WO2016167025A1

WO2016167025A1 - Dynamic vibration absorber

Info

Publication number: WO2016167025A1
Application number: PCT/JP2016/055301
Authority: WO
Inventors: 富山　直樹
Original assignee: 株式会社エクセディ
Priority date: 2015-04-13
Filing date: 2016-02-23
Publication date: 2016-10-20
Also published as: JP2016200236A

Abstract

Provide is a torque converter with which it is possible to reliably damp fluctuations in torque and to impart flexibility to the design and placement of a dynamic vibration absorber. A torque converter (1) is provided with: a front cover (2), a lock-up device (7), and a dynamic vibration absorber (8). The lock-up device (7) has a piston (24) and a damper unit (30). The piston (24) allows or releases the transmission of torque from the front cover (2). When the transmission of torque is allowed by the piston (24), the damper unit (30) damps fluctuations in torque from the front cover (2). The dynamic vibration absorber (8) is directly coupled to the lock-up device (7). The dynamic vibration absorber (8) damps fluctuations in torque from the lock-up device (7) and outputs the torque from the lock-up device (7) to the transmission.

Description

Dynamic vibration absorber

The present invention relates to a dynamic vibration absorber, and more particularly to a dynamic vibration absorber for attenuating fluctuations in torque transmitted from an engine to a transmission.

A conventional torque converter having a lockup clutch (28) and a damper device (11) is disclosed (see Patent Document 1). The lockup clutch transmits torque from the front cover (21) to the damper device. The damper device is connected to the lockup clutch. The damper device has a first spring (31), an inertia member (32), and a differential mechanism (30). The differential mechanism is connected to the lockup clutch via the first spring and the inertia member. The differential mechanism is connected to the crankshaft (14) of the engine. Thus, the differential mechanism operates between the lock-up clutch and the engine crankshaft (14). Further, when the differential mechanism is operated, the inertia member rotates relative to the crankshaft while the first spring expands and contracts. Thereby, torque fluctuation is attenuated. The differential mechanism includes a sun gear mounted on the crankshaft, a ring gear arranged outside the sun gear, and a planetary gear arranged between the sun gear and the ring gear.

Japanese Patent Application Laid-Open No. 2014-177956

In the conventional torque converter, the differential mechanism operates between the lockup clutch and the engine crankshaft. That is, the differential mechanism is always connected to the engine. For this reason, in the conventional configuration, even when the lockup clutch is on or when the lockup clutch is off, torque fluctuations from the engine may be input to the differential mechanism via the crankshaft. .

For example, when the lockup clutch is on, the torque fluctuation from the engine is directly input from the crankshaft to the differential mechanism. On the other hand, when the lock-up clutch is off, the sun gear mounted on the crankshaft is operated due to the difference in rotational speed between the turbine and the engine (crankshaft) (for example, FIG. 4B). reference). Thus, even when the lockup clutch is off, the differential mechanism operates. For this reason, when a differential mechanism operates, there exists a possibility that an operation vibration and an operation noise may occur.

In the conventional configuration, the dynamic vibration absorber is configured by the differential mechanism, the first spring, and the inertia member.

The present invention has been made in view of the above problems, and an object of the present invention is to provide a torque converter capable of reliably attenuating torque fluctuations. Another object of the present invention is to provide a torque converter that can reduce operating vibration and operating noise of a dynamic vibration absorber.

(1) A torque converter according to one aspect of the present invention is a torque converter for transmitting torque from an engine to a transmission. The torque converter includes a front cover, a lockup device, and a dynamic vibration absorber.

∙ Torque from the engine is input to the front cover. The lock-up device has a clutch part and a damper part. The clutch portion permits or cancels transmission of torque from the front cover. The damper portion attenuates torque fluctuation from the front cover when torque transmission is permitted in the clutch portion. The dynamic vibration absorber is directly connected to the lockup device. The dynamic vibration damping device attenuates torque fluctuations from the lockup device and outputs torque from the lockup device to the transmission.

In this torque converter, when the clutch portion permits transmission of torque in the lockup device, torque from the engine is transmitted to the damper portion via the clutch portion. Next, the torque fluctuation from the engine is attenuated in the damper portion. Subsequently, in the dynamic vibration absorber, the torque fluctuation output from the lockup device is attenuated. Finally, torque is output from the dynamic vibration absorber to the transmission. On the other hand, when the clutch part cancels the transmission of torque in the lockup device, the torque from the engine is transmitted to the transmission without going through the dynamic vibration absorber.

As described above, in this torque converter, when the clutch portion permits transmission of torque in the lockup device, the fluctuation of the engine torque is attenuated in the lockup device, and then the operation directly connected to the lockup device is performed. In the vibration absorber, the torque fluctuation of the lockup device is further attenuated. As a result, the torque converter can reliably attenuate the torque fluctuation.

Further, in this torque converter, when the clutch portion releases torque transmission in the lock-up device, the dynamic vibration absorber is arranged independently of the engine, so that the dynamic vibration due to the difference in the rotational speed between the turbine and the engine The operation vibration and operation sound of the device are not substantially generated. Thereby, in this torque converter, the operation vibration and operation sound of a dynamic vibration damper can be reduced compared with a prior art.

(2) The torque converter according to another aspect of the present invention is preferably configured as follows. The dynamic vibration absorber includes an input unit, an output unit, an inertial mass unit, a connecting unit, and an elastic unit. The input unit is connected to the lockup device. The output unit is connected to the transmission. The inertial mass unit is movable relative to the input unit between the input unit and the output unit. The connecting portion is connected to the output portion, and is connected to the input portion and the inertial mass portion. The connecting part operates so that the input part and the inertial mass part are relatively movable. The elastic part elastically connects the input part and the inertial mass part.

In this torque converter, first, torque from the lockup device is input to the input unit. Next, when the elastic portion is actuated by this torque, the connecting portion operates between the input portion and the inertia mass portion, and the inertia mass portion moves relative to the input portion. Thereby, the fluctuation | variation of the torque from a lockup apparatus is attenuated.

This configuration makes it possible to reliably and effectively attenuate the torque fluctuation transmitted from the lockup device.

(3) The torque converter according to another aspect of the present invention is preferably configured as follows. A first torque transmitted directly from the input part to the connecting part, and a second torque transmitted from the input part to the inertial mass part via the elastic part and further transmitted from the inertial mass body to the connecting part Is transmitted from the connecting portion to the output portion.

In this case, when the torque from the lockup device is input to the input unit, the first torque is directly transmitted from the input unit to the connection unit, and the second torque is indirectly transmitted from the input unit to the connection unit. Is transmitted to. Specifically, the second torque is transmitted from the input unit to the inertial mass unit via the elastic unit, and further transmitted from the inertial mass body to the coupling unit.

With this configuration, the torque from the lockup device can be output to the transmission only by the configuration of the dynamic vibration absorber. For example, the torque from the lock-up device can be output to the transmission only by the configuration of the dynamic vibration absorber without using an engine-side member (for example, a crankshaft or the like). As a result, torque fluctuations from the lockup device can be reliably damped in the dynamic vibration absorber.

(4) The torque converter according to another aspect of the present invention is preferably configured as follows. When the second torque is less than the operating torque of the elastic portion, the torque from the lockup device is transmitted to the output portion by moving the connecting portion together with the input portion and the inertial mass portion in a state where the connecting portion does not substantially operate. Is done.

With this configuration, the torque input to the input unit can be efficiently output from the output unit. In particular, the torque input to the input unit can be efficiently output from the output unit by operating the dynamic vibration absorber with the above-described configuration at a rotational speed at which attenuation of torque fluctuation is not required.

(5) The torque converter according to another aspect of the present invention is preferably configured as follows. When the second torque is equal to or greater than the operating torque of the elastic portion, the fluctuation of the torque from the lockup device is attenuated by operating the connecting portion in a state where the operating center of the connecting portion does not substantially move.

With this configuration, the inertial mass portion can be stably moved relative to the input portion, and torque fluctuation can be more reliably attenuated in the rotation speed range to be attenuated.

In the torque converter of the present invention, torque fluctuation can be reliably attenuated, and the operating vibration and operating noise of the dynamic vibration absorber can be reduced.

