JP2020106034A - Damper device - Google Patents

Abstract

To improve reliability and durability of a rotary inertia mass damper including a planetary gear mechanism.SOLUTION: A rotary inertia mass damper of a damper device includes a planetary gear mechanism comprising a sun gear, a ring gear, a plurality of pinion gears, and a carrier supporting a plurality of pinion shafts inserted into central holes of the corresponding pinion gears respectively. The carrier of the planetary gear mechanism rotates integrally with a first rotary element of the damper device. One of the sun gear and the ring gear rotates integrally with a second rotary element of the damper device. The other of the sun gear and the ring gear functions as a mass body of the rotary inertia mass damper. Oil passages for guiding oil supplied into an oil chamber to gaps between the pinion gears and the pinion shafts are formed in at least one of the pinion gears and members arranged in proximity to end surfaces of the pinion gears.SELECTED DRAWING: Figure 5

Description

The present disclosure relates to a damper device including an elastic body and a rotary inertia mass damper that transmit torque between an input element and an output element.

Conventionally, as a rotary inertia mass damper of this type of damper device, a sun gear that rotates integrally with an output element, a carrier that rotatably supports a plurality of pinion gears and that rotates integrally with an input element, and a plurality of pinion gears A device having a planetary gear mechanism including a ring gear that functions as a mass body is known (see, for example, Patent Document 1). In this rotary inertia mass damper, the ring gear as the mass body oscillates around the axis according to the relative rotation between the input element and the output element, and has a phase opposite to the vibration transmitted from the elastic body to the output element. (Inertial torque) is transmitted to the output element via the pinion gear. With this, one of the vibration transmitted from the elastic body to the output element and the vibration transmitted from the rotary inertia mass damper to the output element cancels out at least a part of the other, and the vibration of the output element is appropriately damped. Is possible.

International Publication No. 2016/208767

In the rotary inertia mass damper as described above, when the ring gear as the mass body oscillates in response to the rotation of the input element, that is, the carrier of the planetary gear mechanism, each pinion gear does not rotate in one direction and rotates around the axis. Rock to. Therefore, only the limited gear teeth of each pinion gear mesh with the corresponding gear teeth of the ring gear or the sun gear. Therefore, in the rotary inertia mass damper including the planetary gear mechanism, oil film breakage due to heat generation and wear of the pinion gear and pinion shaft are likely to occur around the gear teeth of each pinion gear meshing with the ring gear and the sun gear, which may reduce reliability and reliability. There is also a possibility that durability will be reduced.

Therefore, the present disclosure mainly aims to improve reliability and durability of a rotary inertia mass damper including a planetary gear mechanism.

A damper device of the present disclosure includes a plurality of rotating elements including an input element and an output element to which torque from an engine is transmitted, an elastic body that transmits torque between the input element and the output element, and the plurality of rotating elements. A rotary inertia mass damper having a mass body that oscillates around an axis according to relative rotation between a first rotary element that is one of the rotary elements and a second rotary element that is different from the first rotary element; In the damper device arranged in the oil chamber, the rotary inertia mass damper includes a sun gear, a ring gear, a plurality of pinion gears, and a carrier that supports a plurality of pinion shafts that are respectively inserted through the center holes of the corresponding pinion gears. A planetary gear mechanism having, wherein the carrier rotates integrally with the first rotating element, one of the sun gear and the ring gear rotates integrally with the second rotating element, and the other of the sun gear and the ring gear rotates. , The pinion gear, which functions as the mass body, and at least one of the members arranged in proximity to the end face of the pinion gear, supplies the oil supplied into the oil chamber between the pinion gear and the pinion shaft. An oil passage for guiding is formed.

The damper device of the present disclosure includes a rotary inertia mass damper having a mass body that swings around an axis according to relative rotation between the first rotating element and the second rotating element, and is arranged in the oil chamber. The rotary inertia mass damper has a sun gear, a ring gear, a plurality of pinion gears, and a carrier that supports a plurality of pinion shafts that are inserted through the center holes of the corresponding pinion gears. An oil passage that guides the oil supplied into the oil chamber between the pinion gear and the pinion shaft is formed in at least one of the pinion gear and a member arranged near the end surface of the pinion gear. As a result, when the ring gear as the mass body oscillates, even if only the limited gear teeth of each pinion gear mesh with the corresponding gear teeth of the ring gear or the sun gear, the oil supplied to the oil chamber can be supplied to the pinion gear and the pinion gear. It can be guided between the shaft and the both, and both can be satisfactorily lubricated and cooled. As a result, it is possible to satisfactorily suppress oil film breakage due to heat generation and wear of the pinion gear and pinion shaft, and to improve the reliability and durability of the rotary inertia mass damper including the planetary gear mechanism.

It is a schematic structure figure of a starting device containing a damper device of this indication. It is sectional drawing which shows the damper apparatus of this indication. It is a front view showing a damper device of this indication. It is a principal part enlarged view which shows the rotary inertia mass damper of the damper apparatus of this indication. It is a principal part enlarged view which shows the rotary inertia mass damper of the damper apparatus of this indication. FIG. 9 is an enlarged view showing another pinion gear applicable to the rotary inertia mass damper of the damper device of the present disclosure. FIG. 9 is an enlarged view showing another washer applicable to the rotary inertia mass damper of the damper device of the present disclosure. FIG. 8 is an enlarged view showing still another washer applicable to the rotary inertia mass damper of the damper device of the present disclosure. It is a schematic block diagram which shows the other damper apparatus of this indication. It is a schematic structure figure showing other damper devices of this indication. It is a schematic block diagram which shows the other damper apparatus of this indication.

Next, a mode for carrying out the invention of the present disclosure will be described with reference to the drawings.

FIG. 1 is a schematic configuration diagram showing a starting device 1 including a damper device 10 of the present disclosure, and FIG. 2 is a sectional view showing the starting device 1. The starting device 1 shown in these drawings is mounted on a vehicle including an engine (internal combustion engine) EG as a drive device, and is connected to a crankshaft of the engine EG in addition to the damper device 10. Front cover 3 as an input member for transmitting torque from the pump, a pump impeller (input side fluid transmission element) 4 fixed to the front cover 3, and a turbine runner (output side fluid transmission) rotatable coaxially with the pump impeller 4. Element) 5, a damper hub 7 as an output member which is connected to the damper device 10 and is fixed to the input shaft IS of the transmission TM which is an automatic transmission (AT) or a continuously variable transmission (CVT), and a lockup clutch 8 Including etc.

