JP7021050B2 - Torsion vibration reduction device - Google Patents

Description

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

Patent Document 1 describes an example in which a planetary gear mechanism is used as a device for reducing torsional vibration. The planetary gear mechanism is arranged inside a torque converter having a lockup clutch and outside the spring damper in the radial direction so as to be concentrically aligned with the spring damper. The lockup clutch and the input side member of the spring damper are connected to the carrier of the planetary gear mechanism, and torque is input to the carrier via the lockup clutch. Further, the output side member of the spring damper is connected to the sun gear. That is, the carrier and the sun gear are connected via a spring damper. An annular side plates having an outer diameter and an inner diameter substantially the same as the outer diameter and the inner diameter of the ring gear are provided on both sides of the ring gear in the axial direction, and the side plates and the ring gear are integrated by rivets. Each side plate and rivet function as an inertial mass together with the ring gear. Then, when the input torque vibrates, the spring of the spring damper expands and contracts, and the carrier and the sun gear rotate relative to each other by a predetermined angle. Along with this, the ring gear is forcibly rotated, and the inertial torque of the ring gear acts as a resistance to the vibration of the input torque, and the vibration of the torque output from the planetary gear mechanism is reduced.

International Publication No. 2016/208767

In a device that reduces torque vibration by the reciprocating motion of an inertial mass, the larger the inertial torque, the lower the resonance rotation speed and the larger the vibration damping torque. The moment of inertia is determined by the moment of inertia and the angular acceleration, and the moment of inertia increases as the mass of the inertial mass body increases and as the inertial mass body is arranged outside in the radial direction. In the device described in Patent Document 1, since the ring gear and the side plate are configured to function as an inertial mass, the moment of inertia can be increased as compared with the case where another rotating element functions as an inertial mass. .. However, the outer diameter of the ring gear is restricted by the clearance set between the ring gear and the inner surface of the torque converter in order to avoid interference with the inner surface of the torque converter, the inner diameter of the torque converter, and the like. On the other hand, the pitch circle diameter of the ring gear is restricted by the pitch circle diameters of the pinion gear and the sun gear arranged inside the ring gear and the mounting position of the spring in the radial direction of the torque converter. Therefore, it is difficult to increase the moment of inertia by increasing the size of the ring gear in the radial direction. Even if the ring gear is to be increased in size, if the ring gear is simply increased in size, the size of the device as a whole may be increased.

The present invention has been made by paying attention to the above technical problems, and can increase the moment of inertia required to reduce the vibration of the input torque without increasing the size of the device in the radial direction. It is an object of the present invention to provide a torsional vibration reduction device.

The present invention has a first rotating element to which torque is input, a second rotating element, and a third rotating element that functions as a rotational inertia mass body, in order to achieve the above object, and the first rotating element. It is provided with a planetary rotation mechanism that performs a differential action by the second rotation element and the third rotation element, and an elastic member that connects the first rotation element and the second rotation element at a predetermined angle so as to be relatively rotatable. The elastic member is elastically deformed by the vibration of the torque, the first rotating element and the second rotating element are relatively rotated, and the rotation of the third rotating element is configured to generate vibration. In the torsional vibration reducing device, the first is such that it is the outer peripheral portion of the third rotating element in the radial direction of the planetary rotation mechanism and protrudes from the third rotating element in the direction of the rotation center axis of the planetary rotating mechanism. An additional inertial body is added to the three rotating elements, and the planetary rotating mechanism 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. It has a carrier rotating element that is arranged between the inner peripheral portion of the rotating element and holds a plurality of planetary rotating elements that rotate and revolve due to relative rotation between the central rotating element and the ring rotating element. The first rotating element is one of the central rotating element and the carrier rotating element, and the second rotating element is the other of the central rotating element and the carrier rotating element. The third rotating element is characterized by being the ring rotating element.

In the present invention, the additional inertial body is formed in a cylindrical shape having a length in the rotation center axis direction longer than the ring rotating element, and the ring rotating element is formed on the inner peripheral surface of the additional inertial body in the radial direction. It may be integrated.

In the present invention, the additional inertial body is formed by an annular plate having the same outer diameter as the outer diameter of the ring rotating element and having an inner diameter larger than the inner diameter of the ring rotating element, and is formed on the outer peripheral portion of the plate. A protrusion protruding in the direction of the center axis of rotation may be provided, and the plate may be provided on at least one of both side surfaces of the ring rotating element in the direction of the center axis of rotation.