The cross-sectional block diagram of the torque converter provided with the lockup apparatus by 1st Embodiment of this invention. The expanded sectional view of the dynamic vibration damping device of FIG. The side view of the dynamic vibration damping device of FIG. The schematic diagram for demonstrating a torque flow. The schematic diagram for demonstrating operation | movement of a dynamic vibration damper. The schematic diagram for demonstrating operation | movement of a dynamic vibration damper. The schematic diagram for demonstrating operation | movement of a dynamic vibration damper. The schematic diagram for demonstrating operation | movement of a dynamic vibration damper. FIG. 3 is a characteristic diagram of engine speed and rotational speed fluctuation. The cross-sectional block diagram of the torque converter provided with the lockup apparatus by 2nd Embodiment of this invention. The expanded sectional view of the dynamic vibration damper of FIG. The side view of the dynamic vibration damper of FIG. The schematic diagram for demonstrating operation | movement of a dynamic vibration damper. The schematic diagram for demonstrating operation | movement of a dynamic vibration damper. The schematic diagram for demonstrating operation | movement of a dynamic vibration damper. The schematic diagram for demonstrating operation | movement of a dynamic vibration damper.

<First Embodiment>
FIG. 1 is a partial sectional view of a torque converter 1 according to an embodiment of the present invention. An engine (not shown) is arranged on the left side of FIG. 1, and a transmission (not shown) is arranged on the right side of the figure.

In addition, the rotating shaft of the torque converter 1 is indicated by a symbol O. The axial direction is a direction in which the rotation axis O of the torque converter 1 extends or a direction along the rotation axis O of the torque converter 1. The circumferential direction is a direction around the rotation axis O of the torque converter 1. The radial direction is a direction away from the rotation axis O of the torque converter 1.

[Overall configuration of torque converter]
The torque converter 1 is a device for transmitting torque from an engine-side crankshaft (not shown) to a transmission input shaft, and includes a front cover 2 fixed to an engine-side member and three types of impellers ( A torque converter main body 6 including an impeller 3, a turbine 4, and a stator 5), a lockup device 7, and a dynamic vibration absorber 8 are configured.

The front cover 2 is a disk-shaped member, and an outer peripheral cylindrical portion 10 that protrudes toward the transmission side is formed on the outer peripheral portion thereof. The impeller 3 includes an impeller shell 12 fixed to the outer peripheral cylindrical portion 10 of the front cover 2 by welding, a plurality of impeller blades 13 fixed to the inside thereof, and a cylindrical shape provided on the inner peripheral side of the impeller shell 12. The impeller hub 14.

Here, the impeller shell 12 has a shell body 12a and an outer shell 12b fixed to the outer periphery of the shell body 12a. The outer shell 12b is fixed to the outer cylindrical portion 10 of the front cover 2 by welding. The inner peripheral portion of the shell body 12a is fixed to the impeller hub 14 by welding.

The turbine 4 is disposed to face the impeller 3 in the fluid chamber. The turbine 4 includes a turbine shell 15, a plurality of turbine blades 16 fixed to the turbine shell 15, and a turbine hub 17 fixed to the inner peripheral side of the turbine shell 15. The turbine hub 17 has a flange 17a extending to the outer peripheral side. The inner peripheral portion of the turbine shell 15 is fixed to the flange 17 a by a plurality of rivets 18. An input shaft of a transmission (not shown) is splined to the inner peripheral portion of the turbine hub 17.

The stator 5 is disposed between the inner periphery of the impeller 3 and the inner periphery of the turbine 4. The stator 5 is a mechanism for rectifying hydraulic fluid that returns from the turbine 4 to the impeller 3. The stator 5 is mainly composed of a stator carrier 5a and a plurality of stator blades 21 provided on the outer peripheral surface thereof. The stator carrier 5a is supported on the fixed shaft via a one-way clutch.

[Configuration of lock-up device]
As shown in FIG. 1, the lockup device 7 is disposed in a space between the front cover 2 and the turbine 4. The lockup device 7 includes a piston 24, a first drive plate 25, a first torsion spring 26, and a first driven plate 28.

The piston 24 is a disk-shaped plate and is disposed on the transmission side of the front cover 2. A cylindrical portion 24 a extending to the transmission side is formed at the inner peripheral end of the piston 24. The cylindrical portion 24a is supported on the outer peripheral surface of the turbine hub 17 so as to be axially movable and relatively rotatable. A flat portion 24 b is formed on the outer peripheral portion of the piston 24. An annular friction material 33 is fixed to the surface of the flat portion 24b on the front cover 2 side. When the friction material 33 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the piston 24. That is, the piston 24 and the friction material 33 constitute a clutch portion.

A stepped portion including a small-diameter portion 17b on the engine side and a large-diameter portion 17c on the transmission side is formed on the outer peripheral side of the turbine hub 17. The piston 24 is supported by the small diameter portion 17b. A seal member 35 is attached to the small diameter portion 17b. Thereby, the space between the inner peripheral surface of the piston 24 and the turbine hub 17 is sealed. Further, the axial movement of the piston 24 toward the transmission side is restricted by the tip of the cylindrical portion 24a coming into contact with the side surface of the large diameter portion 17c.

The first drive plate 25 is fixed to the side surface on the transmission side in the outer peripheral portion of the piston 24. Specifically, the first drive plate 25 is formed in a substantially annular shape. An inner peripheral portion 25 a of the first drive plate 25 is fixed to a transmission side surface of the piston 24 by a rivet 37. A plurality of first engaging portions 25 b are formed on the outer peripheral portion of the first drive plate 25. The first engaging portion 25b is formed by bending the outer peripheral portion of the first drive plate 25 toward the transmission side and the rotating shaft O side. The first engaging portion 25 b is engaged with both ends of the first torsion spring 26 in the circumferential direction.

Further, a plurality of first spring holding portions 25c protruding toward the transmission side are formed in the radial direction intermediate portion of the first drive plate 25. The plurality of first spring holding portions 25c are formed at predetermined intervals in the circumferential direction. Each first spring holding portion 25 c supports the inner peripheral side of the first torsion spring 26.

As described above, the first engagement portion 25b of the first drive plate 25 is engaged with both ends of the first torsion spring 26. In addition, second engagement portions 28 b (described later) of the first driven plate 28 are engaged with both end portions of the first torsion spring 26.

The first driven plate 28 outputs the torque transmitted from the first torsion spring 26 to the first drive plate 25.

The first driven plate 28 has a driven main body portion 28a, a second engagement portion 28b, and a second spring holding portion 28b.

The driven main body 28a is connected to a dynamic vibration absorber 8 to be described later. By this connection, torque is transmitted from the lockup device 7 to the dynamic vibration absorber 8. The driven main body portion 28a is formed in an annular shape.

The second engaging portion 28b is a portion extending from the driven main body portion 28a to the engine side. The second engagement portion 28b is formed integrally with the driven main body portion 28a. The second engaging portions 28b are provided at a predetermined interval in the circumferential direction. A first torsion spring 26 is disposed between the second engaging portions 28b adjacent to each other in the circumferential direction. The second engaging portion 28 a is engaged with both ends of the first torsion spring 26 in the circumferential direction.

The second spring holding portion 28b is a recess provided between the second engaging portions 28a adjacent to each other in the circumferential direction. The second spring holding portion 28b restricts the movement of the first torsion spring 26 toward the transmission side.

[Configuration of dynamic vibration absorber]
The dynamic vibration absorber 8 is for attenuating fluctuations in torque transmitted from the engine to the transmission. Specifically, the dynamic vibration damping device 8 is for attenuating fluctuations in torque output from the lockup device 7.

Hereinafter, the rotation center of the second drive plate 51 (described later) is used in the same meaning as the rotation axis of the second drive plate 51. The rotation axis of the second drive plate 51 is coaxial with the rotation axis O of the torque converter 1.

The axial direction is a direction in which the rotation axis O of the second drive plate 51 extends or a direction along the rotation axis O of the second drive plate 51. The circumferential direction is a direction around the rotation axis O of the second drive plate 51. The radial direction is a direction away from the rotation axis O of the second drive plate 51.

As shown in FIG. 2, the dynamic vibration damping device 8 includes a second drive plate 51 (an example of an input unit; 61, 63, 65), an inertia ring 53 (an example of an inertial mass unit), and a connection gear unit 55 (connection). Part), a second torsion spring 57 (an example of an elastic part), and a second driven plate 59 (an example of an output part).

The second drive plate 51 is configured to be rotatable by inputting torque. The second drive plate 51 is connected to the first driven plate 28. For example, the second drive plate 51 is fixed to the first driven plate 28. Note that the second dry plate may be formed integrally with the first driven plate 28.

The second drive plate 51 includes a main plate 61, a side plate 63, and an inner ring 65.

The main plate 61 is fixed to the first driven plate 28. Specifically, the main plate 61 is fixed to the driven main body portion 28a of the first driven plate 28 by fixing means such as welding.