In the following description, the "axial direction" basically indicates the extending direction of the central axes (axial centers) of the starting device 1 and the damper device 10 unless otherwise specified. Further, the “radial direction” is basically the radial direction of the starting device 1, the damper device 10, and the rotating elements such as the damper device 10, that is, the center of the starting device 1 and the damper device 10, unless otherwise specified. The extending direction of a straight line extending from the axis in the direction (radial direction) orthogonal to the central axis is shown. Further, the "circumferential direction" is basically the circumferential direction of the starting device 1, the damper device 10, and the rotating elements such as the damper device 10, that is, the rotational direction of the rotating element, unless otherwise specified. Indicates the direction.

The pump impeller 4 is arranged on the inner surface of the pump shell 40, which is tightly fixed to the front cover 3 and defines a fluid chamber (oil chamber) 9 through which the working oil flows together with the front cover 3. And a plurality of pump blades 41. The turbine runner 5 has a turbine shell 50 and a plurality of turbine blades 51 arranged on the inner surface of the turbine shell 50. The inner peripheral portion of the turbine shell 50 is fixed to the damper hub 7 via a plurality of rivets. The pump impeller 4 and the turbine runner 5 face each other, and a stator 6 that rectifies the flow of the working oil (working fluid) from the turbine runner 5 to the pump impeller 4 is coaxially arranged between them. The stator 6 has a plurality of stator blades 60, and the one-way clutch 61 sets the rotation direction of the stator 6 in only one direction. The pump impeller 4, the turbine runner 5, and the stator 6 form a torus (annular flow path) for circulating the hydraulic oil, and function as a torque converter (fluid transmission device) having a torque amplification function. However, in the starting device 1, the stator 6 and the one-way clutch 61 may be omitted and the pump impeller 4 and the turbine runner 5 may function as a fluid coupling.

The lockup clutch 8 performs lockup for connecting the front cover 3 and the damper hub 7 via the damper device 10 and releases the lockup. In the present embodiment, the lockup clutch 8 is a single-plate hydraulic clutch including a lockup piston 80 to which a friction material 81 is attached. The lockup piston 80 of the lockup clutch 8 is axially movably fitted to the damper hub 7 so as to be located inside the front cover 3 on the opposite side of the turbine runner 5 with respect to the damper device 10. It faces the inner wall surface of the cover 3 on the engine EG side. However, the lockup clutch 8 may be a multi-plate hydraulic clutch.

As shown in FIGS. 1 and 2, the damper device 10 includes a drive member (input element) 11 and a driven member (output element) 15 as rotating elements. Further, the damper device 10 serves as a torque transmission element (torque transmission elastic body) and includes a plurality of (for example, six in this embodiment) that act in parallel between the drive member 11 and the driven member 15 to transmit torque. The first spring (first elastic body) SP1 and a plurality of (for example, three in this embodiment) second springs (third in the present embodiment) capable of acting in parallel between the drive member 11 and the driven member 15 to transmit torque. 2 elastic body) SP2.

As shown in FIG. 1, the plurality of first springs SP1 form a first torque transmission path TP1 that transmits torque between the drive member 11 and the driven member 15. The plurality of second springs SP2 form a second torque transmission path TP2 that transmits torque between the drive member 11 and the driven member 15. As illustrated, the second torque transmission path TP2 is provided in parallel with the first torque transmission path TP1. The plurality of second springs SP2 of the second torque transmission path TP2 are such that the input torque (driving torque) to the drive member 11 or the torque (driven torque) applied to the driven member 15 from the axle side is the maximum torsion of the damper device 10. The torque is a predetermined torque (first threshold) T1 that is smaller than the torque T2 (second threshold) corresponding to the angle θmax, and the twist angle of the drive member 11 with respect to the driven member 15 is a predetermined angle θref or more. At times, it acts in parallel with the first spring SP1 of the first torque transmission path TP1. As a result, the damper device 10 has a two-stage (two-stage) damping characteristic.

Further, in the present embodiment, as the first and second springs SP1 and SP2, linear coil springs made of a metal material spirally wound so as to have a straight axis extending when no load is applied are linear coil springs. Has been adopted. As a result, the first and second springs SP1 and SP2 can be more appropriately expanded and contracted along the axial center, as compared with the case where the arc coil spring is used. As a result, the torque transmitted from the first spring SP1 or the like to the driven member 15 when the relative displacement between the drive member 11 (input element) and the driven member 15 (output element) increases, and the drive member 11 and the driven member. It is possible to reduce the difference between the torque transmitted from the first spring SP1 and the like to the driven member 15, that is, the hysteresis when the relative displacement with the member 15 decreases. However, an arc coil spring may be adopted as at least one of the first and second springs SP1 and SP2.

As shown in FIG. 2, the drive member 11 of the damper device 10 includes a plurality of annular first input plates 12 connected to the lock-up piston 80 of the lock-up clutch 8 and a plurality of opposing first input plates 12. It includes an annular second input plate 13 connected to the first input plate 12 via a rivet (connecting member) 90 (see FIG. 3 ). As a result, the drive member 11, that is, the first and second input plates 12 and 13 rotates integrally with the lockup piston 80, and the lockup clutch 8 engages to lock the front cover 3 (engine EG) and the damper device 10. The drive member 11 will be connected.

The first input plate 12 is an annular stamped product formed by stamping a steel plate or the like, and as shown in FIGS. 2 and 3, each extends in an arc shape and is spaced apart in the circumferential direction ( A plurality of (for example, six in the present embodiment) inner spring accommodation windows (first accommodation windows) 12wi arranged at equal intervals and a plurality (a plurality of books) extending along the inner edge of each inner spring accommodation window 12wi. In the embodiment, for example, six spring support portions 12a, a plurality (for example, six in this embodiment) of spring support portions 12b extending along the outer edge of each inner spring accommodation window 12wi, and each inner spring. It includes a plurality (for example, 12 in this embodiment) of inner spring contact portions 12ci provided on both sides of the accommodation window 12wi in the circumferential direction. As can be seen from FIG. 3, each inner spring accommodation window 12wi has a peripheral length corresponding to the natural length of the first spring SP1.

Further, the plurality of first input plates 12 extend in an arc shape and are arranged at equal intervals in the circumferential direction on the outer side in the radial direction of the corresponding inner spring housing windows 12wi (in the present embodiment, For example, three (3) outer spring accommodation windows (second accommodation windows) 12wo, and a plurality of (for example, three in this embodiment) spring support portions 12d extending along the outer edge of each outer spring accommodation window 12wo, A plurality of (for example, six in the present embodiment) outer spring contact portions 12co provided on both sides in the circumferential direction of each outer spring housing window 12wo are included. As shown in FIG. 3, each outer spring accommodating window 12wo has a circumference longer than the natural length of the second spring SP2.