In the present invention, the elastic member may be arranged concentrically with the planetary rotation mechanism inside the planetary rotation mechanism in the radial direction.

In the present invention, a housing connected to an engine, a drive-side member connected to the housing to generate a fluid flow, and a driven-side member driven by the fluid flow are engaged with the inner surface of the housing. A fluid transmission device having a drive-side member and a direct-coupled clutch for connecting the driven-side member may be provided, and the planetary rotation mechanism may be provided inside the fluid transmission device.

In the present invention, the first rotating element may be the carrier rotating element, and the second rotating element may be the central rotating element.

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

According to the present invention, when the elastic member is elastically deformed by the vibration of torque and the relative rotation between the first rotating element and the second rotating element occurs, it functions as a rotational inertia mass body by the differential action of the planetary rotation mechanism. The third rotating element is forcibly rotated. Since the rotation of the third rotating element is due to the vibration of torque, vibration occurs in the rotation of the third rotating element. The third rotating element is a ring rotating element of the planetary rotating mechanism, and the ring rotating element is an outer peripheral portion of the ring rotating element and protrudes from the ring rotating element in the direction of the rotation center axis of the planetary rotating mechanism. As such, an additional inertial body is added. Therefore, as compared with the case where the additional inertial body is provided almost evenly from the inner peripheral portion of the ring rotating element in the radial direction and from the inner peripheral portion to the outer peripheral portion of the ring rotating element in the radial direction, the entire ring rotating element is provided. The moment of inertia of is increased. Then, the inertial torque of the ring rotating element determined by the moment of inertia and the angular acceleration becomes large. That is, the moment of inertia can be increased without particularly increasing the outer diameter of the ring rotating element. In addition, the size of the device as a whole is not particularly large.

It is sectional drawing which shows typically an example of the torsional vibration reduction apparatus which concerns on 1st Embodiment of this invention. FIG. 3 is an enlarged cross-sectional view showing a part of the planetary gear mechanism shown in FIG. 1. It is a side view which shows a part of a ring gear enlarged. It is a figure which shows the relationship between the engine speed and the engine torque reduced by a torsional vibration reduction device. It is sectional drawing which shows typically an example of the torsional vibration reduction apparatus which concerns on 2nd Embodiment of this invention. It is sectional drawing which shows typically an example of the torsional vibration reduction apparatus which concerns on 3rd Embodiment of this invention. It is sectional drawing which shows typically an example of the torsional vibration reduction apparatus which concerns on 4th Embodiment of this invention. It is sectional drawing which shows typically an example of the torsional vibration reduction apparatus which concerns on 5th Embodiment of this invention. It is sectional drawing which shows typically an example of the torsional vibration reduction apparatus which concerns on 6th Embodiment of this invention.

Next, an embodiment of the present invention will be described. FIG. 1 is a cross-sectional view showing an example of a torque converter 2 provided with a torsional vibration reducing device 1 as the first embodiment of the present invention. A torque converter 2 is connected to an output shaft (not shown) of the driving force source. The driving force source is an internal combustion engine that outputs power by intermittently burning a mixture of fuel and air, and therefore the output torque of the driving force source inevitably vibrates. In the following description, the driving force source will be referred to as an engine. The torque converter 2 has the same configuration as that conventionally known, and the housing 3 of the torque converter 2 has a front cover 4 connected to the output shaft of the engine and a pump integrated with the front cover 4. It is formed in a liquidtight state by the shell 5.

A fluid (oil) that transmits torque is sealed inside the housing 3. A plurality of pump blades 6 are attached to the inner surface of the pump shell 5 to form a pump impeller 7. A turbine runner 8 that rotates in response to the fluid flow generated by the pump impeller 7 is arranged to face the pump impeller 7. The turbine runner 8 has a shape substantially symmetrical to that of the pump impeller 7, and is composed of a turbine shell (not shown) and a large number of turbine blades 9 mounted on the inner surface of the turbine shell. The turbine runner 8 is connected to an input shaft (not shown) of the transmission via a turbine hub 10. The torque converter 2 described above corresponds to the fluid transmission device according to the embodiment of the present invention, the pump impeller 7 corresponds to the drive side member according to the embodiment of the present invention, and the turbine runner 8 corresponds to the driven side according to the embodiment of the present invention. It corresponds to a member. The transmission may be, for example, a conventionally known transmission such as a stepped transmission in which the gear ratio changes stepwise, or a continuously variable transmission in which the gear ratio continuously changes.