The main plate 61 has a first spring storage portion 71 and a gear storage portion 72.

The first spring storage portion 71 is formed in a substantially annular shape. The first spring accommodating portion 71 has a plurality of (for example, four) first window portions 71a. A second torsion spring 57 is disposed in the first window portion 71a. A pair of wall portions opposed to each other in the circumferential direction in the first window portion 71 a abuts against both end portions of the second torsion spring 57.

The gear storage portion 72 stores the connecting gear portion 55. Further, the gear storage portion 72 stores the inner ring 65. The gear housing portion 72 is a portion pushed out to the piston 24 side (engine side).

The gear accommodating part 72 has the outer peripheral side cylinder part 72a, the inner peripheral side cylinder part 72b, and the annular part 72c. The outer peripheral side cylinder part 72 a is formed integrally with the first spring storage part 71 so as to protrude from the inner peripheral part of the first spring storage part 71 to the piston 24 side (engine side). The inner peripheral side cylinder part 72b is disposed to face the inner peripheral side of the outer peripheral side cylinder part 72a. The annular portion 72c is formed in an annular shape. The annular portion 72c connects the outer peripheral side cylindrical portion 72a and the inner peripheral side cylindrical portion 72b in the radial direction. The outer peripheral part of the annular part 72c is formed integrally with the outer peripheral side cylindrical part 72a, and the inner peripheral part of the annular part 72c is formed integrally with the inner peripheral side cylindrical part 72b.

A connecting gear portion 55 and an inner ring 65 are disposed between the outer peripheral side cylindrical portion 72a and the inner peripheral side cylindrical portion 72b in the radial direction. Specifically, the inner ring 65 is disposed on the outer periphery of the inner peripheral side cylinder portion 72b. A connecting gear portion 55 is disposed between the outer peripheral side cylinder portion 72 a and the inner ring 65.

The gear storage portion 72 having this configuration is disposed between the piston 24 and the torque converter body 6 (for example, the turbine 4) in the axial direction. The gear storage 72 is disposed on the inner peripheral side of the first torsion spring. Thereby, a torque converter can be reduced in size in an axial direction.

The side plate 63 is provided facing the main plate 61 in the axial direction. For example, the side plate 63 is disposed to face the main plate 61 with a predetermined interval. The side plate 63 is fixed to the main plate 61 by fixing means such as bolts. As a result, the side plate 63 rotates integrally with the main plate 61. A stopper 62 is fixed between the side plate 63 and the main plate 61 by fixing means such as the above-described bolts (see FIG. 3).

The side plate 63 is substantially annular. More specifically, the outer peripheral portion of the side plate 63 is formed in an annular shape, and the inner peripheral portion of the side plate 63 is bent toward the piston 24 (engine side). With this configuration, the side plate 63 can be disposed along the outer peripheral surface of the torque converter body 6 (for example, the turbine 4). That is, the torque converter can be reduced in size in the axial direction.

The side plate 63 has a second spring storage portion 73. The second spring storage portion 73 has a plurality of (for example, four) second window portions 73a. The second window portion 73a is disposed to face the first window portion 71a in the axial direction. A second torsion spring 57 is disposed in the second window portion 73a. A pair of wall portions facing each other in the circumferential direction in the second window portion 73 a abuts against both end portions of the second torsion spring 57. That is, both end portions of the second torsion spring 57 are in contact with the first window portion 71 a of the main plate 61 and the second window portion 73 a of the side plate 63 in the circumferential direction.

2 and 3, the inner ring 65 is attached to the main plate 61. For example, the inner ring 65 is fixed to the inner peripheral portion of the main plate 61 by fixing means such as bolts. More specifically, the inner ring 65 is fixed to the gear storage portion 72 of the main plate 61 by fixing means such as bolts. The connecting gear portion 55 is screwed into the inner ring 65. The inner ring 65 may be formed integrally with the main plate 61.

The inner ring 65 has a first annular portion 65a and an inner gear portion 65b (an example of a first screwing portion). The first annular portion 65a is substantially annular. The first annular portion 65 a is attached to the main plate 61. For example, the first annular portion 65 a is disposed on the outer peripheral portion of the inner peripheral cylinder portion 72 b of the main plate 61. The first annular portion 65a is fixed to the annular portion 72c of the main plate 61 by fixing means such as a bolt.

The inner gear portion 65b is partially provided in the first annular portion 65a in the circumferential direction with the rotation center O of the main plate 61 as a reference. Specifically, the inner gear portion 65b is formed in a predetermined range (first gear formation range G1) on the outer peripheral portion of the first annular portion 65a. Here, a plurality of (for example, five) inner gear portions 65b are integrally formed on the outer peripheral portion of the first annular portion 65a. Each of the plurality of inner gear portions 65b is provided at a predetermined interval in the circumferential direction. The connecting gear portion 55 is screwed into each inner gear portion 65b.

Here, an example in which a plurality of (for example, five) inner gear portions 65b are integrally formed on the outer peripheral portion of the first annular portion 65a has been shown. However, the inner gear portion 65b is replaced with the first annular portion. You may form separately from 65a. In this case, the inner gear portion 65b is attached to the first annular portion 65a by fixing means such as bolts, rivets, and welding.

The inertia ring 53 is configured to be capable of attenuating torque fluctuations input to the second drive plate 51 by moving relative to the second drive plate 51. Specifically, when the inertia ring 53 moves relative to the second drive plate 51, the inertia force of the inertia ring 53 acts in a direction opposite to the direction in which the second drive plate 51 rotates. Thereby, the torque fluctuation | variation input into the 2nd drive plate 51 is attenuated.

2 and 3, the inertia ring 53 is disposed between the main plate 61 and the side plate 63 in the axial direction. The inertia ring 53 is formed in a substantially annular shape. The inertia ring 53 has a ring main body portion 74 and an outer gear portion 75 (an example of a second screwing portion).

The ring main body portion 74 is disposed between the first spring storage portion 71 and the second spring storage portion 73. The ring main body 74 includes a second annular portion 74a, a plurality (for example, four) of concave portions 74b, and a plurality (for example, four) of third window portions 74c.

The second annular portion 74a is substantially formed in an annular shape. Specifically, the outer peripheral portion of the second annular portion 74a is formed in an annular shape, and the inner peripheral portion of the second annular portion 74a is bent toward the piston 24 (engine side).

The plurality of concave portions 74b are provided on the outer peripheral portion of the second annular portion 74a. For example, each of the plurality of concave portions 74b is provided on the outer peripheral portion of the second annular portion 74a with a predetermined interval in the circumferential direction. In each recess 74b, fixing means for connecting the main plate 61 and the side plate 63, for example, a shaft portion of a bolt, is arranged.

The third window portion 74c is provided on the outer peripheral portion of the second annular portion 74a. For example, the third window portion 74c is provided on the outer peripheral portion of the second annular portion 74a between the concave portions 74b adjacent in the circumferential direction. The third window portion 74c is disposed to face the first window portion 71a and the second window portion 73a in the axial direction. A second torsion spring 57 is disposed in the third window portion 74c. A pair of wall portions facing each other in the circumferential direction in the third window portion 74 c abuts against both end portions of the second torsion spring 57. The frame portion of the third window portion 74c can contact the stopper 62 in the circumferential direction.

The outer gear portion 75 is partially provided in the second annular portion 74a in the circumferential direction. The outer gear portion 75 is provided to face the inner gear portion 65b in the radial direction. A connecting gear portion 55 is disposed on the outer gear portion 75 and the inner gear portion 65b.

Specifically, the outer gear portion 75 is formed in a predetermined range (second gear formation range G2) in the inner peripheral portion of the second annular portion 74a. Here, a plurality of (for example, five) outer gear portions 75 are integrally formed on the inner peripheral portion of the second annular portion 74a. Each of the plurality of outer gear portions 75 is provided at a predetermined interval in the circumferential direction. The connecting gear portion 55 is screwed into each outer gear portion 75.

The connecting gear portion 55 connects the second drive plate 51 and the inertia ring 53. Specifically, the connection gear portion 55 connects the second drive plate 51 and the inertia ring 53 so that the inertia ring 53 can move relative to the second drive plate 51. More specifically, the connection gear portion 55 connects the second drive plate 51 and the inertia ring 53 so that the inertia ring 53 can rotate relative to the second drive plate 51.

The connecting gear portion 55 is configured to be rotatable between the second drive plate 51 and the inertia ring 53. For example, when the inertia ring 53 rotates relative to the second drive plate 51, the connecting gear portion 55 rotates between the inner gear portion 65 b and the outer gear portion 75.

