JP7393993B2 - Damper device and starting device - Google Patents

Description

The present disclosure relates to a damper device including an input element, an intermediate element, and an output element, and a starting device equipped with the damper device.

Conventionally, a first rotating member (input element) connected to an engine, a second rotating member (intermediate element) rotatable relative to the first rotating member, and a second rotating member connected to a transmission and relative to the second rotating member. a first damper having a plurality of first elastic members that elastically connect the first rotating member and the second rotating member in the rotational direction; A damper mechanism is known that includes a second damper that elastically connects a member and a third rotating member in the rotational direction and starts operating with a torque smaller than the minimum operating torque of the first damper (for example, as disclosed in the patent (See Reference 1). In this damper mechanism, the first damper has characteristics of low rigidity and high hysteresis torque, and the second damper has characteristics of low rigidity and low hysteresis torque. Further, the first elastic member of the first damper is provided on one of the first and second rotating members in a state in which it is compressed in advance in the rotational direction. As a result, the first elastic member is not compressed and only the second damper is activated until the input torque transmitted from the engine to the first rotating member exceeds the minimum operating torque according to the compression state of the first elastic member. Absorbs and damps torsional vibration. Then, when the input torque exceeds the minimum operating torque, compression of the first elastic member, that is, relative rotation of the first and second rotating members is started, and the first and second dampers are operated in series. As a result, in this damper mechanism, a relatively large load is applied to the first rotating member and the second rotating member in the direction of returning the relative positions of the two to the initial state, which prevents return failure in the high rotational speed region. The occurrence can be suppressed. Further, a plurality of windows are formed in the third rotating member to accommodate three types of second elastic bodies that constitute the second damper, and are located inside the first elastic body in the radial direction. Between the two coil springs and the corresponding windows, gaps having different lengths in the rotational direction are secured so that the second damper operates in three stages.

Patent No. 4755000

In the conventional damper mechanism described above, since the first elastic member is provided in a pre-compressed state on either the first or second rotating member, when the torsion angle of the first damper is relatively small, the first elastic member The actual stiffness of the damper increases. Therefore, even when the second damper has low rigidity, the input torque transmitted from the engine to the first rotating member and the torque transmitted from the transmission side to the third rotating member (deceleration torque due to resistance) are approximately equal to each other. When they become equal, only the vibration (vibration torque) from the engine is transmitted to the transmission, which may cause noise or the like. Furthermore, when the input torque transmitted from the engine to the first rotating member suddenly decreases, the first to third rotating members of the damper mechanism, especially the second rotating member, vibrate between the engine and the transmission. There is also a possibility that the vibration of the second rotating member is transmitted to the transmission side, causing noise or the like.

Therefore, the present disclosure provides that vibrations from the engine are transmitted to the transmission side when the torque transmitted from the engine to the input element and the torque transmitted from the transmission side to the output element are approximately equal; The main object is to provide a damper device that can satisfactorily suppress the vibration of a rotating element when the torque transmitted from an engine to an input element suddenly decreases, and a starting device equipped with the damper device.

The damper device of the present disclosure includes a plurality of rotating elements including an input element connected to an engine, an intermediate element, and an output element connected to a transmission, and a damper device that transmits torque between the input element and the intermediate element. a first damper including a first elastic body; and a second damper including a second elastic body that transmits torque between the intermediate element and the output element; When the torque is not being transmitted between the input element and the output element, one of the first or second elastic bodies having a higher rigidity or hysteresis can be used to connect the input element to the intermediate element or the intermediate element. The first or second elastic body, which is the other one of the first and second dampers having lower rigidity or hysteresis, is supported between the intermediate element and the output element with a gap in the rotational direction, and is supported between the intermediate element and the output element. It is arranged in a pre-compressed state between the output element or between the input element and the intermediate element.

In the damper device of the present disclosure, one of the first and second dampers having higher rigidity or hysteresis, the first or second elastic body, when no torque is transmitted between the input element and the output element, It is supported with a gap in the rotational direction between the input element and the intermediate element or between the intermediate element and the output element. As a result, when the difference between the torque transmitted from the engine to the input element and the torque transmitted from the transmission side to the output element becomes extremely small, one of the first and second dampers with higher rigidity or hysteresis will respond to the input It is supported with a gap in the rotational direction between the element and the intermediate element or between the intermediate element and the output element. Therefore, when the torque from the engine and the torque from the transmission side become approximately equal, the torque transmission by one of the first and second dampers with higher rigidity or hysteresis is cut off, and vibrations from the engine are reduced. It becomes possible to suppress transmission to the transmission side. Further, the first or second elastic body of the other one of the first and second dampers having lower rigidity or hysteresis is in a pre-compressed state between the intermediate element and the output element or between the input element and the intermediate element. It will be placed in Thereby, when the torsion angle (absolute value) of the other of the first and second dampers, which has lower rigidity or hysteresis, is relatively small, the substantial rigidity of the other can be increased. Therefore, when the torque transmitted from the engine to the input element suddenly decreases, it is possible to satisfactorily suppress the vibration of the rotating element, especially the intermediate element.

1 is a schematic configuration diagram showing a starting device of the present disclosure. FIG. 1 is a cross-sectional view showing a starting device of the present disclosure. FIG. 1 is a front view showing a starting device of the present disclosure. It is a chart showing the relationship between the torsion angle and input torque in the first damper of the damper device of the present disclosure. It is a chart showing the relationship between the torsion angle and input torque in the second damper of the damper device of the present disclosure.

Next, embodiments 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 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 V (for example, a front wheel drive vehicle) including an engine (internal combustion engine) EG as a prime mover. The starting device 1 includes a front cover 3 as an input member connected to the crankshaft of the engine EG, a pump impeller (input side fluid transmission element) 4 fixed to the front cover 3, and a pump impeller 4 that can rotate coaxially with the pump impeller 4. It includes a turbine runner (output side fluid transmission element) 5, a damper hub 7 as an output member connected to the transmission TM, a lockup clutch 8, a damper device 10 connected to the damper hub 7, and the like.