A stator 11 is arranged between the pump impeller 7 and the turbine runner 8. The stator 11 is attached to a fixed shaft in the torque converter 2 via a one-way clutch 12. When the speed ratio between the pump impeller 7 and the turbine runner 8 is small, the stator 11 changes the flow direction of the oil flowing out from the turbine runner 8 and supplies it to the pump impeller 7, and when the speed ratio is large, the stator 11 is supplied from the turbine runner 8. It is configured so that the flow direction of the oil is not changed by being pushed by the flowing oil and rotating. Therefore, the one-way clutch 12 is configured to engage to stop the rotation of the stator 11 when the speed ratio is small, and to rotate the stator 11 when the speed ratio is large.

A lockup clutch 13 corresponding to the directly connected clutch in the embodiment of the present invention is arranged facing the inner surface of the front cover 4. The lockup clutch 13 shown in FIG. 1 is a multi-plate clutch, and covers, for example, a plurality of clutch discs 14 spline-fitted to a clutch hub integrated with a front cover 4 and an outer peripheral side of the clutch hub. A plurality of clutch plates 16 spline-fitted and alternately arranged with the clutch disc 14 are provided on the inner peripheral surface of the clutch drum 15 arranged in the above. The clutch disc 14 and the clutch plate 16 are alternately arranged between the lockup piston 17 and a snap ring (not shown) attached to the clutch drum 15. Therefore, when the lockup piston 17 advances and sandwiches the clutch disc 14 and the clutch plate 16 between the snap ring, the clutch disc 14 and the clutch plate 16 are in frictional contact with each other, and torque is transmitted between them. To. That is, the lockup clutch 13 is in an engaged state in which torque is transmitted. A return spring 18 is arranged on the inner peripheral side of the lockup clutch 13 in the radial direction of the torque converter 2 along with at least a part of the lockup clutch 13. The return spring 18 presses the lockup piston 17 in the direction of releasing the lockup clutch 13, that is, in the direction of separating the clutch disc 14 and the clutch plate 16.

The above-mentioned torsional vibration reducing device 1 is arranged adjacent to the lockup clutch 13 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 a spring damper 19 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 configured by a single pinion type planetary gear mechanism 20. .. The planetary gear mechanism 20 includes a sun gear 21, a ring gear 22 arranged concentrically with respect to the sun gear 21, and a carrier 24 that rotatably holds a plurality of pinion gears 23 that mesh with the sun gear 21 and the ring gear 22. The sun gear 21 described above corresponds to the first rotating element, the second rotating element, and the central rotating element in the embodiment of the present invention, and the ring gear 22 functions as a rotational inertia mass body in the embodiment of the present invention. , The pinion gear 23 corresponds to the planetary rotating element in the embodiment of the present invention, and the carrier 24 corresponds to the first rotating element, the second rotating element, and the carrier rotating element in the embodiment of the present invention. There is.

The clutch drum 15 of the lockup clutch 13 and the drive plate 25 of the spring damper 19 are connected to the carrier 24, and this is an input element. The sun gear 21 is formed on the outer peripheral portion of the driven plate 26 of the spring damper 19, and this is an output element. An additional inertial body 27 configured to protrude from the ring gear 22 in the axial direction is integrally provided on the outer peripheral portion of the ring gear 22. That is, the additional inertial body 27 is provided unevenly on the outer peripheral portion of the ring gear 22 in the radial direction. As a result, the ring gear 22 is provided with the additional inertial body 27 having the same mass substantially evenly from the inner peripheral portion to the outer peripheral portion of the ring gear 22 in the radial direction as compared with the case where the additional inertial body 27 is provided on the inner peripheral portion of the ring gear 22. The generated moment of inertia increases. The additional inertial body 27 may be configured as a separate body from the ring gear 22 and may be attached to the ring gear 22 so as to rotate integrally with the ring gear 22.