Further, the outer peripheral portion 12o of the first input plate 12 is formed into a flat and annular shape, and is circumferentially spaced (equal spacing) so as to be located radially outside of the corresponding outer spring accommodation window 12wo. The plurality of (for example, three in this embodiment) pinion gear support portions 12p arranged in the above, and a portion positioned on the outer side in the radial direction of each outer spring accommodating window 12wo are included. Further, the outer peripheral portion 12o of the first input plate 12 is disposed on the same side as the spring supporting portions 12a, 12b, 12d from the inner peripheral portion 12i including a plurality of inner spring accommodating windows 12wi and outer spring accommodating windows 12wo, respectively. It is offset axially of the device 10. The outer peripheral portion 12o is connected to the inner peripheral portion 12i via a short tubular and endless connecting portion 12r extending along the plurality of pinion gear supporting portions 12p and the plurality of outer spring accommodating windows 12wo.

The second input plate 13 is an annular stamped product formed by stamping a steel plate or the like, and as shown in FIGS. 2 and 3, extends in an arc shape and is spaced apart in the circumferential direction ( A plurality of (for example, six in this embodiment) inner spring accommodation windows (first accommodation windows) 13wi arranged at equal intervals, and a plurality (books) extending along the inner edge of each inner spring accommodation window 13wi. In the embodiment, for example, six spring support portions 13a, a plurality (for example, six in the present embodiment) of spring support portions 13b extending along the outer edge of each inner spring housing window 13wi, and each inner spring. It includes a plurality of (for example, 12 in this embodiment) inner spring contact portions 13ci provided on both sides in the circumferential direction of the accommodation window 13wi. Each inner spring accommodating window 13wi has a peripheral length corresponding to the natural length of the first spring SP1 similarly to each inner spring accommodating window 12wi of the first input plate 12.

Further, the plurality of second input plates 13 extend in an arc shape and are arranged radially outward of the corresponding inner spring accommodating windows 13wi at intervals (at equal intervals) in the circumferential direction (in the present embodiment, For example, three outer spring housing windows (second housing windows) 13wo, and a plurality (for example, three in this embodiment) of spring support portions 13d extending along the outer edge of each outer spring housing window 13wo, It includes a plurality of (for example, six in the present embodiment) outer spring contact portions 13co provided on both sides in the circumferential direction of each outer spring housing window 13wo. Each outer spring accommodation window 13wo has a peripheral length longer than the natural length of the second spring SP2, similarly to each outer spring accommodation window 12wo of the first input plate 12.

Further, the outer peripheral portion 13o of the second input plate 13 is formed in a flat and annular shape, and is circumferentially spaced (equal intervals) so as to be located radially outside of the corresponding outer spring accommodation window 13wo. A plurality of (for example, three in this embodiment) pinion gear support portions 13p arranged in the above, and a portion located radially outside of each outer spring accommodating window 13wo. Further, the outer peripheral portion 13o of the second input plate 13 is disposed on the same side as the spring supporting portions 13a, 13b, 13d from the inner peripheral portion 13i including the plurality of inner spring accommodating windows 13wi and the outer spring accommodating windows 13wo, respectively. It is offset axially of the device 10. The outer peripheral portion 13o is connected to the inner peripheral portion 13i via a short tubular endless connecting portion 13r extending along the plurality of pinion gear supporting portions 13p and the plurality of outer spring accommodating windows 13wo. In the present embodiment, the first and second input plates 12 and 13 having the same shape are adopted, which makes it possible to reduce the number of types of parts.

The driven member 15 is a plate-shaped and annular press-formed product formed by pressing a steel plate or the like, is arranged between the first and second input plates 12 and 13 in the axial direction, and includes a plurality of members. It is fixed to the damper hub 7 via rivets. As shown in FIGS. 2 and 3, the driven member 15 includes a plurality of (for example, six in this embodiment) inner spring holding windows (first portions) arranged at intervals (equal intervals) in the circumferential direction. (Holding window) 15wi, a plurality (for example, 12 in this embodiment) of inner spring contact portions 15ci provided on both sides in the circumferential direction of each inner spring housing window 12wi, and the corresponding inner spring holding window 15wi in the radial direction. A plurality of (for example, three in this embodiment) outer spring holding windows 15wo (second holding windows) arranged on the outer side, and a plurality (in this embodiment in the present embodiment) provided on both sides of each outer spring housing window 12wo in the circumferential direction. , For example, 6) outer spring contact portions 15co.

As can be seen from FIG. 3, each inner spring holding window 15wi has a circumference corresponding to the natural length of the first spring SP1, and each outer spring holding window 15wo has a circumference corresponding to the natural length of the second spring SP2. Have a length. Further, in the present embodiment, the driven members 15 are plural (for example, three in the present embodiment) formed so as to project outward in the radial direction at intervals (at equal intervals) in the circumferential direction from the outer peripheral portion. Each of the protrusions 15e is formed with one outer spring holding window 15wo.

One first spring SP1 is arranged (fitted) in each inner spring holding window 15wi of the driven member 15, and the plurality of first springs SP1 are arranged on the same circumference. The inner spring contact portions 15ci provided on both sides in the circumferential direction of each inner spring holding window 15wi contact one end or the other end of the first spring SP1 in the inner spring holding window 15wi. Further, one second spring SP2 is arranged (fitted) in each of the outer spring holding windows 15wo of the driven member 15, and the plurality of second springs SP2 are smaller than the plurality of first springs SP1 in the driven member 15. Lined up on the same circumference on the outside in the radial direction. The outer spring contact portions 15co provided on both sides of each outer spring holding window 15wo in the circumferential direction contact one end or the other end of the second spring SP2 in the outer spring holding window 15wo.

The first and second input plates 12 and 13 of the drive member 11 include a plurality of rivets 90 so as to sandwich the driven member 15, the plurality of first springs SP1 and the plurality of second springs SP2 from both sides in the axial direction of the damper device 10. Are connected to each other via. As a result, the side portion of each first spring SP1 is accommodated in the corresponding inner spring accommodation windows 12wi, 13wi of the first and second input plates 12, 13 and is supported from the radially inner side by the spring support portions 12a, 13a. (Guided). Furthermore, each of the first springs SP1 can be supported (guided) by the spring supporting portions 12b and 13b of the first and second input plates 12 and 13 located on the radially outer side. Further, in the mounted state of the damper device 10, the inner spring contact portions 12ci provided on both sides in the circumferential direction of each inner spring housing window 12wi and the inner spring contact portions 12ci provided on both sides in the circumferential direction of each inner spring housing window 13wi. The contact portion 13ci is in contact with one end or the other end of the first spring SP1 in the inner spring housing windows 12wi and 13wi. As a result, the drive member 11 and the driven member 15 are connected via the plurality of first springs SP1.