In the present embodiment, the transmission TM includes a primary shaft PS as a drive-side rotation shaft, a secondary shaft SS as a driven-side rotation shaft extending parallel to the primary shaft PS, and a primary shaft PS provided on the primary shaft PS. A mechanical continuously variable transmission (CVT) that includes a pulley (not shown), a secondary pulley (not shown) provided on a secondary shaft SS, and a transmission belt (not shown) wound around the primary pulley and the secondary pulley. It is. The primary shaft PS of the transmission TM is connected to an input shaft IS fixed to the damper hub 7 via a forward/reverse switching mechanism BF. The secondary shaft SS of the transmission TM is connected to the left and right drive shafts DS and drive wheels DW via a gear mechanism and a differential DF (not shown).

The forward/reverse switching mechanism BF includes a planetary gear mechanism (not shown) including a rotating element connected to the input shaft IS and a rotating element connected to the primary shaft PS, and a clutch C1, both of which are hydraulic multi-plate frictional engagement elements. and brake B1. When the brake B1 of the forward/reverse switching mechanism BF is released and the clutch C1 is engaged, the power transmitted to the input shaft IS is directly transmitted to the primary shaft PS of the transmission TM. Further, when the brake B1 is engaged and the clutch C1 is released, the primary shaft PS rotates in a direction opposite to the rotational direction of the input shaft IS (engine EG). Furthermore, when both the clutch C1 and the brake B1 are released, the connection between the input shaft IS and the primary shaft PS is released.

The pump impeller 4 of the starting device 1 includes a pump shell (not shown) tightly fixed to the front cover 3 and a plurality of pump blades (not shown) arranged on the inner surface of the pump shell. As shown in FIG. 2, the turbine runner 5 includes a turbine shell 50 and a plurality of turbine blades 51 disposed on the inner surface of the turbine shell 50, and has a fluid chamber defined by the front cover 3 and the pump impeller 4. It is located within 9. The inner peripheral portion of the turbine shell 50 is fixed to a turbine hub 52 rotatably supported by 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 (see FIG. 1) that rectifies the flow of hydraulic oil (working fluid) from the turbine runner 5 to the pump impeller 4 is coaxially disposed between them. will be placed in The stator 6 includes a plurality of stator blades, and the rotation direction of the stator 6 is set to only one direction by a one-way clutch 60. The pump impeller 4, turbine runner 5, and stator 6 function as a torque converter due to the action of the stator 6 when the rotational speed difference between the pump impeller 4 and the turbine runner 5 is large, and function as a fluid coupling when the rotational speed difference between them becomes small. do. However, in the starting device 1, the stator 6 and the one-way clutch 60 may be omitted so that the pump impeller 4 and the turbine runner 5 function only as fluid couplings.

The lock-up clutch 8 performs lock-up to (mechanically) connect the pump impeller 4 and the turbine runner 5, that is, the front cover 3 and the damper hub 7 (input shaft IS) via the damper device 10, and the release of the lock-up. This is done selectively. In this embodiment, the lock-up clutch 8 is a hydraulic single-plate friction clutch, and is moved in the axial direction with respect to the input shaft IS inside the front cover 3 and near the inner wall surface of the front cover 3 on the engine EG side. The lock-up piston 80 includes a freely disposed lock-up piston 80 and a friction material 81 affixed to the outer peripheral side of the lock-up piston 80 and the surface on the front cover 3 side.

A lockup chamber (release side oil chamber), not shown, is defined between the lockup piston 80 and the front cover 3 and faces the fluid chamber 9 via the lockup piston 80. The lockup chamber is connected to a hydraulic control device (not shown) via an oil passage formed in the input shaft IS and the like. By lowering the oil pressure in the lockup chamber to be lower than the oil pressure in the fluid chamber 9 using the hydraulic control device, the lockup clutch 8 can be engaged to connect the front cover 3 and the damper hub 7 via the damper device 10. can. In addition, by draining the hydraulic oil in the fluid chamber 9 and supplying hydraulic oil (hydraulic pressure) into the lockup chamber by the hydraulic control device, the lockup clutch 8 is released and the front cover 3 and the damper hub 7 are connected. Can be canceled. However, the lockup clutch 8 may be a hydraulic multi-disc friction clutch.

As shown in FIGS. 1 and 2, the damper device 10 includes a drive member (input element) 11, a first intermediate member (first intermediate element) 12, and a second intermediate member (second intermediate element) as rotating elements. ) 15 and a driven member (output element) 16. Furthermore, the damper device 10 includes a plurality of (for example, two in this embodiment) outer springs as first elastic bodies disposed close to the outer periphery of the damper device 10 as torque transmitting elements (torque transmitting elastic bodies). (input side elastic body) SP1, and first inner springs (intermediate elastic body) SP21 and a second inner spring (output side elastic body) SP22.

In addition, in the following description, the "axial direction" basically indicates the extending direction of the central axis (axis center) of the starting device 1 and the damper device 10, unless otherwise specified. In addition, unless otherwise specified, "radial direction" basically refers to the radial direction of the rotating elements such as the starting device 1, the damper device 10, and the damper device 10, that is, the center of the starting device 1 and the damper device 10. It shows the direction in which a straight line extends from the axis in a direction (radial direction) perpendicular to the central axis. Furthermore, unless otherwise specified, "circumferential direction" basically refers to the circumferential direction of a rotating element such as the starting device 1, the damper device 10, or the damper device 10, that is, along the rotational direction of the rotating element. Show direction.

In this embodiment, the outer spring SP1 is an arc coil spring, and the first and second inner springs SP21 and SP22 are linear coil springs having the same specifications. The plurality of outer springs SP1 act in parallel between the drive member 11 and the first intermediate member 12 to constitute a first damper D1 (see FIG. 1) of the damper device 10. Further, the plurality of first inner springs SP21 act in parallel between the first intermediate member 12 and the second intermediate member 15, and the plurality of second inner springs SP22 act in parallel between the second intermediate member 15 and the driven member 16. It acts in parallel between. Furthermore, the plurality of first inner springs SP21 and the plurality of second inner springs SP22 act in series via the second intermediate member 15 to constitute the second damper D2 of the damper device 10. In the present embodiment, the spring constants of the outer spring SP1 and the first and second inner springs SP21, SP22 are determined by the stiffness of the first damper D1, that is, the composite spring constant of the plurality of outer springs SP1, and the stiffness of the second damper D2. That is, the spring constant is set to be larger than the composite spring constant of the plurality of first and second inner springs SP21 and SP22. As shown in FIG. 2, spring seats 90 are attached (fitted) to both ends of each outer spring SP1.

