogonal to the plane including the tangent line. Then, in a state where the divided pieces 19s are aligned in the circumferential direction, the outer protruding portion 19a and the inner protruding portion 19b of the divided pieces 19s adjacent to each other are brought into contact with each other. Then, those joints are welded together to form a ring. With such a configuration, since the seam portion has a crank shape, the welding length becomes longer than that of the second embodiment, and the strength of the connecting portion can be further improved. Further, even if there is a deviation due to the shape tolerance of each of the divided pieces 19s, the assembling property is not particularly impaired. Therefore, the same actions and effects as those of the above-described embodiments can be obtained.

(Fourth Embodiment)
FIG. 7 is a diagram schematically showing a connecting portion of the divided pieces 19s of the inertial mass body 19 according to the fourth embodiment of the present invention. The example shown in FIG. 7 is an example in which the ends of the divided pieces 19s adjacent to each other are joined by a so-called mortise and tenon, and the joints thereof are welded. As shown in FIG. 7, a tenon 19c protruding in the circumferential direction is formed at an intermediate portion in the radial direction at one end in the length direction of the divided piece 19s. Both sides of the groove 19c in the radial direction are planes parallel to the plane including the tangent line of the outer peripheral surface of the divided piece 19s, and the tip surface of the groove 19c in the circumferential direction is a plane including the tangent line. It is a plane orthogonal to the plane. A mortise groove 19d into which the tenon 19c fits is formed in a radial intermediate portion at the other end of the split piece 19s. Then, in a state where the divided pieces 19s are aligned in the circumferential direction, the tenons 19c are fitted into the groove 19d, and the divided pieces 19s adjacent to each other are joined to each other to form a ring shape. Further, the joint portions thereof are welded to integrate the divided pieces 19s. With such a configuration, since the joint portions are welded in a state where the divided pieces 19s are connected to each other by fitting, the strength of the connecting portion can be improved as compared with each of the above-described embodiments. In addition, the welding length is longer than that of the third embodiment. This also makes it possible to improve the strength of the connecting portion. Therefore, the same actions and effects as those of the above-described embodiments can be obtained.

(Fifth Embodiment, Sixth Embodiment)
FIG. 8 is a diagram schematically showing a connecting portion of the divided pieces 19s of the inertial mass body 19 according to the fifth embodiment of the present invention. The example shown in FIG. 8 is an example in which the ends of the divided pieces 19s are spliced together by a so-called splicing or the like so as to prevent the divided pieces 19s adjacent to each other from coming off each other in the circumferential direction. That is, in the middle portion in the radial direction at one end in the length direction of the divided piece 19s, the tip portion such as an arrowhead shape or a triangular shape protruding in the circumferential direction extends in the radial direction from the root portion. The portion 19e is formed. A dovetail groove 19f that fits into the dovetail portion 19e is formed in a radial intermediate portion at the other end of the divided piece 19s. Then, in a state where the divided pieces 19s are aligned in the circumferential direction, the divided pieces 19s located in the groove 19f are fitted together, and the divided pieces 19s adjacent to each other are spliced together to form a ring shape. With such a configuration, when a tensile load that separates the divided pieces 19s from each other due to centrifugal force acts on their connecting portions, the jaw portion of the portion 19e located in the groove 19f is caught. The other divided piece 19s can be prevented from coming off with respect to one divided piece 19s. That is, in the fifth embodiment, the strength of the connecting portion can be ensured without welding, and since welding is not performed, the manufacturing cost can be reduced accordingly. If the joint portion of the connecting portion is welded, the strength of the connecting portion can be further improved as compared with each of the above-described embodiments. Therefore, even with such a configuration, the same actions and effects as those of the above-described embodiments can be obtained. Further, the shape of the above-mentioned existing portion 19e may be circular as shown in FIG. 9 as the sixth embodiment instead of the arrowhead shape or the triangular shape shown in FIG. 8 as the fifth embodiment. Even with such a configuration, the same actions and effects as those of the fifth embodiment shown in FIG. 8 can be obtained.