Here, a plurality of (for example, five) connecting gear portions 55 are arranged between the second drive plate 51 and the inertia ring 53.

Each connecting gear portion 55 is screwed into the second drive plate 51 and the inertia ring 53 so as to be rotatable between the second drive plate 51 and the inertia ring 53. Specifically, each connecting gear portion 55 is disposed between the outer gear portion 75 and the inner gear portion 65b in the radial direction. In this state, each connecting gear portion 55 is screwed into the outer gear portion 75 and the inner gear portion 65b.

Each connecting gear portion 55 is rotatably supported by the second driven plate 59. As shown in FIG. 3, each connection gear part 55 has the gear main-body part 55a, the tooth | gear part 55b, and the hole 55c. The gear body 55a is formed in an annular shape. The tooth portion 55b is formed integrally with the outer peripheral portion of the gear main body portion 55a. The tooth part 55b is screwed into the tooth part 55b of the outer gear part 75 and the tooth part 55b of the inner gear part 65b. The hole part 55c is formed in the inner peripheral part of the gear main-body part 55a. A support portion 77 (described later) of the second driven plate 59 is disposed in the hole portion 55c. As a result, the gear body 55a can rotate around the support part 77 of the second driven plate 59 in a state where the tooth part 55b is screwed into the tooth part 55b of the outer gear part 75 and the tooth part 55b of the inner gear part 65b. become.

The second torsion spring 57 elastically connects the second drive plate 51 and the inertia ring 53. For example, the second torsion spring 57 is disposed in the first window 71 a and the second window 73 a of the second drive plate 51 and the third window 74 c of the inertia ring 53.

As described above, both end portions of the second torsion spring 57 are connected to the wall portion of the first window portion 71a and the wall portion of the second window portion 73a of the second drive plate 51 (the main plate 61 and the side plate 63), and the inertia. It abuts against the wall of the third window 74c of the ring 53 (ring body 74) in the circumferential direction.

In this state, when one end of the second torsion spring 57 is pressed in the circumferential direction by the second drive plate 51 (the wall of the first window 71a and the wall of the second window 73a), The second torsion spring 57 is compressed while the other end of the torsion spring 57 is supported by the inertia ring 53 (wall portion of the third window portion 74c).

When it is considered that the second torsion spring 57 is pressed in the circumferential direction by the inertia ring 53, one end portion of the second torsion spring 57 is circled by the inertia ring 53 (wall portion of the third window portion 74c). When pressed in the circumferential direction, the second end of the second torsion spring 57 is supported by the second drive plate 51 (the wall portion of the first window portion 71a and the wall portion of the second window portion 73a). The torsion spring 57 is compressed.

The second driven plate 59 is configured to be able to output the torque transmitted from the second drive plate 51 and the inertia ring 53 to the connecting gear portion 55.

As shown in FIG. 2, the second driven plate 59 is attached to the turbine hub 17. For example, the second driven plate 59 is fixed to the turbine hub 17. More specifically, the second driven plate 59 is fixed to the flange 17 a of the turbine hub 17 by fixing means such as the rivet 18.

Thereby, the torque output from the second driven plate 59 is transmitted to the turbine hub 17. That is, the torque output from the second driven plate 59 is transmitted to the transmission via the turbine hub 17.

The second driven plate 59 can rotate integrally with the turbine 4 and the turbine hub 17. The second driven plate 59 supports the connection gear portion 55 in a rotatable manner. The second driven plate 59 has a plate body 76 and a support portion 77.

The support portion 77 includes a shaft portion 77a and a sliding member 77b. The shaft portion 77a is formed integrally with the plate body 76. For example, the shaft portion 77 a protrudes from the plate body 76 toward the engine side and is formed integrally with the plate body 76. The shaft portion 77a is disposed in the hole portion 55c of the connection gear portion 55 (see FIG. 3). Here, the shaft center of the shaft portion 77 a is the rotation center P of the connecting gear portion 55. The shaft portion 77a may be separated from the plate body 76. For example, the shaft portion 77a may be configured by attaching the pin member to the plate body 76 as a separate body.

2 and 3, the sliding member 77b is for smoothly rotating the connecting gear portion 55 relative to the shaft portion 77a. The sliding member 77b is, for example, a bush disposed on the outer peripheral portion of the shaft portion 77a. The bush 77b is disposed between the hole portion 55c of the connection gear portion 55 and the shaft portion 77a.

Specifically, a shaft portion 77a is disposed on the inner peripheral portion of the cylindrical portion of the bush 77b. A hole portion 55c of the connection gear portion 55 is disposed on the outer peripheral portion of the cylindrical portion of the bush 77b. A flange portion provided at one end of the cylindrical portion of the bush 77b is disposed between the connecting gear portion 55 and the main plate 61 of the second driven plate 59 in the axial direction. A flange portion provided at the other end portion of the cylindrical portion of the bush 77b is disposed between the connecting gear portion 55 and the plate body 76 of the second driven plate 59 in the axial direction.

Note that the bush 77b is divided into two parts at the axially central part of the cylindrical part. Thereby, as above-mentioned, a bush can be easily arrange | positioned with respect to each member.

[Description of torque flow of torque converter]
Here, the torque flow of the above-described configuration will be described with reference to FIG. Note that the torque shown here may be used as a term including an average torque component and / or a torque fluctuation component.

First, the piston 24 moves to the front cover 2 side, and the friction material 33 attached to the piston 24 is pressed against the front cover 2. Thereby, the torque of the engine is transmitted to the lockup device 7.

Next, in the lockup device 7, torque is transmitted to the first drive plate 25 through the front cover 2 and the piston 24. Then, this torque causes the first torsion spring 26 to expand and contract between the first drive plate 25 and the first driven plate 28. As a result, the torque fluctuation component is attenuated. Thereafter, the average component of the torque input to the first torsion spring 26 and the fluctuation component of the torque that cannot be attenuated by the first torsion spring 26 are transmitted from the first driven plate 28 to the second drive plate 51. . In this way, engine torque is transmitted to the dynamic vibration absorber 8 via the lockup device 7.

Subsequently, in the dynamic vibration damping device 8, torque is transmitted from the second drive plate 51 (the main plate 61, the side plate 63, and the inner ring 65) to the connecting gear portion 55. This torque transmission path corresponds to a first torque transmission path T1 (described later). In this case, at the same time, the torque is transmitted from the second drive plate 51 to the connection gear portion 55 via the second torsion spring 57 and the inertia ring 53. This torque transmission path corresponds to a second torque transmission path T2 (described later). Here, the second torsion spring 57 can be expanded and contracted between the second drive plate 51 and the inertia ring 53 by a torque fluctuation component of the second torque transmission path T2. Here, when the second torsion spring 57 expands and contracts, the torque fluctuation component is attenuated.

Thereafter, the torque of the first torque transmission path T1 and the torque of the second torque transmission path T2 are transmitted from the coupling gear portion 55 to the second driven plate 59. In this manner, the torque output from the lockup device 7 is transmitted to the transmission side via the dynamic vibration absorber 8.

The torque transmission in the dynamic vibration absorber 8 and the operation of the dynamic vibration absorber 8 at the time of torque transmission will be described in detail in the following [Operation of the dynamic vibration absorber].

[Operation of dynamic vibration absorber]
First, the torque output from the lockup device 7 is input to the dynamic vibration absorber 8. Specifically, the torque output from the first driven plate 28 (driven main body portion 28a) of the lockup device 7 is input to the second drive plate 51 (main plate 61 and side plate 63) of the dynamic vibration absorber 8. .

Next, as shown in FIG. 5A, the torque input to the main plate 61 of the second drive plate 51 is transmitted to the inner ring 65 and the second torsion spring 57.

For example, torque transmitted from the main plate 61 of the second drive plate 51 to the inner ring 65 is transmitted to the connecting gear portion 55. In other words, the torque input to the second drive plate 51 (the main plate 61, the side plate 63, and the inner ring 65) is directly transmitted to the connection gear portion 55. Hereinafter, this torque transmission path is referred to as a first torque transmission path T1.

On the other hand, the torque transmitted from the main plate 61 and the side plate 63 of the second drive plate 51 to the second torsion spring 57 is transmitted to the inertia ring 53. This torque is transmitted from the inertia ring 53 to the connecting gear portion 55. In other words, the torque input to the second drive plate 51 (the main plate 61 and the side plate 63) is indirectly transmitted to the connecting gear portion 55 via the second torsion spring 57 and the inertia ring 53. Hereinafter, this torque transmission path is referred to as a second torque transmission path T2.

