CN111120531B - Torsional vibration reducing device - Google Patents

Abstract

The present invention provides a torsional vibration reducing device capable of increasing the moment of inertia required to reduce vibration of an input torque without increasing the size of the device in the radial direction. In the torsional vibration reducing device (1), on the outer peripheral portion of the third rotating element (22) and so as to protrude from the third rotating element (22) in the direction of the rotation center axis, the third rotating element (22) An additional inertial body (27) is attached to the upper, and the planetary rotation mechanism (20) has a center rotation element (21), an internal meshing rotation element (22) and a planetary carrier rotation element (24), and the first rotation element is set as the center rotation element. One of the element (21) and the carrier rotation element (24), the second rotation element is set to the other of the center rotation element (21) and the carrier rotation element (24), and the third rotation element is set to is the internal meshing rotating element (22).

Description

Torsional Vibration Mitigation Device

technical field

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

Background technique

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 concentrically with the spring damper inside the torque converter having the lock-up clutch and on the outer side of the spring damper in the radial direction. A lock-up clutch and an input-side member of a spring damper are connected to the carrier of the planetary gear mechanism, so that torque is input to the carrier via the lock-up clutch. In addition, 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 the spring damper. In the axial direction and on both sides of the ring gear, annular side plates with an outer diameter and an inner diameter that are substantially the same as those of the ring gear are respectively provided, and these side plates and the ring gear are connected by rivets. been integrated. Each side plate and rivet function together with the ring gear as an inertial mass body. Then, when the input torque vibrates, the spring of the spring damper expands and contracts, so that the carrier and the sun gear relatively rotate at a predetermined angle. Along with this, the ring gear is forcibly rotated, and the inertia torque of the ring gear acts as a resistance to the vibration of the input torque, thereby making the torque output from the planetary gear mechanism vibration is reduced.

prior art literature

Patent Literature

Patent Document 1: International Publication No. 2016/208767

SUMMARY OF THE INVENTION

The problem to be solved by the invention

In a device that reduces torque vibration by reciprocating motion of an inertial mass body, the larger the inertial torque, the more the resonance rotational speed can be reduced, and the more the vibration-damping torque can be increased. The inertia moment is determined by the inertia moment and angular acceleration, and the inertia moment increases as the mass of the inertial mass body is larger and 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 the inertial mass bodies, compared with the case where other rotational elements function as the inertial mass bodies, it is possible to Increase the moment of inertia. 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 diameter of the ring gear is affected by the pitch diameters of the pinion gears and the sun gear arranged inside the ring gear, the mounting positions of the springs in the radial direction of the torque converter, and the like. constraints. Therefore, it is difficult to increase the moment of inertia by increasing the size of the ring gear in the radial direction. In addition, even if the ring gear is increased in size by any chance, there is a possibility that the size of the entire device may be increased when only the ring gear is increased in size.

The present invention has been made in view of the above-mentioned technical problems, and an object of the present invention is to provide a torsion capable of increasing the moment of inertia required to reduce the vibration of the input torque without increasing the size of the device in the radial direction. Vibration mitigation device.

methods for solving problems

In order to achieve the above-mentioned object, the present invention is a torsional vibration reducing device comprising: a planetary rotating mechanism having a first rotating element to which torque is input, a second rotating element, and a first rotating element functioning as a rotating inertial mass body Three rotating elements, and the differential action is implemented by the first rotating element, the second rotating element, and the third rotating element; and an elastic member, which is used for the first rotating element and the second rotating element. The torsional vibration reducing device is connected so as to be relatively rotatable by a predetermined angle, and the torsional vibration reducing device is configured such that the elastic member is elastically deformed by the vibration of the torque to cause the first rotation The element and the second rotating element rotate relative to each other, and vibration is generated during the rotation of the third rotating element, and the torsional vibration reducing device is characterized in that in the radial direction of the planetary rotating mechanism and the An additional inertial body is attached to the third rotating element at the outer peripheral portion of the third rotating element so as to protrude from the third rotating element in the direction of the rotation center axis of the planetary rotating mechanism. The planetary rotation mechanism includes: a center rotation element; an internal meshing rotation element arranged on a concentric circle with respect to the center rotation element; a carrier rotation element for holding a plurality of planetary rotation elements, the planetary rotation elements The rotating element is arranged between the outer peripheral portion of the central rotating element and the inner peripheral portion of the internal meshing rotating element, and rotates and revolves by relative rotation of the central rotating element and the internal meshing rotating element, The first rotation element is set as one of the center rotation element and the carrier rotation element, and the second rotation element is set as one of the center rotation element and the carrier rotation element. On the other hand, the third rotation element is set as the internal meshing rotation element.