(7th Embodiment)
FIG. 10 is a diagram schematically showing a connecting portion of the divided pieces 19s of the inertial mass body 19 according to the seventh embodiment of the present invention. In the example shown in FIG. 10, an outer protruding portion 19a protruding in the circumferential direction is formed on the outer portion in the radial direction at one end portion in the length direction of the divided piece 19s. At the tip of the outer protruding portion 19a, an outer hook portion 19g protruding inward in the radial direction from the root portion thereof is formed. Further, an inner protruding portion 19b protruding in the circumferential direction is formed on the inner portion in the radial direction at the other end portion in the length direction of the divided piece 19s. At the tip of the inner protruding portion 19b, an inner hook portion 19h protruding outward in the radial direction from the root portion thereof is formed. Then, with the divided pieces 19s aligned in the circumferential direction, as shown in FIG. 10, the inner hook portion 19h of the inner protruding portion 19b is fitted to the root portion of the outer protruding portion 19a, and the inner protruding portion 19b is fitted with the inner hook portion 19h. The outer hook portion 19g of the outer protrusion 19a is fitted to the root portion, and the divided pieces 19s are integrated into a ring shape. With such a configuration, when a tensile load that separates the divided pieces 19s from each other due to centrifugal force acts on their connecting portions, the hook portions 19g and 19h are caught by each other, so that the divided pieces 19s are separated from each other. Can be prevented from each other. That is, as in the fifth embodiment, the strength of the connecting portion can be ensured without welding, and since welding is not performed, the manufacturing cost can be reduced accordingly. If the joint portion of the connecting portion is welded, the strength of the connecting portion can be further improved as compared with each of the above-described embodiments. Therefore, even with such a configuration, the same actions and effects as those of the above-described embodiments can be obtained.

(8th Embodiment)
FIG. 11 is a cross-sectional view schematically showing a connecting portion of the divided pieces 19s of the inertial mass body 19 according to the eighth embodiment of the present invention, and FIG. 12 is a front view of the connecting portion shown in FIG. In the example shown here, a recess 19i recessed in the axial direction is formed at one end of the divided piece 19s in the length direction, and the axis is arranged in the recess 19i at the other end. A bent portion 19j bent in the direction is formed. Then, in a state where the divided pieces 19s are aligned in the circumferential direction, the bent portion 19j is arranged in the recess 19i to form a ring shape. The contact portions of the divided pieces 19s adjacent to each other extend in the radial direction as shown in FIG. Even with such a configuration, when a tensile load that separates the divided pieces 19s from each other due to centrifugal force acts on their connecting portions, the bent portion 19j is caught on the edge portion of the recess 19i. The divided pieces 19s can be prevented from coming off each other. Further, if the contact portions of the divided pieces 19s adjacent to each other are welded, the strength of the connecting portion can be further improved as in the fifth to seventh embodiments described above. Therefore, even with such a configuration, the same actions and effects as those of the above-described embodiments can be obtained.

(9th embodiment, 10th embodiment)
FIG. 13 is a cross-sectional view schematically showing a part of the inertial mass body 19 according to the ninth embodiment of the present invention. In the example shown in FIG. 13, the inner portion of the divided piece 19s in the radial direction is a ring gear in the axial direction. This is an example in which the inner bent portion 19k is formed by bending to the R side, and the ring gear R is brought into contact with the upper side surface (upper surface in FIG. 13) of the inner bent portion 19k. Further, FIG. 14 is a cross-sectional view schematically showing a part of the inertial mass body 19 according to the tenth embodiment of the present invention, and in the example shown in FIG. 14, the outer portion of the divided piece 19s is axially oriented in the radial direction. This is an example in which the outer bent portion 19l is formed by bending toward the ring gear R side, and the lower side surface (lower surface in FIG. 14) of the outer bent portion 19l is brought into contact with the ring gear R. The structure for connecting the divided pieces 19s adjacent to each other in the circumferential direction may be any of the above-described embodiments.

According to the ninth embodiment and the tenth embodiment described above, the geometrical moment of inertia of the divided piece 19s can be improved by forming the inner bent portion 19k and the outer bent portion 19l, so that the inertial mass body 19 as a whole is rigid. And strength is improved. As a result, as described above, it is possible to prevent or suppress the deformation of the inertial mass body 19 due to the deformation of the ring gear R due to the pinion gear P being pressed against the ring gear R by the centrifugal force. Further, in the ninth embodiment, the ring gear R and the upper side surface of the inner bent portion 19k are in direct contact, and in the tenth embodiment, the ring gear R and the lower side surface of the outer bent portion 19l are in direct contact between them. Causes frictional force. Therefore, the ring gear R and the inertial mass body 19 are integrated rather than the rivet 29 alone. As a result, their relative movement can be suppressed more effectively, and an excessive shearing force is less likely to act on the rivet 29. Even with such a configuration, the durability of the device as a whole can be improved, and the same actions and effects as those of the above-described embodiments can be obtained. When the inertial mass bodies 19 are arranged on both sides of the ring gear R in the axial direction, the inner bent portion 19k may be formed on the inner portion of each inertial mass body 19, or the inertial mass bodies 19 may be formed. An outer bent portion 19 l may be formed on the outer portion. Alternatively, the inner bent portion 19k may be formed on the inner portion of one inertial mass body 19, and the outer bent portion 19l may be formed on the outer portion of the other inertial mass body 19. With any of the configurations, the same actions and effects as those of the ninth embodiment and the tenth embodiment described above can be obtained.