Here, as shown in FIG. 5B, in the second torque transmission path T2, when the torque (average torque component and torque fluctuation component) input to the second drive plate 51 is less than the predetermined torque, The 2 torsion spring 57 is not activated.

When the second torsion spring 57 is not operated, that is, when the second drive plate 51 is not rotating relative to the inertia ring 53, the connecting gear portion 55 is substantially not operated.

Specifically, when the torque transmitted from the main plate 61 and the side plate 63 to the second torsion spring 57 (the torque of the second torque transmission path T2) is less than the operating torque of the second torsion spring 57, the second The torsion spring 57 is not compressed. For this reason, the connecting gear portion 55 does not substantially rotate between the second drive plate 51 (including the inner gear portion 65b) and the inertia ring 53 (including the outer gear portion 75).

In this case, in a state where the connection gear portion 55 is not substantially rotated, the connection gear portion 55 (the rotation center P of the connection gear portion 55), together with the second drive plate 51 and the inertia ring 53, Move in the direction of rotation. In FIG. 5B, the movement amount in this case is indicated by a reference Y0.

Thus, when the connection gear part 55 moves in the rotation direction without rotating, the average component of the torque of the first torque transmission path T1 and the average component of the torque of the second torque transmission path T2 are the connection gear part. 55 to the second driven plate 59. In this case, since the inertia ring 53 does not rotate relative to the second drive plate 51, the torque fluctuation component of the first torque transmission path T1 and the torque fluctuation component of the second torque transmission path T2 are It is not substantially attenuated.

Subsequently, as shown in FIG. 5C, when the torque input to the second drive plate 51 in the second torque transmission path T2 increases, the second torsion spring 57 operates and the connecting gear portion 55 rotates. The inertia ring 53 rotates relative to the second drive plate 51.

In this case, the second drive plate 51 rotates around the rotation axis O by the average component of torque. The rotation angle at this time is the rotation angle Y11. The inertia ring 53 rotates with respect to the second drive plate 51 by a torque fluctuation component (torque fluctuation). The rotation direction of the inertia ring 53 is opposite to the rotation direction of the second drive plate 51. The rotation angle at this time is the rotation angle Y12.

Here, the absolute value of the rotation angle Y12 of the inertia ring 53 is smaller than the absolute value of the rotation angle Y11 of the second drive plate 51. For this reason, the rotation center P of the connection gear part 55 moves in the circumferential direction between the rotation center P0 determined by the average component of torque and the rotation center P1 determined by the torque fluctuation component. In this state, the connecting gear portion 55 rotates between the second drive plate 51 (including the inner gear portion 65b) and the inertia ring 53 (including the outer gear portion 75).

When the inertia ring 53 rotates in the direction opposite to the rotation direction described above, the rotation center P of the connecting gear portion 55 is the rotation center P0 and the rotation center P1 in the circumferential direction with respect to the rotation center P0. It moves in the circumferential direction between the opposite side (not shown).

In this case, the average component of the torque of the first torque transmission path T1 and the average component of the torque of the second torque transmission path T2 are output from the connection gear portion 55 to the second driven plate 59. Further, the torque fluctuation component of the first torque transmission path T1 and the torque fluctuation component of the second torque transmission path T2 are attenuated by the relative rotation of the inertia ring 53 with respect to the second drive plate 51. In this case, since the rotation center P moves due to a torque fluctuation component, the second drive plate 51 is transmitted with a rotation speed fluctuation corresponding to this movement.

Subsequently, as shown in FIG. 5D, when the torque input to the second drive plate 51 is further increased in the second torque transmission path T2, the operation amount of the second torsion spring 57 is increased. Also at this time, the inertia ring 53 rotates relative to the second drive plate 51 while the connecting gear portion 55 rotates.

In this case, the second drive plate 51 rotates around the rotation axis O by the average component of torque. The rotation angle at this time is the rotation angle Y21. Further, the inertia ring 53 rotates with respect to the second drive plate 51 by a torque fluctuation component. The rotation direction of the inertia ring 53 is opposite to the rotation direction of the second drive plate 51. The rotation angle at this time is the rotation angle Y22.

Here, the absolute value of the rotation angle Y22 of the inertia ring 53 is substantially the same as the absolute value of the rotation angle Y21 of the second drive plate 51. For this reason, the rotation center P0 determined by the average component of torque and the rotation center P1 determined by the torque fluctuation component substantially coincide. That is, in this case, the rotation center P of the connecting gear portion 55 does not substantially move in the circumferential direction due to the varying torque. In this state, the connecting gear portion 55 rotates between the second drive plate 51 (including the inner gear portion 65b) and the inertia ring 53 (including the outer gear portion 75).

Even when the inertia ring 53 rotates in the direction opposite to the above rotation direction, the rotation center P of the connection gear portion 55 does not substantially move in the circumferential direction due to the varying torque.

In this case, the average component of the torque of the first torque transmission path T1 and the torque of the second torque transmission path T2 is output from the connection gear portion 55 to the second driven plate 59. Further, the torque fluctuation component of the first torque transmission path T1 and the torque of the second torque transmission path T2 are attenuated by the relative rotation of the inertia ring 53 with respect to the second drive plate 51. In this case, since the rotation center P does not substantially move due to the torque fluctuation component, the rotation speed fluctuation is not transmitted to the second drive plate 51.

As described above, the state shown in FIG. 5D, that is, the state in which the rotation center P of the connecting gear portion 55 does not substantially move in the circumferential direction due to the torque fluctuation component, most effectively It can be attenuated. That is, in this embodiment, as shown by the solid line in FIG. 6, the dynamic vibration absorber 8 can attenuate the torque fluctuation component most effectively at the rotational speed TG to be attenuated.

Finally, when the torque input to the second drive plate 51 is further increased in the second torque transmission path T2, the frame portion of the third window portion 74c comes into contact with the stopper 62 (see FIG. 3). Thereby, the connection gear part 55 becomes non-rotatable between the inner gear part 65b and the outer gear part 75. In this state, the torque of the first torque transmission path T1 and the second torque transmission path T2 are directly output from the coupling gear portion 55 to the second driven plate 59.

Second Embodiment
FIG. 7 is a partial cross-sectional view of the torque converter 1 according to one embodiment of the present invention. An engine (not shown) is arranged on the left side of FIG. 7, and a transmission (not shown) is arranged on the right side of the figure.

[Configuration of lock-up device]
As shown in FIG. 7, the lockup device 7 is disposed in a space between the front cover 2 and the turbine 4. The lockup device 7 includes a piston 24, a first drive plate 25, a first torsion spring 26, and a first driven plate 28.

As shown in FIG. 8, the dynamic vibration absorber 8 includes a second drive plate 51 (an example of an input unit), an inertia ring 53 (an example of an inertial mass unit), a link unit 55 (an example of a coupling unit), 2 torsion springs 57 (an example of an elastic part) and a second driven plate 59 (an example of an output part).

The second drive plate 51 has a main plate 61, a side plate 63, and an inner pin 65 (an example of a first engagement portion). The main plate 61 is fixed to the first driven plate 28. Specifically, the main plate 61 is fixed to the driven main body portion 28a of the first driven plate 28 by fixing means such as welding. The main plate 61 has a first spring storage part 71 and a link storage part 72.

The link storage unit 72 stores the link unit 55. The link storage portion 72 stores the inner pin 65. Specifically, the inner pins 65 are attached to the link storage portion 72. The link storage portion 72 is a portion pushed out to the piston 24 side (engine side).

The link storage part 72 has an outer peripheral side cylinder part 72a and an annular part 72b. The outer peripheral side cylinder part 72 a is formed integrally with the first spring storage part 71 so as to protrude from the inner peripheral part of the first spring storage part 71 to the piston 24 side (engine side). The annular portion 72b is formed in an annular shape. The outer peripheral part of the annular part 72b is formed integrally with the outer peripheral side cylinder part 72a.

A link portion 55, an inner pin 65, and an outer pin 75 (described later) are disposed on the transmission side of the annular portion 72b. Specifically, the outer pin 75 is disposed on the outer peripheral side of the annular portion 72b, and the inner pin 65 is disposed on the inner peripheral side of the annular portion 72b. In the radial direction, the link portion 55 connects the outer pin 75 and the inner pin.

The link storage portion 72 having this configuration is disposed between the piston 24 and the torque converter body 6 (for example, the turbine 4) in the axial direction. The link storage portion 72 is disposed on the inner peripheral side of the first torsion spring 26. Thereby, a torque converter can be reduced in size in an axial direction.