Furthermore, in this embodiment, the hysteresis of the first damper D1, that is, the plurality of outer springs SP1 is larger than the hysteresis of the second damper D2, that is, the plurality of first and second inner springs SP21 and SP22. The hysteresis of the first damper D1 is caused by the torque transmitted from the outer spring SP1 to the first intermediate member 12 when the relative displacement between the drive member 11 (input element) and the driven member 16 (output element) increases; It is quantified as the difference between the torque transmitted from the outer spring SP1 to the first intermediate member 12 when the relative displacement between the drive member 11 and the driven member 16 decreases. Further, the hysteresis of the second damper D2 is caused by the torque transmitted from the second inner spring SP22 to the driven member 16 when the relative displacement between the drive member 11 and the driven member 16 increases, and the hysteresis between the drive member 11 and the driven member 16. It is quantified as the difference between the torque transmitted from the second inner spring SP22 to the driven member 16 when the relative displacement with respect to the driven member 16 decreases. Note that the specifications of the first and second inner springs SP21 and SP22 may be different from each other. Further, the outer spring SP1 may be a linear coil spring, and the first and second inner springs SP21 and SP22 may be arc coil springs.

The drive member 11 of the damper device 10 is formed in an annular shape and is fixed to the lockup piston 80 so as to be located in the outer circumferential region within the fluid chamber 9 . As shown in FIG. 2, the drive member 11 includes an annular fixing part 111, a plurality of (in this embodiment, for example, two) spring support parts 112 extending in an arc shape, and a plurality of (in this embodiment, for example, four) spring support parts 112. 113). The fixing portion 111 is fixed to the lockup piston 80 of the lockup clutch 8 via a plurality of rivets. The plurality of spring support parts 112 extend in the axial direction from the outer peripheral part of the fixed part 111 toward the pump impeller 4 and the turbine runner 5 so as to support (guide) the inner peripheral part of the corresponding outer spring SP1. There is.

The plurality of torque transmitting parts 113 of the drive member 11 extend radially outward from the outer periphery of the fixing part 111 at intervals in the circumferential direction so as to form pairs of two and are lined up at intervals in the circumferential direction. ing. The two torque transmitting portions 113 that are paired with each other face each other at an interval corresponding to the sum of the natural length of the outer spring SP1 and the thickness of the spring seat 90 attached to both ends of the outer spring SP1. Further, each torque transmission section 113 includes a claw section 113a that extends radially outward from the spring support section 112 toward the pump impeller 4 and the turbine runner 5 in the axial direction. Further, in this embodiment, an annular spring support portion 80a is formed on the outer circumferential portion of the lockup piston 80 to support the plurality of outer springs SP1 together with the spring support portion 112 of the drive member 11.

The first intermediate member 12 includes a first annular plate member 13 and a second annular plate member 14 . The first plate member 13 is arranged close to the turbine runner 5 and rotatably supported by the damper hub 7 . As shown in FIGS. 2 and 3, the first plate member 13 includes a plurality of (for example, three in this embodiment) spring support parts 131 and a plurality of (for example, three in this embodiment) spring support parts 131. 132, a plurality (in this embodiment, for example, 4) of first outer torque transmission parts (outer elastic body contact parts) 133o, and a plurality (in this embodiment, for example, 3) of inner torque transmission parts (inner (elastic body contact portion) 133i.

The plurality of spring support parts 131 are formed on the first plate member 13 so as to be arranged at intervals (equally spaced) in the circumferential direction. The plurality of spring support parts 132 are formed on the first plate member 13 so as to be lined up at intervals (equally spaced) in the circumferential direction on the radially inner side of the plurality of spring support parts 131, and correspond to each other through windows. The spring support portion 131 and the first plate member 13 face each other in the radial direction. The plurality of first outer torque transmitting portions 133o are formed in pairs on the outer peripheral portion of the first plate member 13 so as to be arranged in pairs at intervals in the circumferential direction. Furthermore, the two first outer torque transmitting parts 133o that are paired with each other have an interval that is longer than the sum of the natural length of the outer spring SP1 and the thickness of the spring seat 90 attached to both ends of the outer spring SP1. and face each other. Further, each first outer torque transmitting portion 133o includes a claw portion 133a extending in the axial direction toward the lockup piston 80, as shown in FIG. One inner torque transmission portion 133i is provided between the spring support portions 131 and 132 (adjacent window portions) that are adjacent to each other along the circumferential direction.

The second plate member 14 of the first intermediate member 12 has a larger inner diameter than the first plate member 13, is disposed close to the lock-up piston 80 (front cover 3), and is connected via a plurality of rivets. It is connected (fixed) to the first plate member 13 . As shown in FIG. 2, the second plate member 14 includes a plurality of (in this embodiment, for example, three) spring support parts 141, a plurality of (in this embodiment, for example, three) spring support parts 142, It includes a plurality (for example, three in this embodiment) of torque transmission parts (elastic body contact parts) 143 and a short cylindrical part 144. The plurality of spring support parts 141 are formed on the second plate member 14 so as to be spaced apart (equally spaced) in the circumferential direction. The plurality of spring support parts 142 are formed on the second plate member 14 so as to be lined up at intervals in the circumferential direction (equally spaced) on the radially inner side of the plurality of spring support parts 141, and correspond to each other through windows. The spring support portion 141 and the second plate member 14 face each other in the radial direction. One of the plurality of torque transmission parts 143 is provided between the spring support parts 141 and 142 (adjacent window parts) that are adjacent to each other along the circumferential direction.

The second intermediate member 15 is an annular plate body, and includes a plurality (for example, three in this embodiment) of torque transmission parts (elastic body contact parts) 153 (see FIG. 3). The plurality of torque transmitting portions 153 extend radially inward from the inner peripheral portion of the second intermediate member 15 and are arranged at intervals (equally spaced) in the circumferential direction. As shown in FIG. 2, the second intermediate member 15 is arranged between the first plate member 13 and the second plate member 14 in the axial direction, and is formed by the inner peripheral surface of the cylindrical portion 144 of the second plate member 14. Rotatably supported (aligned).