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

In the present invention, the additional inertial body may have an inner diameter that is the same as the outer diameter of the inner meshing rotating element and larger than the inner diameter of the inner meshing rotating element. A ring-shaped plate is formed, and a protrusion protruding in the direction of the rotation center axis is provided on the outer peripheral portion of the plate, and the plate is rotated by the internal meshing provided in the direction of the rotation center axis. on at least one of the two sides of the element.

In the present invention, the elastic members may be arranged concentrically with the planetary rotation mechanism on the inner side of the planetary rotation mechanism in the radial direction. .

In the present invention, a fluid transmission device including a casing connected to the engine and a drive-side member connected to the casing and allowing the fluid to flow may be adopted. Flow generation; a driven-side member that is driven by the fluid flow; a direct clutch that connects the driving-side member and the driven-side member by engaging with the inner surface of the housing , the planetary rotation mechanism is arranged inside the fluid transmission device.

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

In the present invention, the central rotating element of the planetary rotating mechanism may be constituted by a sun gear, the ring rotating element may be constituted by a ring gear, and the planetary rotating element may be constituted by a sun gear. A pinion gear is formed, and the carrier rotation element is formed by a carrier that holds the pinion gear.

Invention effect

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, the differential action of the planetary rotating mechanism functions as a rotating inertial mass body The third rotation element of the function is forcibly rotated. Since the rotation of the third rotation element is caused by the vibration of torque, vibration occurs during the rotation of the third rotation element. The third rotating element is an internally meshing rotating element of the planetary rotating mechanism, and the internally meshing rotating element is internally meshed at the outer peripheral portion of the internally meshing rotating element in the direction of the rotation center axis of the planetary rotating mechanism. An additional inertial body is attached in such a way that the rotation element protrudes. Therefore, compared with the case where the additional inertial body is provided on the inner peripheral portion of the internally meshing rotary element in the radial direction, or is provided approximately equally in the radial direction from the inner peripheral portion to the outer peripheral portion of the internally meshing rotary element , the inertia moment of the entire inner meshing rotating element will increase. Furthermore, the inertia moment of the internal meshing rotating element determined by the inertia moment and the angular acceleration increases. That is, the moment of inertia can be increased without particularly increasing the outer diameter of the inner meshing rotating element. In addition, the overall size of the apparatus is not particularly increased.

Description of drawings

FIG. 1 is a cross-sectional view schematically showing an example of the torsional vibration reducing device according to the first embodiment of the present invention.

FIG. 2 is an enlarged cross-sectional view showing a part of the planetary gear mechanism shown in FIG. 1 .

FIG. 3 is an enlarged side view showing a part of the ring gear.

4 is a graph showing the relationship between the engine rotational speed and the engine torque reduced by the torsional vibration reducing device.

5 is a cross-sectional view schematically showing an example of a torsional vibration reducing device according to a second embodiment of the present invention.

6 is a cross-sectional view schematically showing an example of a torsional vibration reducing device according to a third embodiment of the present invention.

7 is a cross-sectional view schematically showing an example of a torsional vibration reducing device according to a fourth embodiment of the present invention.

8 is a cross-sectional view schematically showing an example of a torsional vibration reducing device according to a fifth embodiment of the present invention.

9 is a cross-sectional view schematically showing an example of a torsional vibration reducing device according to a sixth embodiment of the present invention.