The spring damper 19 is arranged concentrically with the planetary gear mechanism 20 on the inner peripheral side of the planetary gear mechanism 20 in the radial direction of the torque converter 2. Here, "side by side" means a state in which at least a part of each of the spring damper 19 and the planetary gear mechanism 20 overlaps in the radial direction. The drive plate 25 of the spring damper 19 is arranged on the upstream side in the torque transmission direction of the spring damper 19, and is composed of an annular first drive plate 25A and an annular second drive plate 25B. The outer peripheral portion 25A _O and the inner peripheral portion 25A _I of the first drive plate 25A are configured to be offset from each other in the axial direction, and in the example shown in FIG. 1, the outer peripheral portion 25A _O of the first drive plate 25A is the inner peripheral portion thereof. It is located on the lockup clutch 13 side with respect to the portion _25AI .

The outer peripheral portion 25B _O and the inner peripheral portion 25B _I of the second drive plate 25B are configured to be offset from each other in the axial direction, and in the example shown in FIG. 1, the outer peripheral portion _25BO of the second drive plate 25B is the inner peripheral portion thereof. It is located on the turbine runner 8 side with respect to the portion _25BI . Therefore, the distance between the outer peripheral portion 25A _O of the first drive plate 25A and the outer peripheral portion _25BO of the second drive plate 25B in the axial direction is larger than the distance between the inner peripheral portions _25AI and _25BI . The planetary gear mechanism 20 is arranged here. Further, the pinion gear 23 of the planetary gear mechanism 20 is rotatably attached to the outer peripheral portions _25AO and _25BO of the drive plates 25A and 25B. Therefore, the drive plates 25A and 25B also serve as the carrier 24.

An annular center plates 28A and 28B are provided on both sides of the drive plates 25A and 25B in the axial direction and on the downstream side of the drive plates 25A and 25B in the torque transmission direction. The drive plates 25A and 25B and the center plates 28A and 28B are connected via a first spring 29 so that they can rotate relative to each other at a predetermined angle. An annular driven plate 26 is arranged on the downstream side of the center plates 28A and 28B in the torque transmission direction and between the drive plates 25A and 25B in the axial direction. The driven plate 26 and the center plates 28A and 28B are connected to each other via a second spring (not shown) so that they can rotate relative to each other at a predetermined angle. The first spring 29 and the second spring are configured by a coil spring in the example shown here, and are set to have substantially the same torsional rigidity (spring constant). External teeth are formed on the outer peripheral surface of the driven plate 26, which is the sun gear 21 of the planetary gear mechanism 20 as described above. The inner peripheral portion of the driven plate 26 is riveted to the turbine hub 10 described above. The first spring 29 and the second spring correspond to the elastic member in the embodiment of the present invention, and the elastic member is, in short, elastically deformed to rotate relative to the drive plate 25 and the driven plate 26. Anything that allows

FIG. 2 is an enlarged cross-sectional view of the planetary gear mechanism 20 shown in FIG. To specifically explain the configuration of the planetary gear mechanism 20, the pinion pins 30 are held on the outer peripheral portions 25A _O and 25B _O of the drive plates 25A and 25B, and bearings such as needle bearings are held on the outer peripheral side of the pinion pins 30. A pinion gear 23 is rotatably attached via 31. Large-diameter thrust washers 32 are provided on both sides of the pinion gear 23 in the axial direction. The outer diameter of the thrust washer 32 is set to be slightly larger than the pitch circle diameter of the ring gear 22. Other washers 33 having a diameter smaller than that of the thrust washer 32 are provided on both sides of each thrust washer 32. These washers 32 and 33 receive an axial component force due to the engagement between the pinion gear 23 and the sun gear 21 and an axial component force due to the engagement between the pinion gear 23 and the ring gear 22, and also receive an axial component force due to the above-mentioned component force. The movement of the ring gear 22 is suppressed. Further, as described above, the additional inertial body 27 is formed so as to project in the axial direction from the ring gear 22, and the inner diameter of the additional inertial body 27 is set to be larger than the outer diameter of the clutch drum 15 and the outer diameter of the thrust washer 32. ing. Therefore, it is possible to avoid or suppress the interference between the additional inertial body 27 and the clutch drum 15 and the thrust washer 32.