The driven member 16 is an annular plate body, and includes a plurality of (for example, three in this embodiment) torque transmitting parts (elastic body contact parts) 163 that are formed at intervals in the circumferential direction and extend radially outward. including. As shown in FIG. 2, the driven member 16 is disposed between the first plate member 13 and the second plate member 14 of the first intermediate member 12 in the axial direction, and is fixed to the damper hub 7 via a plurality of rivets. (concatenated).

The plurality of outer springs SP1 are supported (guided) by the spring support portion 80a of the lockup piston 80 from the radially outer side and from the turbine runner 5 side (transmission TM side), and are supported (guided) by the plurality of spring support portions 112 of the drive member 11. It is supported (guided) from the inside in the radial direction. As a result, the plurality of outer springs SP1 are arranged in the outer circumferential region within the fluid chamber 9. Furthermore, in the installed state of the damper device 10, that is, in the state in which torque is not transmitted between the drive member 11 and the driven member 16, each torque transmitting portion 113 of the drive member 11 is attached to the end of the corresponding outer spring SP1. The spring seat 90 is brought into contact with the spring seat 90. As a result, in the installed state of the damper device 10, each outer spring SP1 is held by the two paired torque transmitting portions 113 of the drive member 11. Note that the spring seat 90 may be omitted from the damper device 10.

Further, when the first and second plate members 13 and 14 are connected to each other, each spring support portion 131 of the first plate member 13 faces the corresponding spring support portion 141 of the second plate member 14, and the first Each spring support portion 132 of the plate member 13 faces a corresponding spring support portion 142 of the second plate member 14 . Further, the spring support parts 131, 141 facing each other and the spring support parts 132, 142 located radially inside the spring support parts 131, 141 each have one corresponding first and second inner spring SP21, SP22. Support (guide) each other. As a result, the plurality of first and second inner springs SP21 and SP22 are arranged alternately at intervals in the circumferential direction inside the plurality of outer springs SP1 in the radial direction so as to overlap with the plurality of outer springs SP1 when viewed from the radial direction. will be placed in

Further, in the installed state of the damper device 10, each inner torque transmitting portion 133i of the first plate member 13 of the first intermediate member 12 and each torque transmitting portion 143 of the second plate member 14 have different spring support portions 131. , 132, 141, 142 between the first and second inner springs SP21, SP22. Further, each torque transmitting portion 153 of the second intermediate member 15 is supported by the same spring supporting portions 131, 132, 141, 142 and is transmitted between the first and second inner springs SP21, SP22 that form a pair with each other. abuts against the end of the As a result, the pair of first and second inner springs SP21 and SP22 are connected in series via the torque transmission part 153 of the second intermediate member 15, so that the outer spring SP1, that is, the radially inner side of the first damper D1 It becomes possible to further reduce the rigidity of the second damper D2 disposed in the second damper D2. Note that a spring seat (not shown) may be attached to the end of each first inner spring SP21 and each second inner spring SP22.

Further, the first plate member 13 of the first intermediate member 12 is connected to each first outer torque transmitting portion 133o when the damper device 10 is attached, that is, when torque is not transmitted between the drive member 11 and the driven member 16. As shown in FIG. 3, the spring seat 90 is arranged to face the spring seat 90 attached to the end of the corresponding outer spring SP1 with a slight gap G therebetween. That is, in the installed state of the damper device 10, at least one of the two paired first outer torque transmitting portions 133o of the first plate member 13 does not come into contact with the spring seat 90 of the corresponding outer spring SP1. . In this embodiment, the claw portion 133a of the first outer torque transmission portion 133o of the first plate member 13 is arranged radially inward of the claw portion 113a of the torque transmission portion 113 of the drive member 11, as shown in FIG. Ru.

Furthermore, in the installed state of the damper device 10, each torque transmission section 163 of the driven member 16 is connected between the first and second inner springs SP21 and SP22 supported by mutually different spring support sections 131, 132, 141, and 142. Abuts on both ends. Thereby, the driven member 16 is connected to the drive member 11 via the plurality of outer springs SP1, the first intermediate member 12, the plurality of first inner springs SP21, the second intermediate member 15, and the plurality of second inner springs SP22. It becomes possible to do so.

When the damper device 10 is installed, that is, when torque is not transmitted between the drive member 11 and the driven member 16, each outer spring SP1 connects the two torque transmitting portions 113 of the drive member 11 that are paired with each other. without being pre-compressed. On the other hand, each first inner spring SP21 connects the corresponding inner torque transmitting part 133i and torque transmitting part 143 of the first intermediate member 12, the corresponding torque transmitting part 163 of the driven member 16, and the corresponding torque transmitting part 163 of the second intermediate member 15. It is arranged in a pre-compressed state between it and the corresponding torque transmission section 153. Similarly, each second inner spring SP22 connects the corresponding torque transmitting portion 153 of the second intermediate member 15, the corresponding torque transmitting portion 163 of the driven member 16, and the first intermediate member 12 in the attached state of the damper device 10. It is disposed in a pre-compressed state between the corresponding inner torque transmission section 133i and torque transmission section 143.

The damper device 10 also includes an input side stopper 17 that serves as a stopper that regulates the relative rotation between the drive member 11 and the driven member 16, and an input side stopper 17 that regulates the relative rotation between the drive member 11 and the first intermediate member 12; 12 and an output side stopper 18 that restricts relative rotation between the driven member 16 and the output side stopper 18 .

In this embodiment, the input side stopper 17 includes a stopper portion 114 formed on the drive member 11 and a pair of stopper portions formed on the outer periphery of the second plate member 14 so as to face each other via the outer spring SP1. Consisted of. The stopper portion 114 is formed by extending a portion of each spring support portion 112 of the drive member 11 further in the axial direction toward the pump impeller 4 and the turbine runner 5, as shown in FIGS. 2 and 3. . Thereby, the input side stoppers 17 are provided at two locations in the circumferential direction with respect to the damper device 10.