Detailed ways

Next, embodiments of the present invention will be described. FIG. 1 is a cross-sectional view showing an example of a torque converter 2 including a torsional vibration reducing device 1 as a first embodiment of the present invention. The torque converter 2 is connected to an output shaft (none of which is shown) of the driving force source. The driving force source is an internal combustion engine that outputs power by intermittently combusting a mixture of fuel and air. Therefore, the output torque of the driving force source inevitably vibrates. In addition, in the following description, the driving force source is described as an engine. The torque converter 2 has the same structure as a conventionally known torque converter, and the housing 3 of the torque converter 2 is connected to the output shaft of the engine via a front cover 4 and a pump casing integrated with the front cover 4 The body 5 is formed in a liquid-tight state.

A fluid (oil) for transmitting torque is enclosed in the casing 3 . A plurality of pump vanes 6 are mounted on the inner surface of the pump casing 5, thereby constituting a pump impeller 7. As shown in FIG. A turbine wheel 8 that rotates in response to the fluid flow generated by the pump impeller 7 is disposed opposite to the pump impeller 7 . The turbine 8 has a substantially symmetrical shape with the pump impeller 7, and is constituted by a turbine casing (not shown) and a plurality of turbine blades 9 attached to the inner surface of the turbine casing. The turbine 8 is connected to an input shaft (none of which is shown) of the transmission via a turbine hub 10 . In addition, the above-mentioned torque converter 2 corresponds to the fluid transmission device in the embodiment of the present invention, the pump impeller 7 corresponds to the driving-side member in the embodiment of the present invention, and the turbine runner 8 corresponds to the driven side member in the embodiment of the present invention. side parts. The transmission may be, for example, a conventionally known transmission such as a stepped transmission in which the gear ratio is changed stepwise, or a continuously variable transmission in which the gear ratio is continuously changed.

The stator 11 is arranged between the pump impeller 7 and the turbine 8 . The stator 11 is attached to a fixed shaft in the torque converter 2 via the one-way clutch 12 . The stator 11 is configured to change the flow direction of the oil flowing out of the turbine 8 and supply it to the pump impeller 7 when the speed of the pump impeller 7 and the turbine 8 is relatively small, and to supply it to the pump impeller 7 when the speed is relatively high. , by being pressed against the oil flowing out of the turbine 8 and rotating, the flow direction of the oil does not change. Therefore, the one-way clutch 12 is configured to be engaged in a relatively low speed state to stop the rotation of the stator 11, and to rotate the stator 11 in a relatively high speed state.

A lock-up clutch 13 is arranged to face the inner surface of the front cover 4 , and this lock-up clutch 13 corresponds to a direct clutch in the embodiment of the present invention. The lock-up clutch 13 shown in FIG. 1 is a multi-disc clutch including, for example, a plurality of clutch discs 14 and a plurality of clutch discs 16 connected to a clutch disc hub integrated into the front cover 4 . In key fitting, the clutch plate 16 is spline-fitted with the inner peripheral surface of the clutch drum 15 arranged so as to cover the outer peripheral side of the clutch disc hub, and is arranged alternately with the clutch disc 14 . These clutch discs 14 and clutch plates 16 are alternately arranged between the lockup piston 17 and a snap ring (not shown) attached to the clutch drum 15 . Therefore, by advancing the lock-up piston 17, the clutch disc 14 and the clutch plate 16 are sandwiched between the snap rings, so that the clutch disc 14 and the clutch plate 16 are brought into frictional contact, and torque is transmitted therebetween. That is, the lock-up clutch 13 is in an engaged state for transmitting torque. In the radial direction of the torque converter 2 and on the inner peripheral side of the lock-up clutch 13 , a return spring 18 is arranged in parallel with at least a part of the lock-up clutch 13 . The return spring 18 presses the lockup piston 17 in a direction in which the lockup clutch 13 is released, that is, in a direction in which the clutch disc 14 and the clutch plate 16 are separated from each other.