Further, the side portions of each second spring SP2 are housed in the corresponding outer spring housing windows 12wo, 13wo of the first and second input plates 12, 13 by the spring support portions 12d, 13d located radially outside. Be able to be supported (guided). In the mounted state of the damper device 10, each second spring SP2 is located at a substantially central portion in the circumferential direction of the outer spring housing windows 12wo and 13wo, and the outer spring contact portions 12co of the first and second input plates 12 and 13 are located. , 13co does not abut. Then, at one end of the second spring SP2, the input torque (driving torque) to the drive member 11 or the torque (driven torque) applied to the driven member 15 from the axle side reaches the torque T1 and the drive member is driven. When the twist angle of 11 with respect to the driven member 15 becomes equal to or more than the predetermined angle θref, the outer spring contact portions 12co, 13co provided on both sides of the corresponding outer spring accommodating windows 12wo, 13wo of the first and second input plates 12, 13. Will come into contact with one of the two.

In addition, the damper device 10 includes a stopper 17 that restricts relative rotation between the drive member 11 and the driven member 15. When the input torque to the drive member 11 reaches the torque T2 corresponding to the maximum twist angle θmax of the damper device 10, the stopper 17 restricts the relative rotation between the drive member 11 and the driven member 15, and accordingly. All bending of the first and second springs SP1 and SP2 is restricted. In the present embodiment, the stopper 17 is composed of a plurality of rivets 90 that connect the first and second input plates 12 and 13 of the drive member 11 and each protruding portion 15e of the driven member 15. That is, when at least one of the plurality of rivets 90 comes into contact with the end of the corresponding protruding portion 15e of the driven member 15 in the circumferential direction, the relative rotation between the drive member 11 and the driven member 15 is restricted.

Furthermore, as shown in FIGS. 1 and 2, the damper device 10 includes both a first torque transmission path TP1 including a plurality of first springs SP1 and a second torque transmission path TP2 including a plurality of second springs SP2. And a rotary inertia mass damper 20 provided in parallel with each other. In the present embodiment, the rotary inertia mass damper 20 has a single pinion type planetary gear mechanism 21 (see FIG. 1) arranged between the drive member 11 which is an input element of the damper device 10 and the driven member 15 which is an output element. ) Has.

The planetary gear mechanism 21 includes a driven member 15 that includes external teeth 15ts on the outer periphery and functions as a sun gear of the rotary inertia mass damper 20 (planetary gear mechanism 21), and a plurality of members that mesh with the external teeth 15ts (in this embodiment, for example, The first and second input plates 12 and 13 of the drive member 11 that rotatably supports three (3) pinion gears 23 and functions as a carrier, and the driven member 15 (external teeth 15ts that meshes with each pinion gear 23 and serves as a sun gear). ) And a ring gear 25 arranged concentrically. In the fluid chamber 9, the driven member 15 as the sun gear, the plurality of pinion gears 23, and the ring gear 25 at least partially overlap with the first and second springs SP1 and SP2 in the radial direction of the damper device 10. This makes it possible to reduce the axial length of the rotary inertia mass damper 20 and thus the damper device 10.

As shown in FIG. 2 and FIG. 4, the external teeth 15ts are formed on the outer peripheral surface of the driven member 15 at a plurality of positions that are circumferentially spaced (equal spacing). That is, in this embodiment, the external teeth 15ts are formed between the outer peripheral surfaces of the driven member 15 in the circumferential direction of the adjacent protruding portions 15e. Therefore, the outer teeth 15ts are located radially outside of the inner spring holding window 15wi, that is, the first spring SP1 that transmits torque between the drive member 11 and the driven member 15. If the protruding portion 15e is not formed on the driven member 15, the outer teeth 15ts may be formed on the entire outer periphery of the driven member 15.

Each pinion gear support portion 12p of the first input plate 12 that constitutes the carrier of the planetary gear mechanism 21 axially opposes the corresponding pinion gear support portion 13p of the second input plate 13, and forms a pair with each other. 13p supports the corresponding ends of the pinion shafts 24 inserted into the pinion gears 23, respectively. Accordingly, the plurality of pinion gears 23 of the planetary gear mechanism 21 are arranged such that the plurality of second springs are arranged outside the plurality of first springs SP1 in the radial direction of the driven member 15 and inside the ring gear 25 in the corresponding radial direction. It is arranged so as to line up with SP2 in the circumferential direction. Further, rivets 90 for fastening the first and second input plates 12 and 13 are arranged on both sides of the pinion shaft 24 in the circumferential direction.

As shown in FIG. 4, the pinion gear 23 is an annular member having outer teeth (gear teeth) 23t on the outer circumference, and the tooth width of the pinion gear 23 is smaller than the tooth width of the outer teeth 15ts, that is, the plate thickness of the driven member 15. Is also largely defined. A plurality of needle bearings 230 are arranged in the center hole 23o of the pinion gear 23, that is, between the inner peripheral surface of the pinion gear 23 and the outer peripheral surface of the pinion shaft 24. Further, as shown in FIG. 5, a plurality of oil grooves 23g are formed on the end faces on both sides in the axial direction of each pinion gear 23 so as to open in the center hole 23o side and the outer teeth 23t side and extend in the radial direction. Has been formed. Each oil groove 23g functions as an oil passage that guides the hydraulic oil supplied into the fluid chamber 9 between the corresponding inner peripheral surface of the pinion gear 23 and the pinion shaft 24 (in the center hole 23o). A pair of large-diameter washers 231 is arranged on both sides of each pinion gear 23 in the axial direction. The small-diameter washer 232 is arranged.

As shown in FIG. 4, the ring gear 25 of the planetary gear mechanism 21 includes an annular inner gear 250 having inner teeth 250t formed on the inner periphery thereof and two annular weight bodies 251 (first and second weights). Body), and a plurality of rivets 252 for fixing the internal gear 250 and the two weight bodies 251 to each other. The internal gear 250 and the weight 251 are both press-worked products formed by pressing a steel plate or the like. The two weights 251 are arranged on both sides of the internal gear 250 in the axial direction so as to contact one or the other end surface of the internal gear 250. The internal gear 250, the two weight bodies 251, and the plurality of rivets 252 are integrated and function as a mass body (inertial mass body) of the rotary inertia mass damper 20. In this way, by using the ring gear 25 arranged on the outermost periphery of the planetary gear mechanism 21 as the mass body of the rotary inertia mass damper 20, the moment of inertia of the ring gear 25 is further increased and the vibration of the rotary inertia mass damper 20 is increased. The damping performance can be further improved.

In the present embodiment, the internal teeth 250t are formed over the entire inner peripheral surface of the internal gear 250. However, the internal teeth 250t may be formed on the inner peripheral surface of the internal gear 250 at a plurality of positions that are circumferentially spaced (equal spacing). The tooth width of the internal gear 250 is smaller than the tooth width of the pinion gear 23, and is substantially the same as the tooth width of the external teeth 15ts, that is, the plate thickness of the driven member 15. Further, the axial length (thickness) of the weight 251 is determined so that the sum of the axial length of the two weights 251 and the axial length (thickness) of the internal gear 250 is substantially the same as the axial length of the pinion gear 23. ing. The weight body 251 may be formed by dividing the annular member as described above, and may include a plurality of segments each fixed to the internal gear 250 via the rivet 252.