In the installed state of the damper device 10, each stopper portion 114 of the drive member 11 is arranged between a corresponding pair of stopper portions of the second plate member 14 so as not to contact the side surface of each stopper portion. Each stopper part 114 of the drive member 11 comes into contact with one side of a pair of stopper parts of the second plate member 14 located on both sides as the drive member 11 and the first intermediate member 12 rotate relative to each other. This restricts the relative rotation between the drive member 11 and the first intermediate member 12 and the twisting of each outer spring SP1.

The output side stopper 18 includes a stopper portion 134 extending in the axial direction from the inner peripheral portion of the first plate member 13, and an arc-shaped opening 164 formed in the driven member 16 (see FIG. 3). ). In this embodiment, a plurality of stopper parts 134 (for example, three in this embodiment) are provided on the first plate member 13, and the same number of openings 164 as the stopper parts 134 are provided on the driven member 16, and the output side stopper 18 is , are provided at a plurality of locations (for example, three locations in this embodiment) in the circumferential direction of the damper device 10. In the installed state of the damper device 10, each stopper portion 134 of the first plate member 13 is inserted into the corresponding opening 164 of the driven member 16 so as not to come into contact with the inner wall surfaces on both sides defining the opening 164. It will be done. The stopper portion 134 of the first plate member 13 (first intermediate member 12) comes into contact with one of the inner wall surfaces of the opening 164 located on both sides as the first intermediate member 12 and driven member 16 rotate relative to each other. come into contact with This restricts the relative rotation between the first intermediate member 12 and the driven member 16 and the twisting of each first inner spring SP21 and each second inner spring SP22.

In this embodiment, the input side stopper 17 (specifications of the drive member 11, the first intermediate member 12, the outer spring SP1, etc.) and the output side stopper 18 (the first intermediate member 12, the second intermediate member 15, the driven member 16, and specifications of the first and second inner springs SP21, SP22, etc.), when the torque transmitted to the front cover 3, that is, the input torque to the drive member 11 increases, the output side stopper 18, the input side stopper It is configured (set) to operate in the order of 17. That is, in the damper device 10, the input torque to the drive member 11 reaches a torque (first value: predetermined value) T1 that is smaller than the torque T2 (second value) corresponding to the maximum torsion angle θmax of the damper device 10. Then, the output side stopper 18 restricts the relative rotation of the first intermediate member 12 and the driven member 16 (twisting of the first inner spring SP21). Further, when the input torque to the drive member 11 reaches the torque T2, the input side stopper 17 restricts the relative rotation between the drive member 11 and the first intermediate member 12 (twisting of the outer spring SP1). Thereby, the damper device 10 has a two-stage (two-stage) damping characteristic.

Furthermore, as shown in FIGS. 1 and 2, a dynamic damper 20 is connected to the first intermediate member 12, which is a rotating element (first rotating element) of the damper device 10. The dynamic damper 20 includes a mass body 21 including the turbine runner 5 and a plurality of (in this embodiment, for example, two) vibration-absorbing springs (vibration-absorbing elastic bodies) disposed between the mass body 21 and the first intermediate member 12. ) SPd. Here, the "dynamic damper" is a mechanism that dampens vibration by adding vibration of opposite phase to the vibrating body at a frequency (engine rotation speed) that matches the resonant frequency of the vibrating body. Here, it is constructed by connecting a spring (elastic body) and a mass body so as not to be included in the transmission path of torque (average torque) to the first intermediate member 12). That is, by adjusting the rigidity of the vibration absorbing spring SPd and the weight of the mass body 21, it becomes possible to damp vibrations of a desired frequency by the dynamic damper 20.

The mass body 21 of the dynamic damper 20 includes, in addition to the turbine runner 5 , an annular member 22 connected to the turbine runner 5 . As shown in FIG. 2, the annular member 22 includes an annular connection plate 220 and a plurality of (in this embodiment, three) annular plates 221, 222, and 223. The inner peripheral part of the connecting plate 220 is fixed to the turbine hub 52 via a plurality of rivets together with the inner peripheral part of the turbine shell 50 so that the connecting plate 220 faces the back surface of the turbine runner 5 with a gap therebetween. . Further, the connection plate 220 includes a plurality of (for example, four in this embodiment) torque transmission portions (elastic body contact portions) 225 extending in the axial direction from the outer circumferential portion at intervals in the circumferential direction. The plurality of torque transmitting portions 225 are formed symmetrically with respect to the axis of the annular member 22 so that two (pairs) of the plurality of torque transmitting portions 225 are adjacent to each other. The two torque transmitting parts 225 that are paired with each other are spaced at intervals corresponding to the sum of the natural length of the vibration absorbing spring SPd and the thickness of the spring seat 91 attached (fitted) to both ends of the vibration absorbing spring SPd. and face each other.

The annular plates 221, 222, 223 have the same outer diameter, are overlapped so that their respective outer peripheral surfaces form a single circumferential surface, and are fixed to the connecting plate 220 via a plurality of rivets. . Further, as shown in FIG. 2, the inner diameter of the annular plate 222 is larger than the inner diameter of the annular plate 221, and the inner diameter of the annular plate 223 is larger than the inner diameter of the annular plate 222. This makes it possible to arrange the connecting plate 220 and the plurality of annular plates 221, 222, 223 in a region near the outer periphery of the turbine runner 5, which tends to be a dead space.

On the other hand, the first plate member 13 of the first intermediate member 12 to which the dynamic damper 20 is connected is spaced radially outward from the spring support portion 131 at intervals in the circumferential direction, as shown in FIGS. 2 and 3. It includes a plurality (for example, four in this embodiment) of second outer torque transmitting parts 135 that protrude in such a manner as to project. The plurality of second outer torque transmitting parts 135 are connected to the axis of the first plate member 13 so that two (pairs) of the second outer torque transmitting parts 135 are adjacent to each other without intervening the outer spring SP1. The claws 135a are formed symmetrically with respect to the center and each includes a claw portion 135a extending in the axial direction toward the lockup piston 80. The two second outer torque transmitting parts 135 (claw parts 135a) that form a pair with each other correspond to the sum of the natural length of the vibration absorbing spring SPd and the thickness of the spring seat 91 attached to both ends of the vibration absorbing spring SPd. facing each other with a certain distance between them.