The above-described torsional vibration reducing device 1 is arranged adjacent to the lock-up clutch 13 in the rotational center axis direction of the torque converter 2 (hereinafter, simply referred to as the axis direction). The torsional vibration reducing device 1 includes the planetary rotation mechanism and the spring damper 19 in the embodiment of the present invention. The planetary rotation mechanism is a mechanism that performs differential action mainly by three rotational elements, such as a planetary gear mechanism and a planetary roller mechanism, and is constituted by a single-pinion type planetary gear mechanism 20 in the example shown here. 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 plurality of pinions 23 that mesh with the sun gear 21 and the ring gear 22 so as to be rotatable The carrier 24 for holding. In addition, the above-mentioned sun gear 21 corresponds to the first rotational element, the second rotational element, and the central rotational element in the embodiment of the present invention, and the ring gear 22 corresponds to the embodiment of the present invention and functions as a rotational inertia mass body The third rotating element and the internal meshing rotating element of the function, the pinion 23 corresponds to the planetary rotating element in the embodiment of the present invention, and the planetary carrier 24 corresponds to the first rotating element and the second rotating element in the embodiment of the present invention. , Rotating elements of the planetary carrier.

The clutch drum 15 of the lock-up clutch 13 and the drive plate 25 of the spring damper 19 are connected to the carrier 24, and this structure becomes 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 structure becomes an output element. On the outer peripheral portion of the ring gear 22 , an additional inertial body 27 configured to protrude in the axial direction from the ring gear 22 is integrally provided. That is, the additional inertial body 27 is provided at a position offset in the radial direction toward the outer peripheral portion of the ring gear 22 . Thereby, as in the case where the additional inertial body 27 of the same mass is provided on the inner peripheral portion of the ring gear 22 , or when the additional inertial body 27 spans from the inner peripheral portion to the outer peripheral portion of the ring gear 22 in the radial direction, approximately The inertia moment generated by the ring gear 22 becomes larger than that in the case of being equally arranged. In addition, the additional inertial body 27 may be formed separately 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 above-described spring dampers 19 are arranged concentrically with the planetary gear mechanism 20 in the radial direction of the torque converter 2 and on the inner peripheral side of the planetary gear mechanism 20 . Here, "arrangement" refers to 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 transmission direction of the torque of the spring damper 19, and is constituted by 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. In the example shown in FIG. 1 , the outer peripheral portion 25A _O of the first drive plate 25A is relatively The inner peripheral portion 25A _I is located on the side of the lock-up clutch 13 .

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. In the example shown in FIG. 1 , the outer peripheral portion 25B _O of the second drive plate 25B is relatively The inner peripheral portion _25BI is located on the turbine 8 side. Therefore, in the axial direction, the interval between the outer peripheral portion 25A _O of the first drive plate 25A and the outer peripheral portion 25B _O of the second drive plate 25B is larger than the interval between their inner peripheral portions 25A _I , 25B _I from each other, and The planetary gear mechanism 20 is arranged here. In addition, the pinion 23 of the planetary gear mechanism 20 is attached to the outer peripheral portions 25A _O , 25B _O of each of the drive disks 25A, 25B so as to be able to rotate. Therefore, each of the drive disks 25A and 25B also serves as the carrier 24 .

Annular center plates 28A, 28B are provided on the downstream sides of the respective drive disks 25A, 25B in the torque transmission direction and on both sides of the respective drive disks 25A, 25B in the axial direction, respectively. Each of the drive disks 25A, 25B and each of the center plates 28A, 28B are connected via a first spring 29 so as to be relatively rotatable by a predetermined angle. An annular driven disk 26 is arranged on the downstream side of the center plates 28A, 28B in the torque transmission direction and between the drive disks 25A, 25B in the axial direction. The driven plate 26 and each of the center plates 28A and 28B are connected via a second spring (not shown) so as to be relatively rotatable by a predetermined angle. These first springs 29 and second springs are constituted by coil springs in the example shown here, and both are set to approximately the same torsional stiffness (spring constant). External teeth are formed on the outer peripheral surface of the driven plate 26 , and this structure becomes the sun gear 21 of the planetary gear mechanism 20 as described above. The inner peripheral portion of the driven disk 26 is caulked to the turbine hub 10 described above. In addition, the first spring 29 and the second spring correspond to the elastic members in the embodiment of the present invention, and the elastic members only need to be members that mainly elastically deform to allow the relative rotation of the drive disk 25 and the driven disk 26 . .