Further, the movement of the ring gear 25 in the axial direction is regulated by the large-diameter washer 231 capable of contacting the end surface of the corresponding weight body 251. That is, the outer diameter of the large diameter washer 231 is such that, when each pinion gear 23 and the inner teeth 250t of the ring gear 25 mesh, the large diameter washer 231 faces the end surface of the pinion gear 23 in the axial direction and the weight of the ring gear 25. It is set so as to face the end face of the shaft 251. More specifically, the outer peripheral portion of the large-diameter washer 231 of the present embodiment projects radially outward from the tooth bottoms of the inner teeth 250t of the ring gear 25 and the inner peripheral surface of the weight body 251. Further, in the present embodiment, the outer diameter of the small diameter washer 232 is smaller than the root circle of the outer tooth 23t of the pinion gear 23, and the outer periphery of the small diameter washer 232 is located radially outside the needle bearing 230.

Next, the operation of the starting device 1 configured as described above will be described.

In the starting device 1, when the lockup by the lockup clutch 8 is released, as can be seen from FIG. 1, the torque (power) transmitted from the engine EG to the front cover 3 is the pump impeller 4, the turbine runner 5, And the damper hub 7 to the input shaft IS of the transmission TM. On the other hand, when lockup is performed by the lockup clutch 8 of the starting device 1, the torque transmitted from the engine EG to the drive member 11 via the front cover 3 and the lockup clutch 8 is the input torque or the like. While the torque is less than T1 and the twist angle of the drive member 11 with respect to the driven member 15 is less than the predetermined angle θref, the first torque transmission path TP1 including the plurality of first springs SP1 and the rotary inertia mass damper 20 are interposed. Are transmitted to the driven member 15 and the damper hub 7.

Further, when the drive member 11 rotates (twists) with respect to the driven member 15, the plurality of first springs SP1 bends, and the ring gear as a mass body according to the relative rotation between the drive member 11 and the driven member 15. 25 rotates (swings) around the axis. In this way, when the drive member 11 rotates (swings) with respect to the driven member 15, the drive member 11 as a carrier that is an input element of the planetary gear mechanism 21, that is, the first and second input plates 12 and 13 is driven. The rotation speed becomes higher than the rotation speed of the driven member 15 as the sun gear. Therefore, at this time, the ring gear 25 is accelerated by the action of the planetary gear mechanism 21, and rotates at a higher rotation speed than the drive member 11. Thereby, the inertia torque is applied from the ring gear 25, which is the mass body of the rotary inertia mass damper 20, to the driven member 15, which is the output element of the damper device 10, via the pinion gear 23, and the vibration of the driven member 15 is damped. Is possible. The rotary inertia mass damper 20 mainly transmits the inertia torque between the drive member 11 and the driven member 15, and does not transmit the average torque.

More specifically, when the plurality of first springs SP1 and the rotary inertia mass damper 20 act in parallel, the torque (average) transmitted to the driven member 15 from the plurality of first springs SP1 (first torque transmission path TP1). The torque is dependent (proportional) to the displacement (deflection amount, that is, twist angle) of the first spring SP1. On the other hand, the torque (inertial torque) transmitted from the rotary inertia mass damper 20 to the driven member 15 is the difference in angular acceleration between the drive member 11 and the driven member 15, that is, between the drive member 11 and the driven member 15. In this case, it depends on (proportional to) the second derivative of the displacement of the first spring SP1.

As a result, assuming that the input torque transmitted to the drive member 11 of the damper device 10 periodically oscillates, the vibration transmitted from the drive member 11 to the driven member 15 via the plurality of first springs SP1. And the phase of the vibration transmitted from the drive member 11 to the driven member 15 via the rotary inertia mass damper 20 shifts by 180°. As a result, in the damper device 10, one of the vibration transmitted from the plurality of first springs SP1 to the driven member 15 and the vibration transmitted from the rotary inertia mass damper 20 to the driven member 15 causes at least a part of the other. The vibration of the driven member 15 can be canceled and the vibration of the driven member 15 can be favorably damped.

Further, when the input torque or the like becomes equal to or more than the torque T1 and the twist angle of the drive member 11 with respect to the driven member 15 becomes equal to or more than the predetermined angle θref, one end portion of each second spring SP2 causes the first and second input plates. The outer spring abutment portions 12co and 13co provided on both sides of the outer spring accommodating windows 12wo and 13wo corresponding to the outer spring contact portions 12co and 12co are in contact with each other. As a result, the torque transmitted to the drive member 11 is the first torque transmission path TP1 until the input torque or the like reaches the torque T2 and the relative rotation between the drive member 11 and the driven member 15 is restricted by the stopper 17. Is transmitted to the driven member 15 and the damper hub 7 via the second torque transmission path TP2 including the plurality of second springs SP2 and the rotary inertia mass damper 20.

That is, in the damper device 10, the plurality of second springs SP2 are composed of the corresponding outer spring contact portions 15co of the driven member 15 and the outer spring contact portions 12co, 13co of the first and second input plates 12, 13. It acts in parallel with the first spring SP1 as the relative torsion angle between the drive member 11 and the driven member 15 increases without transmitting the torque (does not bend) until they come into contact with both. As a result, the torsional rigidity of the damper device 10 is increased in accordance with an increase in the relative twist angle between the drive member 11 and the driven member 15, and a large torque is transmitted by the first and second springs SP1 and SP2 acting in parallel, It becomes possible to receive impact torque and the like.

Further, in the rotary inertia mass damper 20, a plurality of oil grooves 23g are formed on the end surface of each pinion gear 23, and each oil groove 23g is provided with the working oil supplied into the fluid chamber 9 at the inner circumference of the corresponding pinion gear 23. It functions as an oil passage leading between the surface and the pinion shaft 24. Accordingly, even when only the limited outer teeth 23t of each pinion gear 23 mesh with the inner teeth 250t of the ring gear 25 or the outer teeth 15ts of the driven member 15 (sun gear) when the ring gear 25 as the mass body swings. , Guides the oil supplied into the fluid chamber 9 between the pinion gear 23 and the pinion shaft 24, and slides the pinion gear 23 and the needle bearing 230 around the outer teeth 23t meshing with the inner teeth 250t and the outer teeth 15ts. The contact portion and the sliding contact portion between the pinion shaft 24 and the needle bearing 230 can be satisfactorily lubricated and cooled. As a result, it is possible to satisfactorily suppress oil film breakage due to heat generation and wear of the pinion gear 23, the pinion shaft 24, and the needle bearing 230, and improve the reliability and durability of the rotary inertia mass damper 20 including the planetary gear mechanism 21. Becomes

Further, in the rotary inertia mass damper 20, each oil groove 23g of each pinion gear 23 is open on the side of the central hole 23o and the side of the external teeth 23t and extends in the radial direction. As a result, the hydraulic oil supplied into the fluid chamber 9 is guided between the pinion gear 23 and the pinion shaft 24 (in the center hole 23o), and the hydraulic oil whose temperature has risen between the pinion gear 23 and the pinion shaft 24 is discharged. It becomes possible to favorably suppress the retention.