The side plate 63 is provided facing the main plate 61 in the axial direction. For example, the side plate 63 is disposed to face the main plate 61 with a predetermined interval. The side plate 63 is fixed to the main plate 61 by fixing means such as bolts. As a result, the side plate 63 rotates integrally with the main plate 61. A stopper 62 is fixed between the side plate 63 and the main plate 61 by the fixing means such as the bolt described above.

8 and 9, the inner pin 65 is attached to the main plate 61. For example, the inner pin 65 is fixed to the inner peripheral portion of the main plate 61 by fixing means such as caulking, welding, and bolts. More specifically, the inner pin 65 is fixed to the hole of the link storage portion 72 of the main plate 61 by the fixing means described above.

The inner pin 65 is provided to face the outer pin 75 in the radial direction. The inner pins 65 are provided on the main plate 61 with a predetermined interval in the circumferential direction. Here, each of a plurality of (for example, eight) inner pins 65 is fixed to the inner peripheral portion of the main plate 61 at a predetermined interval in the circumferential direction. A link portion 55 is engaged with each inner pin 65. Specifically, the link portion 55 is rotatably attached to the inner pin 65.

As shown in FIG. 8, the inner pin 65 has a mounting portion 65a, a shaft portion 65b, and a positioning portion 65c. The mounting portion 65a is fixed to the inner peripheral portion (link storage portion 72) of the main plate 61 by the fixing means described above. A link portion 55 is rotatably attached to the shaft portion 65b. Specifically, the shaft portion 65 b is disposed inside a first long hole portion 55 b (described later) of the link portion 55.

The positioning part 65c positions the link part 55 in the axial direction. The positioning portion 65c is formed with a larger diameter than the shaft portion 65b. The positioning portion 65c is disposed between the main plate 61 (the annular portion 72b of the link storage portion 72) and the link portion 55 in the axial direction. The positioning portion 65c is formed integrally with the mounting portion 65a and the shaft portion 65b. The positioning portion 65c may be a bush disposed around the shaft portion 65b.

8 and 9, the inertia ring 53 is disposed between the main plate 61 and the side plate 63 in the axial direction. The inertia ring 53 is formed in a substantially annular shape. The inertia ring 53 includes a ring main body portion 74 and an outer pin 75 (an example of a second engagement portion).

The ring main body portion 74 is disposed between the first spring storage portion 71 and the second spring storage portion 73. The ring main body 74 includes a second annular portion 74a, a plurality (for example, four) of concave portions 74b, and a plurality (for example, four) of third window portions 74c. The second annular portion 74a is formed in an annular shape. The second annular portion 74a is formed in a substantially annular shape. Specifically, the outer peripheral portion of the second annular portion 74a is formed in an annular shape, and the inner peripheral portion of the second annular portion 74a is bent toward the piston 24 (engine side).

The outer pin 75 is attached to the inertia ring 53. For example, the outer pin 75 is fixed to the inner peripheral portion of the inertia ring 53 by fixing means such as press fitting and welding.

The outer pin 75 is provided to face the inner pin 65 in the radial direction. The outer pins 75 are provided on the ring body 74 with a predetermined interval in the circumferential direction. Here, each of the plurality of (for example, eight) outer pins 75 is fixed to the inner peripheral portion of the second annular portion 74a with a predetermined interval in the circumferential direction. A link portion 55 engages with each outer pin 75. Specifically, the link portion 55 is rotatably attached to a shaft portion 75a (described later) of the outer pin 75 and a shaft portion 65b of the inner pin 65.

The outer pin 75 has a shaft portion 75a and a flange portion 75b. A link portion 55 is rotatably attached to the shaft portion 75a. Specifically, the shaft portion 75 a is disposed inside a second long hole portion 55 c (described later) of the link portion 55. The base end portion of the shaft portion 75a is fixed to the inertia ring 53 by a fixing means such as press fitting. The flange portion 75b abuts on the main plate 61 (the annular portion 72b of the link storage portion 72). In this state, the flange portion 75 b is disposed between the main plate 61 (the annular portion 72 b of the link storage portion 72) and the link portion 55 in the axial direction.

As shown in FIG. 8, the inner pin 65 has a mounting portion 65a, a shaft portion 65b, and a positioning portion 65c. The mounting portion 65a is fixed to the inner peripheral portion (link storage portion 72) of the main plate 61 by the fixing means described above. A link portion 55 is rotatably attached to the shaft portion 65b. The positioning part 65c positions the link part 55 in the axial direction. The positioning portion 65c is formed with a larger diameter than the shaft portion 65b. The positioning portion 65c is disposed between the main plate 61 (the annular portion 72b of the link storage portion 72) and the link portion 55 in the axial direction. The positioning portion 65c is formed integrally with the mounting portion 65a and the shaft portion 65b. The positioning portion 65c may be a bush disposed around the shaft portion 65b.

As shown in FIGS. 8 and 9, the link portion 55 connects the second drive plate 51 and the inertia ring 53. Specifically, the link portion 55 connects the second drive plate 51 and the inertia ring 53 so that the inertia ring 53 can move relative to the second drive plate 51. More specifically, the link part 55 connects the second drive plate 51 and the inertia ring 53 so that the inertia ring 53 can rotate relative to the second drive plate 51.

The link portion 55 is configured to be swingable between the second drive plate 51 and the inertia ring 53. For example, when the inertia ring 53 rotates relative to the second drive plate 51, the link portion 55 swings between the inner pin 65 and the outer pin 75.

Here, a plurality of (for example, five) link portions 55 are arranged between the second drive plate 51 and the inertia ring 53.

Each link portion 55 engages with the second drive plate 51 and the inertia ring 53 so as to be swingable between the second drive plate 51 and the inertia ring 53. Specifically, each link portion 55 is disposed between the outer pin 75 and the inner pin 65 in the radial direction. In this state, each link portion 55 is rotatably engaged with the shaft portion 75 a of the outer pin 75 and the shaft portion 65 b of the inner pin 65.

Each link portion 55 is rotatably supported by the second driven plate 59. Each link portion 55 includes a link main body portion 55a, a first long hole portion 55b, a second long hole portion 55c, and a hole portion 55d. The link body 55a is formed in a plate shape that is long in one direction.

The first long hole 55b is formed at one end of the link main body 55a. The inner pin 65 engages with the first long hole portion 55b. For example, the shaft portion 65b of the inner pin 65 is disposed in the first long hole portion 55b. The shaft portion 65b of the inner pin 65 is movable inside the first long hole portion 55b.

The second slot 55c is formed at the other end of the link body 55a. The outer pin 75 engages with the second long hole portion 55c. For example, the shaft portion 75a of the outer pin 75 is disposed in the second long hole portion 55c. The shaft portion 75a of the outer pin 75 is movable inside the second long hole portion 55c.

The hole 55d is formed in the inner periphery of the link main body 55a. A support portion 77 (described later) of the second driven plate 59 is disposed in the hole portion 55d. As a result, the link main body portion 55 a is supported by the second driven plate 59 in a state where the inner pin 65 is engaged with the first long hole portion 55 b and the outer pin 75 is engaged with the second long hole portion 55 c. It can swing around 77.

The second driven plate 59 is configured to output torque transmitted from the second drive plate 51 and the inertia ring 53 to the link portion 55.

As shown in FIG. 8, the second driven plate 59 is attached to the turbine hub 17. For example, the second driven plate 59 is fixed to the turbine hub 17. More specifically, the second driven plate 59 is fixed to the flange 17 a of the turbine hub 17 by fixing means such as the rivet 18.

The second driven plate 59 can rotate integrally with the turbine 4 and the turbine hub 17. The second driven plate 59 supports the link portion 55 so as to be swingable. The second driven plate 59 has a plate body 76 and a support portion 77.

The support portion 77 includes a shaft portion 77a and a sliding member 77b. The shaft portion 77a is formed integrally with the plate body 76. For example, the shaft portion 77 a protrudes from the plate body 76 toward the engine side and is formed integrally with the plate body 76. The shaft portion 77 a is disposed in the hole portion 55 d of the link portion 55. Here, the shaft center of the shaft portion 77 a is the rotation center P of the link portion 55. The shaft portion 77a may be separated from the plate body 76. For example, the shaft portion 77a may be configured by attaching the pin member to the plate body 76 as a separate body.

8 and 9, the sliding member 77b is for smoothly rotating the link portion 55 with respect to the shaft portion 77a. The sliding member 77b is, for example, a bush disposed on the outer peripheral portion of the shaft portion 77a. The bush 77b is disposed between the hole portion 55d of the link portion 55 and the shaft portion 77a.