FIG. 2 is an enlarged cross-sectional view of the planetary gear mechanism 20 shown in FIG. 1 . When the structure of the planetary gear mechanism 20 is described in detail, the pinion pin 30 is held at the outer peripheral portions 25A _O , 25B _O of the respective drive disks 25A, 25B, and the pinion pin 30 is held on the outer peripheral side of the pinion pin 30 via rollers. The pinion 23 is rotatably attached to a bearing 31 such as a needle bearing. In the axial direction, thrust washers 32 with larger diameters are provided on both sides of the pinion gear 23 . The outer diameter of the thrust washer 32 is set to be slightly larger than the pitch circle diameter of the ring gear 22 . On both sides of each thrust washer 32 , other washers 33 having a smaller diameter than the thrust washer 32 are provided. These washers 32 and 33 receive the component force in the axial direction caused by the meshing of the pinion gear 23 and the sun gear 21, and the component force in the axial direction caused by the meshing of the pinion gear 23 and the ring gear 22, and Movement of the ring gear 22 in the axial direction due to the above-described component force is suppressed. In addition, as described above, the additional inertial body 27 is formed so as to protrude more in the axial direction than the ring gear 22 , and the inner diameter of the additional inertial body 27 is set to match the outer diameter of the clutch drum 15 and the thrust The outer diameter of the gasket 32 is relatively large. Therefore, interference between the additional inertial body 27 and the clutch drum 15 or the thrust washer 32 can be avoided or suppressed.

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

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 at the outer peripheral portion of the ring gear 22 so as to leave a predetermined gap C with the inner surface 36 of the housing 3 . In order to avoid or suppress interference between the additional inertial body 27 and the inner surface 36 of the housing 3, the clearance C is determined in design.

Next, the operation of the first embodiment will be described. When the lock-up clutch 13 is in the engaged state, engine torque is input to the carrier 24 . On the other hand, the sun gear 21 acts on the sun gear 21 via the first spring 29 and the second spring with torque for rotating the transmission (not shown). Therefore, with these torques for rotating the engine and the transmission, a load that compresses the first spring 29 and the second spring is generated, and the first spring 29 and the second spring generate a load corresponding to the load. corresponding displacement. As a result, the carrier 24 and the sun gear 21 are relatively rotated by a predetermined angle, and the respective drive plates 25A, 25B and the driven plate 26 are relatively rotated by a predetermined angle.

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

In addition, since the additional inertial body 27 is provided so as to be biased toward the outer peripheral portion of the ring gear 22 , it is different from providing the additional inertial body 27 on the inner peripheral portion of the ring gear 22 , or disposing it radially from the inside. Compared with the case where the inner peripheral portion of the meshing gear 22 is provided approximately equally across the outer peripheral portion, the inertia moment of the ring gear 22 becomes larger. As a result, the inertia moment of the ring gear 22 determined by the inertia moment and the angular acceleration increases. Since this inertia torque acts as a damping torque against the vibration of the engine torque, the engine torque input to the planetary carrier 24 is reduced by the inertia torque of the ring gear 22 and becomes smoother , and is output from the driven disc 26 . Furthermore, 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 or the torsional vibration reducing device 1 is not particularly enlarged in size. In addition, in the above-mentioned configuration, since 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, the factor that hinders the rotation of the ring gear 22 can be eliminated. , so that the ring gear 22 rotates smoothly.

FIG. 4 is a graph showing the relationship between the engine rotational speed and the engine torque reduced by the torsional vibration reducing device 1 . In the first embodiment, the inertia moment of the ring gear 22 can be increased in the above-described manner, and therefore, compared with the case where the inertia moment of the ring gear 22 is not increased, as shown in FIG. 4 . , the anti-resonance point A of the engine speed ω ₀ at which the vibration of the torque at the driven disk 26 is minimized is shifted to the low speed side. Thereby, the vibration of the torque in the low-speed range can be smoothed, and the lock-up clutch 13 can be engaged in the low-speed range. That is, since the rotational speed region in which the lock-up clutch 13 can be maintained in the engaged state is expanded toward the low rotational speed side, the fuel economy can be improved.