(11th Embodiment)
FIG. 15 is a diagram schematically showing an example of the ring gear R according to the eleventh embodiment of the present invention. The example shown in FIG. 15 is an example in which the ring gear R is divided into a plurality of parts in the circumferential direction, similarly to the inertial mass body 19. That is, the ring gear R shown in FIG. 15 includes a plurality of divided pieces Rs having an arc shape having a constant curvature and having the same shape, and in a state where the divided pieces Rs are aligned in the circumferential direction, the divided pieces Rs adjacent to each other The ends are connected to each other to form a ring. These divided pieces Rs can be formed by press molding in the same manner as the divided pieces 19s of the inertial mass body 19 shown in FIG. 4 as the first embodiment. When the divided pieces Rs are press-molded, the shape of each divided piece Rs may be an arc shape having the same curvature as the curvature of the ring gear R defined by design, or may be a strip shape or a flat plate shape. When the shape of the divided pieces Rs press-formed from the work is strip-shaped or flat plate-shaped, the strip-shaped or flat-plate-shaped split pieces Rs are curved to have the same curvature as the ring gear R described above.

When three pinion gears P are arranged on the circumference of the ring gear R, as shown in FIG. 15, the ring gear R is divided into three equal parts, and the three divided pieces Rs are connected to each other in the circumferential direction. Form in a ring shape. When arranging the four pinion gears P, the ring gear R is divided into four equal parts, and the four divided pieces Rs are connected to each other in the circumferential direction to form a ring. That is, the number of pinion gears P arranged on the circumference of the ring gear R is the same as the number of pinion gears P, and the ring gear R is equally divided to form the divided pieces Rs. In the example shown in FIG. 15, the ring gear R is formed by three divided pieces Rs.

Further, the connecting portion of each divided piece Rs is set outside the range in which the pinion gear P reciprocates on the circumference of the ring gear R. This is to avoid the possibility that the engagement between the ring gear R and the pinion gear P deteriorates at the connecting portion and the rotation of the ring gear R is hindered, resulting in deterioration of the vibration damping performance. The range in which the pinion gear P reciprocates is determined by design or structure as described above, and as shown in FIG. 15, the region α on the forward rotation direction side with the assembly position P0 of the pinion gear P in the circumferential direction. It is the region β on the reverse rotation direction side. That is, the pinion gear P does not mesh with the sun gear S or the ring gear R on both sides of these regions α and β in the circumferential direction. Therefore, in the example shown in FIG. 15, no tooth is formed in the region γ outside the range in which the pinion gear P reciprocates, and the split piece Rs is divided into the region γ in which the tooth is not formed. One Rs is connected to each other. In the example shown in FIG. 15, both end faces of the divided pieces Rs in the length direction are formed in a plane parallel to the plane including the normal of the ring gear R. Therefore, when the divided pieces Rs are aligned in the circumferential direction, the joint portions thereof are welded to integrate the divided pieces Rs with each other in a state where the end faces of the divided pieces Rs adjacent to each other are in contact with each other. ..

Further, the divided pieces Rs may be connected to each other so that the ring gear R formed by connecting the divided pieces Rs can be regarded as one in terms of strength. Therefore, the connecting structure of the divided pieces Rs adjacent to each other may be the same as the connecting structure shown in FIGS. 5 to 10 instead of the connecting structure shown in FIG. 15 described above. Other examples of the structure in which the divided pieces Rs are connected to each other are shown in FIGS. 16 to 21 as the twelfth to seventeenth embodiments. Since the connection structure between the divided pieces Rs shown in FIGS. 16 to 21 is the same as the connection structure shown in FIGS. 5 to 11, the same configuration as that shown in FIGS. 5 to 10 is shown in FIGS. 5 to 10. The same reference numerals as those in FIG. 10 are added, and the description thereof will be omitted. Further, in the examples shown in FIGS. 16 to 21, the teeth of the ring gear R are omitted in order to simplify the drawing.