Further, the outer peripheral portion of the clutch drum 15 slightly extends toward the turbine runner 8 in the axial direction. The outer peripheral portion _25AO of the first drive plate 25A is configured to fit on the inner surface of the outer peripheral portion in the radial direction. Further, a fitting portion 34 recessed in the axial direction is formed on the surface of the clutch drum 15 on the first drive plate 25A side in the axial direction, and the head portion 35 of the pinion pin 30 is fitted in the fitting portion 34. It is designed to fit.

FIG. 3 is an enlarged side view showing a part of the ring gear 22. As shown in FIG. 3, the additional inertial body 27 is integrally provided on the outer peripheral portion of the ring gear 22 with a predetermined clearance C opened between the additional inertial body 27 and the inner surface 36 of the housing 3. The clearance C is designed to avoid or suppress the interference between the additional inertial body 27 and the inner surface 36 of the housing 3.

Next, the operation of the first embodiment will be described. When the lockup clutch 13 is engaged, engine torque is input to the carrier 24. On the other hand, a torque for rotating a transmission (not shown) acts on the sun gear 21 via the first spring 29 and the second spring. Therefore, a load for compressing the first spring 29 and the second spring is generated by these engine torques and the torque for rotating the transmission, and the displacement corresponding to the load is applied to the first spring 29 and the second spring. Occurs. As a result, the carrier 24 and the sun gear 21 rotate relative to each other by a predetermined angle, and the drive plates 25A and 25B and the driven plate 26 rotate relative to each other by a predetermined angle.

The compression force (torsional force) acting on the first spring 29 and the second spring changes due to the vibration of the engine torque. Therefore, the relative rotation between the carrier 24 and the sun gear 21 is repeatedly generated by the vibration of the engine torque. As a result, the pinion gear 23 rotates within a predetermined angle range, the ring gear 22 is forcibly rotated, and vibration occurs in the rotation. At this time, since the rotation speed of the ring gear 22 is increased according to the gear ratio with respect to the rotation speed of the sun gear 21, the angular acceleration of the ring gear 22 is increased.

Further, since the additional inertial body 27 is unevenly provided on the outer peripheral portion of the ring gear 22, the additional inertial body is substantially evenly provided from the inner peripheral portion of the ring gear 22 and the inner peripheral portion of the ring gear 22 to the outer peripheral portion in the radial direction. The moment of inertia of the ring gear 22 is larger than that of the case where the 27 is provided. As a result, the inertia torque of the ring gear 22 determined by the moment of inertia and the angular acceleration becomes large. Since this inertia torque acts as a vibration damping torque with respect to the vibration of the engine torque, the engine torque input to the carrier 24 is reduced by the inertia torque of the ring gear 22 to become smooth, and is output from the driven plate 26. Further, in the first embodiment, the additional inertial body 27 is formed so as to extend in the axial direction, and the ring gear 22 is not particularly enlarged in the radial direction. Therefore, the torque converter 2 and the torsional vibration reducing device 1 are not particularly enlarged. In the above-described configuration, the shape of the inner peripheral portion of the ring gear 22 is not particularly changed by providing the additional inertial body 27, that is, there is no factor that hinders the rotation of the ring gear 22, and the ring gear 22 is rotated smoothly. be able to.

FIG. 4 is a diagram showing the relationship between the engine speed and the engine torque reduced by the torsional vibration reducing device 1. In the first embodiment, since the moment of inertia of the ring gear 22 can be increased as described above, the moment of inertia of the ring gear 22 is set at the anti-resonance point A at the engine speed ω ₀ where the vibration of the torque in the driven plate 26 is minimized. As shown in FIG. 4, it is possible to shift to the low rotation speed side as compared with the case where the moment of inertia is not increased. As a result, the vibration of the torque in the low rotation speed range becomes smooth, and the lockup clutch 13 can be engaged in the low rotation speed range. That is, the rotation speed range in which the lockup clutch 13 can be maintained in the engaged state is expanded to the low rotation speed side, so that fuel efficiency can be improved.

Further, the engine speed ω ₀ at the antiresonance point A can be calculated by the following equation (1). In the following equation (1), "K ₁ " indicates the torsional rigidity (spring constant) of the first spring 29, "K ₂ " indicates the torsional rigidity (spring constant) of the second spring, and " _IR " indicates the torsional rigidity (spring constant). As described above, the moment of inertia of the ring gear 22 provided with the additional inertial body 27 is shown, "I ₂ " shows the moment of inertia of the center plates 28A and 28B, and "B" shows the number of teeth of the sun gear 21 and the number of teeth of the ring gear 22. It is the gear ratio of the planetary gear mechanism 20 obtained by dividing by.