In this embodiment, each vibration absorbing spring SPd is a straight coil spring with the same specifications. However, the vibration absorbing spring SPd may be an arc coil spring. In the installed state of the damper device 10, each vibration absorption spring SPd is connected between the pair of torque transmitting parts 225 of the connecting plate 220 (annular member 22) and between the pair of second torque transmitting parts 225 of the first plate member 13 (first intermediate member 12). It is arranged between the outer torque transmitting parts 135. That is, the spring seats 91 attached to both ends of each vibration-absorbing spring SPd abut on the corresponding torque transmitting section 225 and second outer torque transmitting section 135, respectively.

Thereby, each vibration absorbing spring SPd, that is, the dynamic damper 20 is connected to the first intermediate member 12 of the damper device 10. Furthermore, in this embodiment, one vibration absorbing spring SPd is arranged between two adjacent outer springs SP1 so as to be lined up in the circumferential direction on the same circumference as the outer spring SP1. Further, each vibration absorbing spring SPd overlaps the outer spring SP1 in both the axial direction and the circumferential direction of the starting device 1 and the damper device 10. Further, the claw portions 135a of each second outer torque transmitting portion 135 of the first plate member 13 and the torque transmitting portion 225 of the connecting plate 220 are arranged in the radial direction of the damper device 10, as shown in FIG. More specifically, the claw portion 135a of the second outer torque transmitting portion 135 contacts the spring seat 91 of the corresponding vibration absorbing spring SPd on the radially inner side of the torque transmitting portion 225 of the connecting plate 220. Note that the spring seat 91 may be omitted from the dynamic damper 20.

Furthermore, the dynamic damper 20 (damper device 10) includes a stopper 23 that restricts relative rotation between the annular member 22 (mass body 21) and the first plate member 13 (first intermediate member 12). In this embodiment, the stopper 23 (specifications of the first intermediate member 12, the annular member 22, the vibration absorbing spring SPd, etc.) is configured to stop the annular member 22 and the first intermediate member 12 before each vibration absorbing spring SPd completely contracts. It is configured (set) to restrict relative rotation. However, the stopper 23 may be omitted from the dynamic damper 20.

In addition, in the damper device 10 including the dynamic damper 20, the dynamic damper 20 is connected to the drive member 11, which is a rotating element (second rotating element), by the input side and output side stoppers 17, 18. An additional contact portion 113x is provided so as to come into contact with the spring seat 91 attached to the end of the vibration absorbing spring SPd before relative rotation with the member 16 is restricted. In the present embodiment, the additional contact portion 113x is provided in the rotational direction (direction of the arrow in FIG. 3, hereinafter referred to as "direction of the arrow in FIG. It is included in a plurality of (in this embodiment, two) torque transmitting parts 113 that abut on the spring seat 90 attached to the end of the outer spring SP1 on the downstream side (progressing direction side) in the "rotating direction"). That is, in the attached state of the damper device 10, the plurality of torque transmitting parts 113 (including the claw parts 113a) that come into contact with the spring seat 90 attached to the downstream end in the normal rotation direction of the outer spring SP1 have a high strength in terms of strength. It is extended in the circumferential direction on the downstream side in the normal rotation direction (on the traveling direction side) so as to have a longer circumferential length than the circumferential length required by the above. In this embodiment, the downstream end in the normal rotation direction of the torque transmitting portion 113 extended in the circumferential direction is used as the additional contact portion 113x.

In the installed state of the damper device 10 , each additional contact portion 113 By rotating in the direction of rotation, it is possible to contact the spring seat 91 of the corresponding vibration absorbing spring SPd. In this embodiment, each additional contact portion 113x is connected to the input side stopper 17 before the relative rotation between the drive member 11 and the first intermediate member 12 is regulated, and when the input torque to the drive member 11 is equal to the torque T1. At the same time that the relative rotation between the first intermediate member 12 and the driven member 16 is regulated by the output side stopper 18, the two torque transmitters are brought into contact with the spring seat 91 of the corresponding vibration absorption spring SPd. The circumferential length of the portion 113 (the angle around the axis of the damper device 10 that defines the circumferential length) is determined. That is, the first intermediate member 12 of the drive member 11 until each additional contact portion 113x contacts the spring seat 91 of the corresponding vibration absorption spring SPd and the drive member 11 (second rotating element) is connected to the vibration absorption spring SPd. The rotation angle with respect to the driven member 16 is smaller than the rotation angle of the drive member 11 with respect to the driven member 16 until all of the input side and output side stoppers 17 and 18 are activated.

In addition, in the installed state of the damper device 10, the claw portion 113a included in the additional contact portion 113x is partially aligned radially with the torque transmitting portion 225 of the annular member 22 on the radially outer side of the torque transmitting portion 225 ( Overlap). As a result, in the attached state of the damper device 10, the claw portion 135a of the second outer torque transmitting portion 135 of the first plate member 13, the torque transmitting portion 225 of the annular member 22, and the claw portion 113a included in the additional contact portion 113x. (its ends) are lined up in this order from the inside to the outside. In addition, in the damper device 10, as described above, the claw portion 133a of the first outer torque transmitting portion 133o of the first plate member 13 is radially inner than the claw portion 113a of the torque transmitting portion 113 of the drive member 11. It comes into contact with the spring seat 90 of the corresponding outer spring SP1. As a result, interference between the claw portion 113a of the additional contact portion 113x, the torque transmission portion 225 of the annular member 22, and the claw portion 135a of the second outer torque transmission portion 135 of the first plate member 13 is eliminated, and the drive member 11 Interference between the claw portion 113a of the torque transmitting portion 113 and the claw portion 133a of the first outer torque transmitting portion 133o of the first plate member 13 can be eliminated. As a result, it is possible to ensure good strokes of the outer spring SP1 and the vibration absorbing spring SPd that are arranged in the circumferential direction.

Next, the operations of the starting device 1 and the damper device 10 will be explained.

As can be seen from FIG. 1, while lock-up is executed by the lock-up clutch 8 of the starting device 1 and the input-side and output-side stoppers 17, 18 are not operating, the torque from the engine EG is transmitted to the front cover 3, The lock-up clutch 8, the drive member 11, the first damper D1, that is, the plurality of outer springs SP1, the first intermediate member 12, the second damper D2, that is, the first inner spring SP21, the second intermediate member 15, and the plurality of second inner springs SP22. , driven member 16, and damper hub 7 to the input shaft IS. At this time, fluctuations in the torque transmitted from the engine EG to the front cover 3 are mainly caused by the first damper D1 and the second damper D2 of the damper device 10 that act in series, that is, the outer spring SP1, the first and It is damped (absorbed) by the second inner springs SP21 and SP22.