Therefore, as shown in FIGS. 15 to 21, even when the ring gear R is divided and configured, as in each of the above-described embodiments, as compared with the case where the ring gear R is punched out from the work as an integral product, Since the scrap portion can be reduced, the material yield can be improved and the material cost can be reduced. Further, since the connecting portion between the divided pieces Rs is set in the region γ outside the regions α and β in which the pinion gear P reciprocates in the circumferential direction, it is possible to prevent the engagement between the ring gear R and the pinion gear P from deteriorating. Can be suppressed. As a result, the desired vibration damping performance of the torsional vibration reducing device 1 can be obtained. Further, since the divided pieces Rs are connected to each other by a so-called joint structure, welding, or a combination thereof, even if a tensile load that separates the divided pieces 19s from each other due to centrifugal force acts on those connected portions. , The connected state of the divided pieces Rs can be maintained as in each of the above-described embodiments. That is, it can be regarded as an integral product in terms of strength, and deterioration of durability of the device as a whole can be prevented or suppressed.

(18th Embodiment)
Another example of the torsional vibration reducing device 1 according to the embodiment of the present invention will be described. FIG. 22 is a skeleton diagram schematically showing an example of the torsional vibration reducing device according to the eighteenth embodiment of the present invention. At least one of the inertial mass body 19 and the ring gear R is configured to be divided into a plurality of parts in the circumferential direction as in each of the above-described embodiments, and the divided pieces 19s and Rs are divided into each other in the circumferential direction. It suffices if they are connected to form a ring. In the example shown in FIG. 22, the spring damper 20 is an intermediate plate arranged between the first spring 30, the second spring 31, and the first spring 30 and the second spring 31 in the direction of torque transmission in the spring damper 20. It has 32 and. The first spring 30 is located on the upstream side of the second spring 31 in the torque transmission direction. The drive plate 21 and the intermediate plate 32 are connected via the first spring 30 so as to be able to rotate relative to each other at a predetermined angle. Further, the intermediate plate 32 and the driven plate 22 are connected via the second spring 31 so as to be able to rotate relative to each other at a predetermined angle. That is, the first spring 30 and the second spring 31 are connected in series via the intermediate plate 32. The first spring 30 and the second spring 31 are configured by a coil spring as an example, and are set to have substantially the same torsional rigidity (spring constant). Since other configurations are the same as those shown in FIG. 1, the same configurations as those shown in FIG. 1 are designated by the same reference numerals as those shown in FIG. 1 and the description thereof will be omitted.

(19th Embodiment)
FIG. 23 is a cross-sectional view schematically showing an example of the torsional vibration reducing device according to the 19th embodiment of the present invention. At least one of the inertial mass body 19 and the sun gear S is configured to be divided into a plurality of parts in the circumferential direction as in each of the above-described embodiments, and the divided pieces 19s and Ss are divided into each other in the circumferential direction. It suffices if they are connected to form a ring. Explaining the case where the sun gear S is divided into a plurality of pieces in the circumferential direction, the divided pieces Ss of the sun gear S are press-molded in the same manner as the divided pieces 19s of the inertial mass body 19 and the divided pieces Rs of the ring gear R. Can be formed by. When the divided pieces Ss are press-molded, the shape of each divided piece Ss may be an arc shape having the same curvature as the curvature of the sun gear S defined by design, or may be a strip shape or a flat plate shape. When the shape of the split piece Ss press-formed from the work is strip-shaped or flat plate-shaped, the strip-shaped or flat-plate-shaped split piece Ss is curved to have the same curvature as the above-mentioned sun gear S. Further, the divided pieces Ss may be connected to each other so that the sun gear S formed by connecting the divided pieces Ss can be regarded as one in terms of strength. Therefore, although details are not shown, the connecting structure of the divided pieces Ss adjacent to each other may be the same as the connecting structure shown in FIGS. 15 to 21 like the divided pieces Rs of the ring gear R.