In addition, the engine rotational speed ω ₀ at the anti-resonance point A can be calculated by the following formula (1). In the following formula (1), “K ₁ ” represents the torsional stiffness (spring constant) of the first spring 29, “K ₂ ” represents the torsional stiffness (spring constant) of the second spring, and “IR” _represents the above-mentioned On the other hand, the moment of inertia of the ring gear 22 provided with the additional inertial body 27, “I ₂ ” represents the moment of inertia of the center plates 28A and 28B, and “B” is obtained by dividing the number of teeth of the sun gear 21 by the number of teeth of the ring gear 22 . the gear ratio of the planetary gear mechanism 20 .

Mathematical formula 1

As shown in the formula (1), the larger the moment of inertia IR of the _ring gear 22 is, the smaller the engine speed ω ₀ corresponding to the anti-resonance point A is. Therefore, in the first embodiment, the inertia moment IR of the _ring gear 22 is calculated so that the vibration of the torque output from the driven plate 26 is minimized _at the engine speed ω0 determined in design. set up. In addition, in the first embodiment, since the additional inertial body 27 is provided so as to be biased toward the outer peripheral portion of the ring gear 22 , it is different from the case where the additional inertial body 27 is provided at the inner peripheral portion of the ring gear 22 . In contrast, it is possible to reduce the mass of the additional inertial body 27 required to obtain the inertia moment IR required in design _. That is, a larger moment of inertia IR can be obtained with a smaller mass _.

The present invention is not limited to the above-described embodiment, and the additional inertial body 27 may be provided mainly to increase the mass of the outer peripheral portion of the ring gear 22 larger than the mass of the inner peripheral portion. 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 8 side among both side surfaces of the ring gear 22 in the axial direction. In the configuration shown in FIG. 5 , it is possible to further suppress interference with the lock-up clutch 13 while obtaining the same functions and effects as those of the first embodiment shown in FIG. 1 .

The example shown in FIG. 6 is an example in which the outer peripheral surface of the additional inertial body 27 having the structure shown in FIG. 2 is formed according to the shape of the inner surface 36 of the casing 3 . In the configuration shown in FIG. 6 , the mass of the additional inertial body 27 can be increased as much as possible while the interference with the inner surface 36 of the casing 3 is further suppressed, and the gap C can be made as large as possible. decrease.

The example shown in FIG. 7 is an example in which the additional inertial body 27 and the ring gear 22 of the structure shown in FIG. 2 are formed separately. The additional inertial body 27 shown in FIG. 7 is formed in a cylindrical shape whose length in the axial direction is longer than that of the ring gear 22 , and the ring gear 22 is fixed therein by predetermined fixing means. The fixing means may be a conventionally known fixing means, for example, press-fitting, welding, riveting, or bolting. In the structure 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 increase in cost can be kept to a minimum. In addition, the moment of inertia of the ring gear 22 can be increased or decreased by replacing the additional inertial body 27 attached to the ring gear 22 with the additional inertial body 27 having a different axial length or outer diameter. Tuning of the moment of inertia of the ring gear 22 is easily carried out. Even with the configuration shown in FIG. 7 , the same operations and effects as those of the first embodiment shown in FIG. 1 can be obtained.

The example shown in FIG. 8 is an example in which additional inertial bodies 27 formed by annular plates are provided on both side surfaces of the ring gear 22 in the axial direction. The outer peripheral portion of the additional inertial body 27 becomes a protruding portion 27A protruding in the axial direction, and as shown in FIG. 8 , the cross-section of the additional inertial body 27 is formed in an L-shape. In addition, 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 is set to be the same as that of the thrust washer in order to avoid interference with the thrust washer 32 . The outer diameter of 32 is larger in comparison. The additional inertial bodies 27 are respectively welded, riveted or bolted to both sides of the ring gear 22 . In the configuration shown in FIG. 8 , since the additional inertial body 27 can be formed by, for example, pressing, the manufacturing cost of the additional inertial body 27 can be minimized. In addition, since the inertia moment of the ring gear 22 can be increased or decreased by replacing the additional inertia body 27 attached to the ring gear 22 with the additional inertia body 27 having a different size of the protruding portion 27A, it is possible to easily Tuning of the moment of inertia of the ring gear 22 is carried out. Even with the configuration shown in FIG. 8 , the same operations and effects as those 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 8 side among both side surfaces of the ring gear 22 in the axial direction. With such a configuration, the interference with the lock-up clutch 13 can be further suppressed, and the same operations and effects as those of the first embodiment shown in FIGS. 1 and 8 can be obtained.