As shown in the equation (1), the larger the moment of _inertia IR of the ring gear 22, the smaller the engine speed ω ₀ corresponding to the antiresonance point A. Therefore, in the first embodiment, the moment of inertia IR of the ring gear 22 is set so that the vibration of the torque output from the driven plate 26 is minimized at the engine rotation speed _{ω 0} determined by design. Further, in the first embodiment, since the additional inertial body 27 is provided unevenly on the outer peripheral portion of the ring gear 22, it is required in design as compared with the case where the additional inertial body 27 is provided on the inner peripheral portion of the ring gear 22. The mass of the additional inertial body 27 required to obtain the moment of inertia _IR can be reduced. That is, a large moment of inertia _IR can be obtained with a small mass.

The present invention is not limited to the above-described embodiment, and the additional inertial body 27 is basically provided so that the mass of the outer peripheral portion of the ring gear 22 is larger than the mass of the inner peripheral portion. good. The example shown in FIG. 5 is an example in which the additional inertial body 27 is integrally provided on the side surface on the turbine runner 8 side of both side surfaces of the ring gear 22 in the axial direction. With the configuration shown in FIG. 5, the same operations and effects as those of the first embodiment shown in FIG. 1 can be obtained, and interference with the lockup clutch 13 can be further suppressed.

The example shown in FIG. 6 is an example in which the outer peripheral surface of the additional inertial body 27 having the configuration shown in FIG. 2 is formed following the shape of the inner surface 36 of the housing 3. In the configuration shown in FIG. 6, interference with the inner surface 36 of the housing 3 can be further suppressed, the mass of the additional inertial body 27 can be made as large as possible, and the clearance C can be made as much as possible. It can be made smaller.

The example shown in FIG. 7 is an example in which the additional inertial body 27 having the configuration shown in FIG. 2 is configured as a separate body from the ring gear 22. The additional inertial body 27 shown in FIG. 7 is formed in a cylindrical shape having a length in the axial direction longer than that of the ring gear 22, and the ring gear 22 is fixed inside the additional inertial body 27 by a predetermined fixing means. The fixing means may be a conventionally known fixing means, for example, press fitting, welding, riveting, bolting, or the like. In the configuration shown in FIG. 7, since the additional inertial body 27 is a separate body, the design and manufacture of the ring gear 22 are not particularly changed, so that the cost increase can be minimized. Further, by replacing the additional inertial body 27 attached to the ring gear 22 with an additional inertial body 27 having a different shaft length or outer diameter, the moment of inertia of the ring gear 22 can be increased or decreased, so that the moment of inertia of the ring gear 22 can be tuned. Can be easily performed. Even with the configuration shown in FIG. 7, the same operation / effect as that of the first embodiment shown in FIG. 1 can be obtained.

The example shown in FIG. 8 is an example in which an additional inertial body 27 formed by an annular plate is provided on each of both side surfaces of the ring gear 22 in the axial direction. The outer peripheral portion of the additional inertial body 27 is a protruding portion 27A protruding in the axial direction, and the cross section of the additional inertial body 27 is L-shaped as shown in FIG. Further, the outer diameter of the additional inertial body 27 shown in FIG. 8 is set to be substantially the same as the outer diameter of the ring gear 22, and the inner diameter thereof is larger than the outer diameter of the thrust washer 32 in order to avoid interference with the thrust washer 32. It is set. The additional inertial body 27 is welded, riveted or bolted to each of both side surfaces of the ring gear 22. In the configuration shown in FIG. 8, since the additional inertial body 27 can be formed by, for example, press working, the manufacturing cost of the additional inertial body 27 can be minimized. Further, by replacing the additional inertial body 27 attached to the ring gear 22 with an additional inertial body 27 having a different size of the protruding portion 27A, the moment of inertia of the ring gear 22 can be increased or decreased, so that the moment of inertia of the ring gear 22 can be easily tuned. Can be done. Even with the configuration shown in FIG. 8, the same operation / effect as that of the first embodiment shown in FIG. 1 can be obtained.