In the example shown in FIG. 23, the flywheel 33 is connected to the output shaft 3a of the engine 3, and the drive target portion 4 is connected to the flywheel 33 via the spring damper 20. That is, the drive plate 21 of the spring damper 20 is connected to the flywheel 33. The driven plate 22 of the spring damper 20 is spline-fitted to the input shaft 4a of the drive target portion 4. Further, a damper disc 34 is arranged on the side opposite to the flywheel 33 with the driven plate 22 sandwiched in the axial direction, and the damper disc 34 and the driven plate 22 are riveted. The damper disc 34 is formed in a ring shape as a whole, and the teeth formed on the inner peripheral surface of the damper disc 34 are the ring gear R of the planetary gear mechanism 18. Further, the damper cover 35 is arranged on the side opposite to the driven plate 22 with the damper disk 34 sandwiched in the axial direction. The outer peripheral portion of the damper cover 35 and the outer peripheral portion of the flywheel 33 are integrally connected by welding, for example, and the carrier C of the planetary gear mechanism 18 is integrated with the inner peripheral portion of the damper cover 35. That is, the planetary gear mechanism 18 and the above-mentioned spring damper 20 are arranged between the flywheel 33 and the damper cover 35 in the axial direction.

The planetary gear mechanism 18 is arranged on the inner peripheral side of the spring damper 20 in the radial direction so as to be concentrically aligned with the spring damper 20. Here, "side by side" means a state in which at least a part of each of the spring damper 20 and the planetary gear mechanism 18 overlaps in the radial direction. Then, the inertial mass body 19 is riveted to the sun gear S of the planetary gear mechanism 18. The inertial mass body 19 is arranged on the side opposite to the damper cover 35 with the planetary gear mechanism 18 interposed therebetween in the axial direction. Specifically, in the example shown in FIG. 23, the inertial mass body 19 has a small diameter plate 19 md having substantially the same outer diameter as the sun gear S and a small diameter plate whose inner peripheral portion is riveted to the outer peripheral portion of the small diameter plate 19 md. It is composed of a large diameter plate 19ld having a diameter larger than 19md. As described above, the plates 19md and 19ld of the inertial mass body 19 may be divided in the circumferential direction and connected to each other in the circumferential direction to form a ring. In the nineteenth embodiment, the carrier C described above corresponds to the carrier rotating element and the input element in the embodiment of the present invention, and the sun gear S corresponds to the central rotating element and the inertial element in the embodiment of the present invention. The ring gear R corresponds to the ring rotating element and the output element in the embodiment of the present invention, and the inertial mass body 19 corresponds to the additional inertial body in the embodiment of the present invention.

(20th Embodiment)
FIG. 24 is a cross-sectional view schematically showing an example of a torsional vibration reducing device according to a twentieth embodiment of the present invention. The example shown in FIG. 24 is an example in which the planetary gear mechanism 18 is arranged concentrically with the spring damper 20 on the outer peripheral side of the spring damper 20 shown in FIG. 23 in the radial direction. That is, the damper cover 35 integrally connected to the flywheel 33 includes a first damper cover 35A arranged on the engine 3 side in the axial direction and a second damper cover whose outer peripheral portion is integrally connected to the flywheel 33. It is composed of 35B and. A predetermined interval is provided between the damper covers 35A and 35B in the axial direction. A spring damper 20, a planetary gear mechanism 18, and a damper disk 34 are arranged between the damper covers 35A and 35B. Further, the pinion pins 24 of the planetary gear mechanism 18 are integrally attached to the damper covers 35A and 35B. The teeth formed on the outer peripheral surface of the damper disc 34 are the sun gear S. Further, the inner peripheral portion of the damper disk 34 is spline-fitted to the input shaft 4a of the drive target portion 4. That is, the damper disc 34 also serves as the driven plate 22 of the spring damper 20 in the example shown here. In the twentieth embodiment, the carrier C corresponds to the carrier rotating element and the input element in the embodiment of the present invention, the sun gear S corresponds to the central rotating element and the output element in the embodiment of the present invention, and the ring gear R However, the ring rotating element and the inertial element in the embodiment of the present invention correspond to the inertial mass body 19, and the inertial mass body 19 corresponds to the additional inertial body in the embodiment of the present invention.