Furthermore, in the embodiment of the present invention, the sun gear may be used as the input element, and the carrier may be used as the output element. The point is that it is only necessary to configure the ring gear so as to function as a rotational inertia mass body. Furthermore, the planetary rotation mechanism in the embodiment of the present invention is not limited to the gears, and may be constituted by rollers.

Symbol Description

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

Claims (7)

1. A torsional vibration reducing device, comprising: A planetary rotating mechanism having a first rotating element to which torque is input, a second rotating element, and a third rotating element functioning as a rotating inertial mass body, and having the first rotating element and the second rotating element element and said third rotation element to perform a differential action; an elastic member that connects the first rotation element and the second rotation element so as to be relatively rotatable by a predetermined angle, The torsional vibration reducing device is configured such that the elastic member is elastically deformed by the vibration of the torque to relatively rotate the first rotating element and the second rotating element, And, vibration is generated during the rotation of the third rotating element, The torsional vibration reducing device is characterized in that: In the radial direction of the planetary rotating mechanism and at the outer peripheral portion of the third rotating element, and so as to protrude from the third rotating element in the direction of the rotation center axis of the planetary rotating mechanism, there is a An additional inertial body is attached to the third rotation element, The planetary rotation mechanism has: center rotation element; an internal meshing rotating element, which is arranged on a concentric circle with respect to the central rotating element; A carrier rotating element that holds a plurality of planetary rotating elements, the planetary rotating elements being arranged between an outer peripheral portion of the central rotating element and an inner peripheral portion of the inner meshing rotating element and passing through the The center rotation element and the inner meshing rotation element rotate relative to each other so as to rotate and revolve, The first rotation element is set as one of the center rotation element and the carrier rotation element, The second rotation element is set as the other of the center rotation element and the carrier rotation element, The third rotation element is set as the internal meshing rotation element. 2. The torsional vibration reducing device according to claim 1, wherein: The additional inertial body is formed in a cylindrical shape having a length in the rotation center axis direction longer than that of the internal meshing rotating element, and the internal meshing rotating element is integrated in the radial direction. on the inner peripheral surface of the additional inertial body. 3. The torsional vibration reducing device according to claim 1, wherein: The additional inertial body is formed by an annular plate having the same outer diameter as the outer diameter of the inner meshing rotating element and an inner diameter larger than the inner diameter of the inner meshing rotating element, The outer peripheral portion of the plate is provided with a protruding portion protruding in the direction of the rotation center axis, The plate is provided on at least one side surface of both side surfaces of the inner meshing rotating element in the direction of the rotation center axis. 4. The torsional vibration reducing device according to any one of claims 1 to 3, characterized in that: On the inner side of the planetary rotation mechanism in the radial direction, the elastic members are arranged concentrically with the planetary rotation mechanism. 5. The torsional vibration reducing device according to any one of claims 1 to 3, wherein: With a fluid transmission device, the fluid transmission device has: a casing, which is attached to the engine; a drive-side member that is attached to the housing and causes fluid flow; A driven side member driven by said fluid flow; a direct clutch that connects the drive-side member and the driven-side member by engaging with the inner surface of the housing, The planetary rotation mechanism is provided inside the fluid transmission device. 6. The torsional vibration reducing device according to any one of claims 1 to 3, wherein: The first rotation element is set as the carrier rotation element, The second rotation element is set as the center rotation element. 7. The torsional vibration mitigating device according to any one of claims 1 to 3, wherein: The central rotating element of the planetary rotating mechanism is constituted by a sun gear, the ring rotating element is constituted by a ring gear, the planetary rotating element is constituted by a pinion, and the planetary carrier rotates The element is constituted by a carrier that holds the pinion.

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