The example shown in FIG. 9 is an example in which the additional inertial body 27 shown in FIG. 8 is integrally provided on the side surface on the turbine runner 8 side of both side surfaces of the ring gear 22 in the axial direction. With such a configuration, interference with the lockup clutch 13 can be further suppressed, and the same actions and effects as those of the first embodiment shown in FIGS. 1 and 8 can be obtained.

Further, in the embodiment of the present invention, the sun gear may be used as an input element and the carrier may be used as an output element. In short, the ring gear may be configured to function as a rotational inertia mass body. The planetary rotation mechanism in the embodiment of the present invention is not limited to gears, and may be configured by rollers.

1 ... torsional vibration reduction device, 20 ... planetary gear mechanism (planetary rotation mechanism), 21 ... sun gear (center rotation element), 22 ... ring gear (ring rotation element), 23 ... pinion gear (planetary rotation element), 24 ... carrier (carrier) Rotating element), 27 ... additional inertial body, 29 ... first spring (elastic member).

Claims (7)

It has a first rotating element, a second rotating element, and a third rotating element that functions as a rotational inertia mass body to which torque is input, and by the first rotating element, the second rotating element, and the third rotating element. A planetary rotation mechanism that performs differential action,
An elastic member for connecting the first rotating element and the second rotating element at a predetermined angle so as to be relatively rotatable is provided.
The elastic member is elastically deformed by the vibration of the torque so that the first rotating element and the second rotating element are relatively rotated, and at the same time, a torsion configured so that vibration is generated in the rotation of the third rotating element. In the vibration reduction device
Additional inertia to the third rotating element so that it is the outer peripheral portion of the third rotating element in the radial direction of the planetary rotating mechanism and protrudes from the third rotating element in the direction of the rotation center axis of the planetary rotating mechanism. The body is added,
The planetary rotation mechanism is arranged between a central rotation element, a ring rotation element concentrically arranged with respect to the center rotation element, an outer peripheral portion of the center rotation element, and an inner peripheral portion of the ring rotation element. It has a carrier rotating element that holds a plurality of planetary rotating elements that rotate and revolve by the relative rotation of the central rotating element and the ring rotating element.
The first rotating element is one of the central rotating element and the carrier rotating element.
The second rotating element is the other of the central rotating element and the carrier rotating element.
The third rotating element is a torsional vibration reducing device, characterized in that it is the ring rotating element. In the torsional vibration reducing device according to claim 1,
The additional inertial body is formed in a cylindrical shape having a length in the rotation center axis direction longer than the ring rotating element, and the ring rotating element is integrated with the inner peripheral surface of the additional inertial body in the radial direction. A torsional vibration reduction device characterized by inertia. In the torsional vibration reducing device according to claim 1,
The additional inertial body is formed by an annular plate having an outer diameter equal to the outer diameter of the ring rotating element and an inner diameter larger than the inner diameter of the ring rotating element.
A protruding portion protruding in the direction of the rotation center axis is provided on the outer peripheral portion of the plate.
A torsional vibration reducing device, wherein the plate is provided on at least one of both side surfaces of the ring rotating element in the direction of the rotation center axis. In the torsional vibration reducing device according to any one of claims 1 to 3.
A torsional vibration reducing device, characterized in that the elastic members are arranged concentrically with the planetary rotation mechanism inside the planetary rotation mechanism in the radial direction. In the torsional vibration reducing device according to any one of claims 1 to 4.
The drive-side member by engaging the inner surface of the housing with a housing connected to the engine, a drive-side member connected to the housing to generate a fluid flow, and a driven-side member driven by the fluid flow. And a fluid transmission device having a direct-coupled clutch for connecting the driven side member.
The planetary rotation mechanism is a torsional vibration reducing device provided inside the fluid transmission device. In the torsional vibration reducing device according to any one of claims 1 to 5.
The first rotating element is a carrier rotating element, and the first rotating element is a carrier rotating element.
The second rotating element is a torsional vibration reducing device, characterized in that it is the central rotating element. In the torsional vibration reducing device according to any one of claims 1 to 6.
In the planetary rotation mechanism, the central rotation element is configured by a sun gear, the ring rotation element is configured by a ring gear, the planet rotation element is configured by a pinion gear, and the carrier rotation element is configured by a carrier holding the pinion gear. A torsional vibration reduction device characterized by being configured.

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