Further, in addition to the plurality of oil grooves 23g or in place of the plurality of oil grooves 23g, each pinion gear 23 of the rotary inertia mass damper 20 has, as shown in FIG. 6, a tooth of a center hole 23o and an outer tooth 23t, respectively. A plurality of oil holes 23h that open at the bottom 23b and extend in the radial direction may be formed. By forming at least one such oil hole 23h in the pinion gear 23, the hydraulic oil supplied into the fluid chamber 9 is introduced between each pinion gear 23 and the pinion shaft 24, and the pinion gear 23 and the pinion shaft 24 are also introduced. It is possible to satisfactorily suppress the stay of the hydraulic oil whose temperature has risen between and.

Further, the oil groove 23g may be omitted from each pinion gear 23 of the rotary inertia mass damper 20, and in this case, even if the large diameter washer 231X and the small diameter washer 232X shown in FIG. 7 are applied to the rotary inertia mass damper 20. Good. As shown in the figure, the large-diameter washer 231X is formed with a plurality of oil passage holes (through holes) 231o so as to at least partially overlap with the central hole 23o (outer periphery thereof) of the corresponding pinion gear 23 when viewed from the axial direction. ing. The plurality of oil passage holes 231o are arranged at equal intervals around the center hole through which the pinion shaft 24 is inserted, and a substantially half region on the center hole side of each oil passage hole 231o is in the axial direction. Seen from the center, it overlaps with the center hole 23o of the pinion gear 23. Further, on the surface of the small diameter washer 232X on the large diameter washer 231X side, an annular groove 232a overlapping the plurality of oil passage holes 231o of the large diameter washer 231X when viewed in the axial direction, an outer periphery of the annular groove 232a and an outer periphery of the small diameter washer 232X, respectively. A plurality of oil grooves 232b that are open at the same time and that extend in the radial direction are formed.

In the rotary inertia mass damper 20 including the large diameter washer 231X and the small diameter washer 232X shown in FIG. 7, through the plurality of oil grooves 232b of the small diameter washer 232X, the annular groove 232a, and the plurality of oil passage holes 231o of the large diameter washer 231X, The inside of the center hole 23o of each pinion gear 23 and the inside of the fluid chamber 9 can be communicated with each other. As a result, the working oil supplied into the fluid chamber 9 is guided between the pinion gears 23 and the pinion shafts 24, and the heated working oil is preferably retained between the pinion gears 23 and the pinion shafts 24. Can be suppressed. Note that, instead of the small-diameter washer 232X shown in FIG. 7, a small-diameter washer formed so that the outer periphery thereof is located inside the plurality of oil passage holes 231o of the large-diameter washer 231 in the radial direction as viewed in the axial direction may be adopted. .. Further, in the rotary inertia mass damper 20 including the large diameter washer 231X and the small diameter washer 232X, each pinion gear 23 may have an oil hole 23h as shown in FIG.

Further, when the oil groove 23g is omitted from each pinion gear 23 of the rotary inertia mass damper 20, the large diameter washer 231Y shown in FIG. 8 may be applied to the rotary inertia mass damper 20. As shown in the drawing, on the surface of the large diameter washer 231Y on the pinion gear 23 side (end face side), an annular groove 231a overlapping the center hole 23o of the pinion gear 23 when viewed in the axial direction, an outer periphery of the annular groove 231a and a large diameter washer 231Y, respectively. And a plurality of oil grooves 231b that are open on the outer periphery of the oil groove and extend in the radial direction. In the rotary inertia mass damper 20 including the large diameter washer 231Y, the inside of the center hole 23o of each pinion gear 23 and the inside of the fluid chamber 9 are communicated with each other through the plurality of oil grooves 231b and the annular groove 231a of the large diameter washer 231Y. You can As a result, the working oil supplied into the fluid chamber 9 is guided between the pinion gears 23 and the pinion shafts 24, and the heated working oil is preferably retained between the pinion gears 23 and the pinion shafts 24. Can be suppressed.

Further, as shown in FIG. 8, an annular groove 231c that overlaps the annular groove 231a when viewed in the axial direction is formed on the surface of the large-sized washer 231Y opposite to the surface including the annular groove 231a and the plurality of oil grooves 231b, respectively. A plurality of oil grooves 231d that open in the outer circumference of the groove 231c and the outer circumference of the large-sized washer 231Y and that extend in the radial direction may be formed. This makes it possible to prevent the large diameter washer 231Y from being erroneously assembled. Further, in the rotary inertia mass damper 20 including the large diameter washer 231Y, each pinion gear 23 may have an oil hole 23h as shown in FIG.

FIG. 9 is a schematic configuration diagram showing another damper device 10B of the present disclosure. It should be noted that, of the constituent elements of the damper device 10B, the same elements as those of the damper device 10 described above are designated by the same reference numerals, and a duplicate description will be omitted.

In the damper device 10B shown in FIG. 9, the driven member 15B is formed with internal teeth 15tr that mesh with the external teeth 23t of the plurality of pinion gears 23, and the driven member 15B functions as a ring gear of the planetary gear mechanism 21B. Further, in the damper device 10B, the sun gear 22 of the planetary gear mechanism 21B including the external teeth 22t meshing with the external teeth 23t of the plurality of pinion gears 23 functions as a mass body of the rotary inertia mass damper 20B. In the damper device 10B, when the drive member 11 rotates (twists) with respect to the driven member 15B, the plurality of first springs SP1 bends and the mass of the first spring SP1 changes in accordance with the relative rotation between the drive member 11 and the driven member 15B. The sun gear 22 as a body rotates (swings) around the axis. In this way, when the drive member 11 rotates (swings) with respect to the driven member 15B, the rotation speed of the drive member 11 as a carrier, which is an input element of the planetary gear mechanism 21, rotates the driven member 15B as a ring gear. Higher than speed. Therefore, at this time, the sun gear 22 is accelerated by the action of the planetary gear mechanism 21B and rotates at a higher rotation speed than the drive member 11.