Further, when the torque from the engine EG is transmitted to the first intermediate member 12 during lockup, the mass body 21 (turbine runner 5 and annular member 22 ) swings relative to the first intermediate member 12. Thereby, the vibration of the first intermediate member 12 can be damped by applying opposite phase vibrations from the oscillating mass body 21 to the first plate member 13. As a result, in the starting device 1, the dynamic damper 20 also damps (absorbs) vibrations from the engine EG, and more specifically, it becomes possible to divide the vibration peak into two and reduce the overall vibration level. Therefore, the vibration damping performance of the damper device 10 can be further improved.

Furthermore, in the damper device 10 of the starting device 1, when the input torque to the drive member 11 reaches the torque T1, the output side stopper 18 stops the relative rotation between the first intermediate member 12 and the driven member 16, and the first and second Twisting of inner springs SP21 and SP22 is restricted. Further, almost simultaneously with the operation of the output side stopper 18, each additional contact portion 113x of the drive member 11 comes into contact with the spring seat 91 of the corresponding vibration absorption spring SPd, and the drive member 11 is connected to each vibration absorption spring SPd. When the drive member 11 is connected to each vibration absorption spring SPd, the first damper D1, that is, the plurality of outer springs SP1 and the plurality of vibration absorption springs SPd act in parallel between the drive member 11 and the first intermediate member 12. However, it functions as an elastic body that transmits torque between the two.

As a result, after the relative rotation between the first intermediate member 12 and the driven member 16 is regulated by the output side stopper 18, the torque from the engine EG is applied to the front cover 3, lock-up clutch 8, drive member 11 in parallel. Acting outer spring SP1 (first damper D1), vibration absorption spring SPd, first intermediate member 12, second damper D2 whose deflection is regulated (first inner spring SP21 whose deflection is regulated, second intermediate member 15, deflection It is transmitted to the input shaft IS via a path including the second inner spring SP22), the output side stopper 18 arranged in parallel with the second damper D2, the driven member 16, and the damper hub 7. At this time, fluctuations in the torque input to the front cover 3 are attenuated (absorbed) by the outer spring SP1 and the vibration absorption spring SPd of the damper device 10, which act in parallel.

As a result, in the damper device 10 of the starting device 1, the torque to be handled by the outer spring SP1 that transmits torque between the drive member 11 and the first intermediate member 12 (shared torque) is reduced, and the torque applied to the drive member 11 is reduced. It becomes possible to allow high torque input. Furthermore, when the input torque to the drive member 11 increases, the vibration absorption spring SPd is made to function as an elastic body that transmits torque between the drive member 11 and the first intermediate member 12, so that the second damper D2, that is, the first Also, the second inner springs SP21 and SP22 can be made lower in rigidity.

Further, as described above, among the first and second dampers D1 and D2 of the damper device 10, the plurality of outer springs SP1 (first elastic bodies) included in the first damper D1 having high rigidity and high hysteresis are in the attached state. That is, in a state where no torque is transmitted between the drive member 11 and the driven member 16, there is a gap in the rotational direction between the drive member 11 and the first intermediate member 12 (at most, a gap twice the above gap G). ) is supported. Therefore, while the lockup is being executed, for example, when the accelerator pedal of the vehicle V is depressed on a downhill road, the torque (driving torque) transmitted from the engine EG to the drive member 11 (front cover 3) and the road resistance When the torques (deceleration torques) transmitted from the driving wheels DW to the driven member 16 via the transmission TM etc. are approximately equal to each other, each outer spring SP1 of the first damper D1 It is supported with a gap in the rotational direction between it and the intermediate member 12.

That is, the first damper D1 of the damper device 10, as shown in FIG. As can be seen from the characteristics of the first damper D1 shown in FIG. 4, when the difference between the torque transmitted to the It disappears. Therefore, in the starting device 1, when the torque from the engine EG and the torque from the transmission TM side become approximately equal, the torque transmission by the first damper D1, that is, the plurality of outer springs SP1 is cut off, and the torque from the engine EG is cut off. It is possible to suppress vibrations (fluctuation torque) from being transmitted to the input shaft IS (forward/reverse switching mechanism BF and transmission TM). As a result, the clutch C1 and brake B1 of the forward/reverse switching mechanism BF can effectively suppress vibrations of the friction plate and separator plate caused by vibrations (fluctuation torque) from the engine EG and noise generation at the spline fitting part. becomes possible. Note that the gap G when assembling the outer spring SP1 is adjusted in advance through experimentation and analysis.

Furthermore, in the damper device 10, the first and second inner springs SP21 and SP22 included in the second damper D2, which has lower rigidity and hysteresis than the first damper D1, are connected between the first intermediate member 12 and the driven member 16, That is, it is disposed between the first intermediate member 12 and the second intermediate member 15 or between the second intermediate member 15 and the driven member 16 in a pre-compressed state. As a result, as can be seen from the characteristics of the second damper D2 shown in FIG. 5, when the torsion angle (absolute value) of the second damper D2 (between the first intermediate member 12 and the driven member 16) is relatively small, The substantial rigidity (inclination of the broken line in FIG. 5) of the second damper D2, which has lower rigidity than the first damper D1, can be increased. As a result, for example, when the accelerator pedal of the vehicle V is suddenly released and the torque transmitted from the engine EG to the drive member 11 suddenly decreases (for example, when crossing zero torque), the rotating element of the damper device 10, In particular, it is possible to satisfactorily suppress the vibration of the first intermediate member 12 and to satisfactorily suppress the generation of noise caused by the vibration. Note that the compressive load at the time of assembling the first and second inner springs SP21 and SP22 is adjusted in advance through experimentation and analysis.