Even in the configuration shown in FIGS. 22 to 24, by dividing at least one of the inertial mass body 19, the ring gear R, and the sun gear S, the material yield is the same as in each of the above-described embodiments. Can be improved and the material cost can be reduced. Further, the divided pieces 19s of the inertial mass body 19, the divided pieces Rs of the ring gear R, or the divided pieces Ss of the sun gear S are connected to each other by a so-called joint structure or welding, and they are combined and connected to each other. Even if a tensile load that separates the divided pieces 19s, Rs, and Ss from each other acts on their connecting portions, the divided pieces 19s, Rs, and Ss can be firmly connected to each other and can be prevented from coming off from each other. Therefore, for example, even if the inertial mass body 19 is divided and configured, it is possible to prevent or suppress an excessive load (shear load) acting on the rivet 29 due to the centrifugal force. As described above, even with the configurations shown in FIGS. 22 to 24, the same actions and effects as those of the above-described embodiments can be obtained.

The present invention is not limited to the above-described embodiment, and the carrier C may function as an inertial element instead of the ring gear R, the sun gear S, or the like functioning as an inertial element. Further, the carrier C may be divided in the circumferential direction, and the divided pieces of the carrier C may be connected to each other in the circumferential direction to form a ring shape. Even with such a configuration, the same actions and effects as those of the above-described embodiments can be obtained. Further, as described above, instead of riveting the inertial mass body 19 to the ring gear R, the sun gear S, etc., for example, by crimping the inertial mass body 19, the inertial mass body 19 is attached to the ring gear R, the sun gear S, or the like. It may be attached integrally. In short, the inertial mass body 19 may be integrally attached to the inertial element so as to rotate integrally with the inertial element.

1 ... torsional vibration reduction device, 18 ... planetary gear mechanism (planetary rotation mechanism), 19 ... inertial mass body, 19s ... inertial mass body split piece, 20 ... spring damper (elastic body), 21 ... drive plate (input member) , 22 ... Driven plate (output member), S ... Sun gear (center rotation element), R ... Ring gear (ring rotation element), Rs ... Ring gear split piece, P ... Pinion gear (planetary rotation element), C ... Carrier (carrier rotation) element).

Claims (6)

The central rotating element, the ring rotating element arranged concentrically with respect to the central rotating element, and the central rotating element arranged between the outer peripheral portion of the central rotating element and the inner peripheral portion of the ring rotating element. It is provided with a planetary rotation mechanism that performs a differential action by a carrier rotating element holding a plurality of planetary rotating elements that rotate and revolve as the element and the ring rotating element rotate relative to each other.
Any one of the center rotating element, the ring rotating element, and the carrier rotating element is used as an input element to which torque is input, and among the center rotating element, the ring rotating element, and the carrier rotating element. Any other one is used as an output element for outputting the torque, and any one of the central rotating element, the ring rotating element, and the carrier rotating element is used as the input element and the output element. It is considered to be an inertial element that rotates relative to each other.
In a torsional vibration reducing device in which the input element and the output element are connected to each other via an elastic body so as to be relatively rotatable at a predetermined angle, and an additional inertial body is added to the inertial element.
At least one of the inertial element and the additional inertial body is formed by a plurality of divided pieces divided in the circumferential direction of the planetary rotation mechanism.
A torsional vibration reducing device characterized in that the divided pieces are connected to each other in the circumferential direction to form an annular body. In the torsional vibration reducing device according to claim 1,
The divided pieces are connected to each other in the circumferential direction by at least one of the fitting of the ends of the divided pieces facing each other in the circumferential direction and the welding of the ends. A torsional vibration reduction device characterized by this. In the torsional vibration reducing device according to claim 1 or 2.
A torsional vibration reducing device characterized in that the connecting portion between the divided pieces is a portion deviated from the angular range in which the planetary rotating element reciprocates due to the vibration of the torque in the circumferential direction. In the torsional vibration reducing device according to any one of claims 1 to 3.
The additional inertial body is formed by the plurality of divided pieces divided in the circumferential direction.
A torsional vibration reducing device characterized in that the divided pieces are integrally attached to the side surface of the inertial element in the axial direction of the planetary rotation mechanism in a state of being connected to each other in the circumferential direction by a fixing means. .. In the torsional vibration reducing device according to any one of claims 1 to 4.
The input element is one of the central rotation element and the carrier rotation element, and the output element is the other of the center rotation element and the carrier rotation element.
The torsional vibration reducing device, wherein the inertial element is the ring rotating element. In the torsional vibration reducing device according to any one of claims 1 to 5.
In the planetary rotation mechanism, the central rotation element is composed of a sun gear, the ring rotation element is composed of a ring gear, the planet rotation element is composed of a pinion gear, and the carrier rotation element is composed of a carrier holding the pinion gear. A torsional vibration reduction device characterized by being a configured planetary gear mechanism.

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