This makes it possible to apply an inertia torque to the driven member 15B from the sun gear 22, which is a mass body of the rotary inertia mass damper 20B, via the pinion gear 23 and damp the vibration of the driven member 15B. Further, also in the rotary inertia mass damper 20B, the oil supplied into the fluid chamber 9 is guided between the pinion gear 23 and the pinion shaft 24, and the pinion gear 23 around the outer teeth 23t meshing with the outer teeth 22t and the inner teeth 15tr. It is possible to satisfactorily lubricate and cool the sliding contact portion between the needle bearing 230 and the needle bearing 230 and the sliding contact portion between the pinion shaft 24 and the needle bearing 230. Further, the configuration shown in FIGS. 6 to 8 may be applied to the rotary inertia mass damper 20B.

In the damper devices 10 and 10B, the first torque transmission path TP1 is composed of a plurality of first springs SP1 that can act in parallel between the drive member 11 and the driven member 15 to transmit torque. However, it is not limited to this. That is, the first torque transmission path TP1 is provided between the intermediate member (intermediate element) 14, the drive member 11 and the intermediate member 14 as in the damper device 10' shown in FIG. 10 and the damper device 10B' shown in FIG. Between the plurality of (for example, three) input side springs (input side elastic bodies) SPi that transmit torque by means of the input side springs SPi and the intermediate member 14 and the driven members 15 and 15B. It may include a plurality of (for example, three) output side springs (output side elastic bodies) SPo that transmit torque.

In the damper device 10', 10B' including the intermediate member 14, the input side spring SPi, and the output side spring SPo, the bending of the input side and output side springs SPi, SPo is allowed and the second spring SP2 is not bent. On the other hand, two natural frequencies (resonance frequencies) can be set. In the damper devices 10' and 10B', since the torque transmitted via the first torque transmission path TP1 has two peaks, that is, resonance, due to the presence of the intermediate member 14, the vibration amplitudes of the driven members 15 and 15B. It is possible to set a total of two anti-resonance points at which is theoretically zero. Therefore, in the damper devices 10' and 10B', at two points corresponding to the two resonances generated in the first torque transmission path TP1, the amplitude of the vibration in the first torque transmission path TP1 and the rotational inertia having the opposite phase to that of the vibration. By making the vibration amplitudes of the mass dampers 20 and 20B as close as possible, the vibrations of the driven members 15 and 15B can be damped very well.

Further, in the damper devices 10, 10B, 10', 10B', the second spring SP2 may be arranged outside or inside the plurality of pinion gears 23 in the radial direction. Further, the large-diameter washer 231 and the small-diameter washer 232 may be omitted from the damper device 10, 10B, 10', 10B'. In this case, the first and second inputs for supporting the pinion shaft 24 of each pinion gear 23. An oil groove may be formed in a support portion such as the pinion gear support portions 12p and 13p of the plates 12 and 13.

As described above, the damper device of the present disclosure includes a plurality of rotating elements including the input element (11) and the output element (15, 15B) to which the torque from the engine (EG) is transmitted, and the input element (11). ) And the output element (15, 15B) to transmit torque between the elastic bodies (SP1, SP2, SPi, SPo), and any one of the plurality of rotating elements (11, 15, 15B). A rotary inertia mass damper (20, 20B) having a mass body (25, 22) swinging about an axis in accordance with relative rotation between a rotary element and a second rotary element different from the first rotary element. In the damper device (10, 10B, 10', 10B') arranged in the oil chamber (9), the rotary inertia mass damper (20, 20B) includes a sun gear (15, 15ts, 22) and a ring gear (15). 25, 15B, 15tr), a plurality of pinion gears (23), and a carrier (11) that supports a plurality of pinion shafts (24) inserted through the center holes (23o) of the corresponding pinion gears (23). The planetary gear mechanism (21, 21B) having, the carrier (11) rotates integrally with the first rotating element, and the sun gear (15, 15ts, 22) and the ring gear (25, 15B, 15tr). One rotates integrally with the second rotating element, and the other of the sun gear (15, 15ts, 22) and the ring gear (25, 15B, 15tr) functions as the mass body, and the pinion gear (23). , The oil supplied into the oil chamber (9) is supplied to the pinion gear (23) and/or the member (231, 231X, 231Y) arranged close to the end face of the pinion gear (23). Oil passages (23g, 23h, 231o, 231a, 231b) to be guided to the pinion shaft (24) are formed.

The damper device of the present disclosure includes a rotary inertia mass damper having a mass body that swings around an axis according to relative rotation between the first rotating element and the second rotating element, and is arranged in the oil chamber. The rotary inertia mass damper has a sun gear, a ring gear, a plurality of pinion gears, and a carrier that supports a plurality of pinion shafts that are inserted through the center holes of the corresponding pinion gears. An oil passage that guides the oil supplied into the oil chamber between the pinion gear and the pinion shaft is formed in at least one of the pinion gear and a member arranged near the end surface of the pinion gear. As a result, when the ring gear as the mass body oscillates, even if only the limited gear teeth of each pinion gear mesh with the corresponding gear teeth of the ring gear or the sun gear, the oil supplied to the oil chamber can be supplied to the pinion gear and the pinion gear. It can be guided between the shaft and the both, and both can be satisfactorily lubricated and cooled. As a result, it is possible to satisfactorily suppress oil film breakage due to heat generation and wear of the pinion gear and pinion shaft, and to improve the reliability and durability of the rotary inertia mass damper including the planetary gear mechanism.

The pinion gear (23) has a plurality of oil grooves (opened at the center hole (23o) side and the gear tooth (23t) side and formed in at least one of the end faces so as to extend in the radial direction). 23g) may be included. This makes it possible to guide the oil supplied into the oil chamber between the pinion gear and the pinion shaft, and to satisfactorily prevent the heated oil from staying between the pinion gear and the pinion shaft.

Further, the pinion gear (23) includes at least one oil hole (23h) which is open at the center hole (23o) and the bottom (23b) of the gear tooth (23t) and extends in the radial direction. May be. With such a configuration as well, it is possible to guide the oil supplied into the oil chamber between the pinion gear and the pinion shaft, and it is possible to favorably prevent the heated oil from staying between the pinion gear and the pinion shaft. ..

In addition, a pair of washers (231) may be disposed on both sides of each of the pinion gears (23) in the axial direction, and at least one of the pair of washers (231) may be arranged in the axial direction as viewed from the axial direction. It may include a plurality of oil passage holes (231o) formed so as to at least partially overlap with the central hole (23o) of the pinion gear (23). With such a configuration as well, it is possible to guide the oil supplied into the oil chamber between the pinion gear and the pinion shaft, and it is possible to favorably prevent the heated oil from staying between the pinion gear and the pinion shaft. ..