Specifically, a shaft portion 77a is disposed on the inner peripheral portion of the cylindrical portion of the bush 77b. A hole portion 55d of the link portion 55 is disposed on the outer peripheral portion of the cylindrical portion of the bush 77b. A flange portion provided at one end portion of the cylindrical portion of the bush 77b is disposed between the link portion 55 and the plate body 76 of the second driven plate 59 in the axial direction.

[Description of torque flow of torque converter]
The torque flow of the dynamic vibration damping device of the second embodiment is substantially the same as the torque flow described in the first embodiment. For this reason, the torque flow of 2nd Embodiment is demonstrated here with reference to FIG. 4 of 1st Embodiment. Note that the torque shown here may be used as a term including an average torque component and / or a torque fluctuation component.

Subsequently, in the dynamic vibration absorber 8, torque is transmitted from the second drive plate 51 (main plate 61, side plate 63, and inner ring 65) to the link portion 55. This torque transmission path corresponds to a first torque transmission path T1 (described later). In this case, simultaneously, torque is transmitted from the second drive plate 51 to the link portion 55 via the second torsion spring 57 and the inertia ring 53. This torque transmission path corresponds to a second torque transmission path T2 (described later). Here, the second torsion spring 57 can be expanded and contracted between the second drive plate 51 and the inertia ring 53 by a torque fluctuation component of the second torque transmission path T2. Here, when the second torsion spring 57 expands and contracts, the torque fluctuation component is attenuated.

Thereafter, the torque of the first torque transmission path T1 and the torque of the second torque transmission path T2 are transmitted from the link portion 55 to the second driven plate 59. In this manner, the torque output from the lockup device 7 is transmitted to the transmission side via the dynamic vibration absorber 8.

Next, as shown in FIG. 10A, torque input to the main plate 61 of the second drive plate 51 is transmitted to the inner pin 65 and the second torsion spring 57.

For example, torque transmitted from the main plate 61 of the second drive plate 51 to the inner pin 65 is transmitted to the link portion 55. In other words, torque input to the second drive plate 51 (the main plate 61, the side plate 63, and the inner pin 65) is directly transmitted to the link portion 55. Hereinafter, this torque transmission path is referred to as a first torque transmission path T1.

On the other hand, the torque transmitted from the main plate 61 and the side plate 63 of the second drive plate 51 to the second torsion spring 57 is transmitted to the inertia ring 53 and the outer pin 75. This torque is transmitted from the outer pin 75 to the link portion 55. In other words, the torque input to the second drive plate 51 (the main plate 61 and the side plate 63) is indirectly transmitted to the link portion 55 via the second torsion spring 57, the inertia ring 53, and the outer pin 95. Is done. Hereinafter, this torque transmission path is referred to as a second torque transmission path T2.

Here, as shown in FIG. 10B, in the second torque transmission path T2, when the torque (average torque component and torque fluctuation component) input to the second drive plate 51 is less than the predetermined torque, The 2 torsion spring 57 is not activated.

When the second torsion spring 57 is not operated, that is, when the second drive plate 51 is not swinging with respect to the inertia ring 53, the link portion 55 is substantially not operated.

Specifically, when the torque transmitted from the main plate 61 and the side plate 63 to the second torsion spring 57 (the torque of the second torque transmission path T2) is less than the operating torque of the second torsion spring 57, the second The torsion spring 57 is not compressed. For this reason, the link portion 55 does not substantially swing between the second drive plate 51 (including the inner pin 65) and the inertia ring 53 (including the outer pin 75).

In this case, the link portion 55 (the swing center of the link portion 55) rotates together with the second drive plate 51 and the inertia ring 53 while the link portion 55 is not substantially swung. Move in the direction. In FIG. 10B, the movement amount in this case is indicated by a reference Y0.

Thus, when the link part 55 moves in the rotation direction without swinging, the average component of the torque of the first torque transmission path T1 and the average component of the torque of the second torque transmission path T2 are the link part 55. To the second driven plate 59. In this case, since the inertia ring 53 does not rotate relative to the second drive plate 51, the torque fluctuation component of the first torque transmission path T1 and the torque fluctuation component of the second torque transmission path T2 are It is not substantially attenuated.

Subsequently, as shown in FIG. 10C, when the torque input to the second drive plate 51 increases in the second torque transmission path T2, the second torsion spring 57 operates and the link portion 55 swings. The inertia ring 53 rotates relative to the second drive plate 51.

In this case, the second drive plate 51 rotates around the rotation axis by the average component of torque. The rotation angle at this time is the rotation angle Y11. The inertia ring 53 rotates with respect to the second drive plate 51 by a torque fluctuation component (torque fluctuation). The rotation direction of the inertia ring 53 is opposite to the rotation direction of the second drive plate 51. The rotation angle at this time is the rotation angle Y12.

Here, the absolute value of the rotation angle Y12 of the inertia ring 53 is smaller than the absolute value of the rotation angle Y11 of the second drive plate 51. For this reason, the rotation center P of the link portion 55 moves in the circumferential direction between the rotation center P0 determined by the average component of torque and the rotation center P1 determined by the torque fluctuation component. In this state, the link portion 55 swings between the second drive plate 51 (including the inner pin 65) and the inertia ring 53 (including the outer pin 75).

When the inertia ring 53 rotates in the direction opposite to the rotation direction, the rotation center P of the link portion 55 is the rotation center P0 and the rotation center P1 in the circumferential direction with respect to the rotation center P0. Moves in the circumferential direction between the opposite positions (not shown).

In this case, the average component of the torque of the first torque transmission path T1 and the average component of the torque of the second torque transmission path T2 are output from the link portion 55 to the second driven plate 59. Further, the torque fluctuation component of the first torque transmission path T1 and the torque fluctuation component of the second torque transmission path T2 are attenuated by the relative rotation of the inertia ring 53 with respect to the second drive plate 51. In this case, since the rotation center P moves due to a torque fluctuation component, the second drive plate 51 is transmitted with a rotation speed fluctuation corresponding to this movement.

Subsequently, as shown in FIG. 10D, when the torque input to the second drive plate 51 is further increased in the second torque transmission path T2, the operation amount of the second torsion spring 57 is increased. Also at this time, the inertia ring 53 rotates relative to the second drive plate 51 while the link portion 55 swings.

Here, the absolute value of the rotation angle Y22 of the inertia ring 53 is substantially the same as the absolute value of the rotation angle Y21 of the second drive plate 51. For this reason, the rotation center P0 determined by the average component of torque and the rotation center P1 determined by the torque fluctuation component substantially coincide. That is, in this case, the rotation center P of the link portion 55 does not substantially move in the circumferential direction due to a torque fluctuation component. In this state, the link portion 55 swings between the second drive plate 51 (including the inner pin 65) and the inertia ring 53 (including the outer pin 755).

Even when the inertia ring 53 rotates in the direction opposite to the above rotation direction, the rotation center P of the link portion 55 does not substantially move in the circumferential direction due to the varying torque.

In this case, the average component of the torque of the first torque transmission path T1 and the average component of the torque of the second torque transmission path T2 are output from the link portion 55 to the second driven plate 59. Further, the torque fluctuation component of the first torque transmission path T1 and the torque fluctuation component of the second torque transmission path T2 are attenuated by the relative rotation of the inertia ring 53 with respect to the second drive plate 51. In this case, since the rotation center P does not substantially move due to the torque fluctuation component, the rotation speed fluctuation is not transmitted to the second drive plate 51.

As described above, the state shown in FIG. 10D, that is, the state in which the rotation center P of the link portion 55 does not substantially move in the circumferential direction due to the torque fluctuation component attenuates the torque fluctuation component most effectively. It is ready. That is, in the present embodiment, as shown by the solid line in FIG. 6, the dynamic vibration absorber 8 can most effectively attenuate the torque fluctuation component at the rotation speed TG to be attenuated.

Finally, when the torque input to the second drive plate 51 is further increased in the second torque transmission path T2, the frame portion of the third window portion 74c comes into contact with the stopper 62 (see FIG. 9). Thereby, the link part 55 cannot swing between the inner pin 65 and the outer pin 75. In this state, the torque of the first torque transmission path T1 and the torque of the second torque transmission path T2 are directly output from the connection gear portion 55 to the second driven plate 59.

[Effect of torque converter]
Here, a typical effect of the torque converter 1 in the first embodiment and the second embodiment described above will be described. In addition, the effect demonstrated here is a typical effect of the torque converter 1, Comprising: It is not limited to these effects.