Furthermore, at least a pair of washers (231) may be arranged on both sides of each of the pinion gears (23) in the axial direction, and at least one of the pair of washers (231) may have a pinion gear (23). An annular groove (231a) that overlaps with the central hole (23o) when viewed from the axial direction, and an outer circumference of the annular groove (231a) and an outer circumference of the washer (231), respectively, are formed on a surface facing the end surface and have a diameter. A plurality of oil grooves (231b) extending in the direction may be formed. With such a configuration as well, it is possible to guide the oil supplied into the oil chamber between the pinion gear and the pinion shaft, and it is possible to favorably prevent the heated oil from staying between the pinion gear and the pinion shaft. ..

Further, a plurality of needle bearings (230) may be arranged between the inner peripheral surface of the pinion gear (23) and the outer peripheral surface of the pinion shaft (24). That is, according to the above configuration, it is possible to satisfactorily lubricate and cool the sliding contact portion between the pinion gear and the needle bearing and the sliding contact portion between the pinion shaft and the needle bearing.

Further, the first rotating element may be the input element (11) and the second rotating element may be the output element (15, 15B).

Further, the rotating element may include an intermediate element (14), and the elastic body is an input side elastic body (SPi) that transmits torque between the input element (11) and the intermediate element (14). And an output side elastic body (SPo) that transmits torque between the intermediate element (14) and the output element (15, 15B). This makes it possible to set two anti-resonance points at which the vibration transmitted from the output side elastic body to the output element and the vibration transmitted from the rotary inertia mass damper to the output element theoretically cancel each other. Therefore, the vibration damping performance of the damper device can be further improved.

Further, the output element (15, 15B) may be operatively (directly or indirectly) connected to the input shaft (IS) of the transmission (TM).

Further, it goes without saying that the invention of the present disclosure is not limited to the above-described embodiment, and various modifications can be made within the scope of the extension of the present disclosure. Furthermore, the embodiment for carrying out the invention is merely one specific form of the invention described in the summary of the invention, and does not limit the elements of the invention described in the summary of the invention. Absent.

INDUSTRIAL APPLICABILITY The invention of the present disclosure can be used in the field of manufacturing damper devices and the like.

1 starter device, 3 front cover, 4 pump impeller, 5 turbine runner, 6 stator, 7 damper hub, 8 lockup clutch, 9 fluid chamber, 10, 10B, 10', 10B' damper device, 11 drive member, 12 1st Input plate, 12a, 12b, 12d spring support portion, 12ci inner spring contact portion, 12co outer spring contact portion, 12i inner peripheral portion, 12o outer peripheral portion, 12p pinion gear support portion, 12r connecting portion, 12wi inner spring accommodating window, 12wo outer spring accommodating window, 13 second input plate, 13a, 13b, 13d spring support portion, 13ci inner spring contact portion, 13co outer spring contact portion, 13i inner peripheral portion, 13o outer peripheral portion, 13p pinion gear support portion, 13r Connecting part, 13wi inner spring accommodating window, 13wo outer spring accommodating window, 14 intermediate member, 15,15B driven member, 15B driven member, 15ci inner spring abutting part, 15co outer spring abutting part, 15e protruding part, 15ts external tooth , 15tr inner teeth, 15wi inner spring holding window, 15wo outer spring holding window, 17 stopper, 20,20B rotary inertia mass damper, 21,21B planetary gear mechanism, 22 sun gear, 22t outer tooth, 23 pinion gear, 23b tooth bottom, 23g Oil groove, 23h Oil hole, 23o Central hole, 23t External tooth, 230 Needle bearing, 231, 231X, 231Y Large diameter washer, 231a, 231c, 232a Annular groove, 231b, 231d, 232b Oil groove, 231o Oil passage hole, 232 , 232X small diameter washer, 24 pinion shaft, 25 ring gear, 250 internal gear, 250t internal tooth, 251 weight body, 252 rivet, 40 pump shell, 41 pump blade, 50 turbine shell, 51 turbine blade, 60 stator blade, 61 one way Clutch, 80 lockup piston, 81 friction material, 90 rivet, EG engine, IS input shaft, SP1 first spring, SP2 second spring, TM transmission, TP1 first torque transmission path, TP2 second torque transmission path.

Claims (9)

Any one of a plurality of rotating elements including an input element and an output element to which torque from the engine is transmitted, an elastic body that transmits torque between the input element and the output element, and the plurality of rotating elements. A damper including a rotary inertia mass damper having a mass body that oscillates around an axis in accordance with relative rotation between a first rotating element and a second rotating element different from the first rotating element, the damper being arranged in an oil chamber. In the device,
The rotary inertia mass damper includes a planetary gear mechanism having a sun gear, a ring gear, a plurality of pinion gears, and a carrier that supports a plurality of pinion shafts that are respectively inserted through the center holes of the corresponding pinion gears,
The carrier rotates integrally with the first rotating element, one of the sun gear and the ring gear rotates integrally with the second rotating element, and the other of the sun gear and the ring gear functions as the mass body. ,
An oil passage for guiding the oil supplied into the oil chamber between the pinion gear and the pinion shaft is formed in at least one of the pinion gear and a member arranged in proximity to the end face of the pinion gear. Damper device. The damper device according to claim 1,
The said pinion gear is a damper apparatus containing the some oil groove formed in at least one said end surface so that it may each open at the said center hole side and a gear tooth side, and may extend in a radial direction. The damper device according to claim 1 or 2,
The said pinion gear is a damper apparatus containing the said center hole and the at least 1 oil hole which extends in the radial direction while opening in the root of the gear tooth. The damper device according to claim 1,
A pair of washers is arranged on both sides of each of the pinion gears in the axial direction,
At least one of the pair of washers includes a plurality of oil passage holes formed so as to at least partially overlap the central hole of the pinion gear when viewed in the axial direction. The damper device according to claim 1,
At least a pair of washers are arranged on both sides of each of the pinion gears in the axial direction,
At least one of the pair of washers has a surface facing the end surface of the pinion gear, and an annular groove that overlaps with the central hole when viewed in the axial direction, and an opening at the outer circumference of the annular groove and the outer circumference of the washer, respectively. A damper device in which a plurality of oil grooves extending in the radial direction are formed. The damper device according to any one of claims 1 to 5,
A damper device in which a plurality of needle bearings are arranged between an inner peripheral surface of the pinion gear and an outer peripheral surface of the pinion shaft. The damper device according to any one of claims 1 to 6,
The damper device in which the first rotating element is the input element and the second rotating element is the output element. The damper device according to any one of claims 1 to 7,
The rotating element includes an intermediate element,
The elastic body includes a damper including an input side elastic body that transmits torque between the input element and the intermediate element, and an output side elastic body that transmits torque between the intermediate element and the output element. .. 9. The damper device according to claim 1, wherein the output element is operatively connected to an input shaft of a transmission.

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