(1) The torque converter 1 is a torque converter 1 for transmitting torque from the engine to the transmission. The torque converter 1 includes a front cover 2, a lockup device 7, and a dynamic vibration absorber 8.

The front cover 2 receives torque from the engine. The lock-up device 7 includes a piston 24 (friction material 33) and a damper portion 30 (first drive plate 25, first torsion spring 26, and first driven plate 28). The piston 24 (friction material 33) permits or cancels transmission of torque from the front cover 2. The damper portion 30 attenuates torque fluctuation from the front cover 2 when torque transmission is permitted in the piston 24 (friction material 33). The dynamic vibration damping device 8 is directly connected to the lockup device 7. The dynamic vibration damping device 8 attenuates torque fluctuations from the lockup device 7 and outputs the torque from the lockup device 7 to the transmission.

In the torque converter 1, when the piston 24 comes into contact with the front cover 2 in the lockup device 7, torque from the engine is transmitted to the damper unit 30 via the piston 24. Next, in the damper part 30, the torque fluctuation from the engine is attenuated. Subsequently, in the dynamic vibration absorber 8, the torque fluctuation output from the lockup device 7 is attenuated. Finally, torque is output from the dynamic vibration absorber 8 to the transmission. On the other hand, when the piston 24 moves away from the front cover 2 in the lockup device 7, torque from the engine is transmitted to the transmission without passing through the dynamic vibration absorber 8.

As described above, in the torque converter 1, when the piston 24 comes into contact with the front cover 2, the fluctuation of the engine torque is attenuated in the lockup device 7, and then the movement directly connected to the lockup device 7 is performed. In the vibration absorber 8, the torque variation of the lockup device 7 is further attenuated. Thereby, in this torque converter 1, torque fluctuation can be attenuate | damped reliably.

In the torque converter 1, when the piston 24 is separated from the front cover 2 in the lockup device 7, the dynamic vibration damping device 8 is arranged independently of the engine, so that the rotational speed of the turbine 4 and the engine The operation vibration and operation sound of the dynamic vibration absorber 8 due to the difference are not substantially generated. Thereby, in this torque converter 1, compared with a prior art, the operating vibration and operating sound of the dynamic vibration damper 8 can be reduced.

(2) The torque converter 1 is preferably configured as follows. The dynamic vibration absorber 8 includes a second drive plate 51, a second driven plate 59, an inertia ring 53, a connecting portion 55 (a connecting gear portion 55 and a link portion 55), and a second torsion spring 57. The second drive plate 51 is connected to the lockup device 7. The second driven plate 59 is connected to the transmission. The inertia ring 53 is movable relative to the second drive plate 51 between the second drive plate 51 and the second driven plate 59. The connecting portion 55 (the connecting gear portion 55 and the link portion 55) is connected to the second driven plate 59 and connected to the second drive plate 51 and the inertia ring 53. The connecting part 55 (the connecting gear part 55 and the link part 55) operates so that the second drive plate 51 and the inertia ring 53 can move relative to each other. The second torsion spring 57 elastically connects the second drive plate 51 and the inertia ring 53.

In the torque converter 1, first, torque from the lockup device 7 is input to the second drive plate 51. Next, when the second torsion spring 57 is actuated by this torque, the connecting portion 55 (the connecting gear portion 55, the link portion 55) operates between the second drive plate 51 and the inertia ring 53, and the inertia ring 53 becomes the second. It moves relative to the drive plate 51. Thereby, the fluctuation | variation of the torque from the lockup apparatus 7 is attenuated.

With this configuration, the torque fluctuation transmitted from the lockup device 7 can be attenuated reliably and effectively.

(3) The torque converter 1 is preferably configured as follows. The first torque transmitted directly from the second drive plate 51 to the connecting portion 55 (the connecting gear portion 55, the link portion 55) and the second drive plate 51 to the inertia ring 53 via the second torsion spring 57. And the second torque further transmitted from the inertia mass body to the connecting portion 55 (the connecting gear portion 55, the link portion 55) is second driven from the connecting portion 55 (the connecting gear portion 55, the link portion 55). Is transmitted to the plate 59.

Note that the first torque is torque transmitted through the first torque transmission path T1. The second torque is torque transmitted through the second torque transmission path T2.

In this case, when the torque from the lockup device 7 is input to the second drive plate 51, the first torque is directly transmitted from the second drive plate 51 to the connecting portion 55 (the connecting gear portion 55, the link portion 55). The second torque is indirectly transmitted from the second drive plate 51 to the connecting portion 55 (the connecting gear portion 55 and the link portion 55). Specifically, the second torque is transmitted from the second drive plate 51 to the inertia ring 53 via the second torsion spring 57, and from the inertia mass body to the connection portion 55 (connection gear portion 55, link portion 55). And further communicated.

With this configuration, the torque from the lockup device 7 can be output to the transmission only by the configuration of the dynamic vibration absorber 8. For example, the torque from the lockup device 7 can be output to the transmission only by the configuration of the dynamic vibration absorber 8 without passing through an engine-side member (for example, a crankshaft or the like). Thereby, the torque fluctuation from the lockup device 7 can be reliably attenuated in the dynamic vibration absorber 8.

(4) The torque converter 1 is preferably configured as follows. When the second torque is less than the operating torque of the second torsion spring 57, the connecting portion 55 (the connecting gear portion 55, the link portion 55) is substantially inoperative and together with the second drive plate 51 and the inertia ring 53. By moving, the torque from the lockup device 7 is transmitted to the second driven plate 59.

With this configuration, the torque input to the second drive plate 51 can be efficiently output from the second driven plate 59. In particular, the torque input to the second drive plate 51 is efficiently output from the second driven plate 59 by operating the dynamic vibration absorber 8 with the above-described configuration at a rotational speed at which no torque fluctuation attenuation is required. be able to.

(5) The torque converter 1 is preferably configured as follows. When the second torque is greater than or equal to the operating torque of the second torsion spring 57, the connection portion 55 (connection gear portion 55) is in a state where the operation center of the connection portion 55 (connection gear portion 55, link portion 55) does not substantially move. , Link portion 55) is actuated to attenuate the torque fluctuation from the lock-up device 7.

With this configuration, the inertia ring 53 can be stably moved relative to the second drive plate 51, and torque fluctuations can be more reliably attenuated in the rotation speed range to be attenuated.

[Other Embodiments]
The present invention is not limited to the above-described embodiments, and various changes or modifications can be made without departing from the scope of the present invention.

(A) In each of the above embodiments, the present invention is applied to the lock-up device 7 of the torque converter 1. However, the present invention can be similarly applied to other power transmission devices.

(B) The configuration of the dynamic vibration absorber 8 is not limited to the above-described embodiments, and various modifications are possible.

DESCRIPTION OF SYMBOLS 1 Torque converter 2 Front cover 4 Turbine 6 Torque converter main body 7 Lockup apparatus 8 Dynamic vibration absorber 51 2nd drive plate 53 Inertia ring 55 Connecting gear part, ring part 57 2nd torsion spring 59 2nd driven plate

Claims

A torque converter for transmitting torque from an engine to a transmission,
A front cover to which torque from the engine is input;
A lockup device comprising: a clutch portion that permits or releases transmission of torque from the front cover; and a damper portion that attenuates fluctuations in torque from the front cover when transmission of the torque is permitted;
A dynamic vibration absorber that is directly connected to the lockup device, attenuates fluctuations in torque from the lockup device, and outputs torque from the lockup device to the transmission;
A torque converter comprising:
The dynamic vibration absorber is
An input connected to the lock-up device;
An output connected to the transmission;
An inertial mass part movable relative to the input part between the input part and the output part;
A connecting part connected to the output part and connected to the input part and the inertial mass part, wherein the input part and the inertial mass part operate to be relatively movable;
An elastic part that elastically connects the input part and the inertial mass part;
The torque converter according to claim 1.
A first torque transmitted directly from the input part to the connecting part, and transmitted from the input part to the inertial mass part via the elastic part and from the inertial mass body to the connecting part; The transmitted second torque is transmitted from the connecting portion to the output portion.
The dynamic vibration absorber for automobiles according to claim 2.
When the second torque is less than the operating torque of the elastic part, the connecting part moves with the input part and the inertial mass part in a substantially inoperative state, thereby generating torque from the lockup device. Is transmitted to the output unit,
The torque converter according to claim 3.
When the second torque is equal to or greater than the operating torque of the elastic part, the connecting part is operated in a state where the operating center of the connecting part is not substantially moved, whereby the torque fluctuation from the lockup device is changed. Attenuated,
The torque converter according to claim 3 or 4.