In addition, in the damper device 10, the first and second inner springs SP21 and SP22 of the second damper D2, which is located radially inward of the first damper D1 (outer spring SP1), connect the first intermediate member 12 and the driven member 16. It is placed in a pre-compressed state between them. This makes it possible to reduce the hysteresis of the second damper D2 while increasing the substantial rigidity when the torsion angle of the second damper D2 is relatively small. The second damper D2 also includes a second intermediate member 15 and a first inner spring SP21 (intermediate elastic body) disposed in a pre-compressed state between the first intermediate member 12 and the second intermediate member 15. , a second inner spring SP22 (output side elastic body) disposed between the second intermediate member 15 and the driven member 16 in a pre-compressed state. As a result, when the torsional angle of the second damper D2 is relatively small, the substantial rigidity of the second damper D2 is increased, and when the torsional angle increases, the rigidity of the second damper D2 is made smaller. It becomes possible to further improve the vibration damping performance of the device 10. However, the second intermediate member 15 and one of the first and second inner springs SP21 and SP22 may be omitted from the damper device 10, that is, the second damper D2.

On the other hand, when the lock-up is released by the lock-up clutch 8 of the starting device 1, as can be seen from FIG. Runner 5, annular member 22 (connection plate 220), vibration absorption spring SPd, first intermediate member 12, second damper D2, that is, first inner spring SP21, second intermediate member 15 and second inner spring SP22, driven member 16, damper hub 7 to the input shaft IS. When torque is transmitted from the engine EG to the input shaft IS via the pump impeller 4 and the turbine runner 5 in this way, the driven member 16 is the same as the turbine runner 5 until the above-mentioned stopper 23 operates. The vibration absorbing spring SPd expands and contracts as the annular member 22 fixed to the turbine runner 5 and the driven member 16 rotate relative to each other.

Therefore, in the starting device 1, while the lockup is released by the lockup clutch 8 and the stopper 23 is not operating, the torque transmission system from the turbine runner 5 including the vibration absorption spring SPd and the second damper D2 to the damper hub 7 is Resonance may occur. On the other hand, in the starting device 1, the first and second inner springs SP21 of the second damper D2 are , the frequency of resonance can be shifted to the high frequency (high rotation) side or to the low frequency (low rotation) side by adjusting the rigidity, that is, the spring constant of the SP22. As a result, while ensuring good vibration damping performance of the dynamic damper 20, it is possible to effectively prevent resonance of the torque transmission system including the vibration absorption spring SPd and the second damper D2 from becoming apparent when the lockup is released. It becomes possible to suppress this. Furthermore, when a relatively large torque is transmitted from the engine EG to the front cover 3 in a state where the lock-up is released, the stopper 23 is activated. Thereby, it is possible to suppress transmission of torque from the turbine runner 5 to the first intermediate member 12 in a state where each vibration absorption spring SPd is completely contracted, thereby further improving the durability of each vibration absorption spring SPd.

In addition, in the damper device 10, the outer spring SP1 of the first damper D1, which has higher rigidity and hysteresis than the second damper D2, is driven when no torque is transmitted between the drive member 11 and the driven member 16. The first and second inner springs SP21 and SP22 of the second damper D2, which is supported with a gap in the rotational direction between the member 11 and the first intermediate member 12 and whose rigidity and hysteresis are lower than that of the first damper D1, are Although it is disposed between the intermediate member 12 and the driven member 16 in a pre-compressed state, the present invention is not limited thereto. In other words, one of the first and second dampers D1 and D2, which has a higher rigidity, has an elastic body that rotates between the corresponding rotating elements when no torque is transmitted between the drive member 11 and the driven member 16. The other elastic body, which is supported with a gap in and has lower rigidity, may be disposed in a pre-compressed state between the corresponding rotating elements. Furthermore, among the first and second dampers D1 and D2, one of the elastic bodies with high hysteresis causes a rotational direction between the corresponding rotating elements when no torque is transmitted between the drive member 11 and the driven member 16. The other elastic body supported with a gap in and having low hysteresis may be disposed in a pre-compressed state between the corresponding rotating elements.

Further, in the embodiment described above, the drive member 11 (second rotating element) may be connected to the vibration absorption spring SPd by the additional contact portion 113x coming into contact with the torque transmission portion 225 of the annular member 22, for example. Further, the additional contact portions 113x and the output side stopper 18 prevent the relative rotation between the first intermediate member 12 and the driven member 16 after each additional contact portion 113x contacts the spring seat 91 of the corresponding vibration absorption spring SPd. It may be configured to be regulated. Further, the additional contact portion 113x may be separated from the torque transmission portion 113 so as to be lined up with the torque transmission portion 113 in the circumferential direction. Further, the rotating element (first rotating element) to which the dynamic damper 20 is connected may be a rotating element other than the first intermediate member 12, such as the drive member 11, for example, and the dynamic damper 20 is not connected to the vibration absorbing spring SPd. The rotating element (second rotating element) coupled to may be a rotating element other than the drive member 11, such as the first intermediate member 12, for example. Further, the transmission TM may be a stepped transmission including at least one frictional engagement element that does not require the forward/reverse switching mechanism BF.

As described above, the damper device of the present disclosure includes a plurality of input elements (11) connected to the engine (EG), an intermediate element (12), and an output element (16) connected to the transmission (TM). a first damper (D1) including a first elastic body (SP1) that transmits torque between the input element (11) and the intermediate element (12); and the intermediate element (12). In a damper device (10) including a second damper (D2) including a second elastic body (SP21, SP22) that transmits torque to and from the output element (16), the first and second dampers (D1 . is supported with a gap in the rotational direction between the input element (11) and the intermediate element (12) or between the intermediate element (12) and the output element (16), and The first or second elastic body (SP1, SP21, SP22), which is the other one of the first and second dampers (D1, D2) with lower rigidity or hysteresis, is the intermediate element (12) and the output element (16). or between the input element (11) and the intermediate element (12) in a pre-compressed state.

In the damper device of the present disclosure, one of the first and second dampers having higher rigidity or hysteresis, the first or second elastic body, when no torque is transmitted between the input element and the output element, It is supported with a gap in the rotational direction between the input element and the intermediate element or between the intermediate element and the output element. As a result, when the difference between the torque transmitted from the engine to the input element and the torque transmitted from the transmission side to the output element becomes extremely small, one of the first and second dampers with higher rigidity or hysteresis will respond to the input It is supported with a gap in the rotational direction between the element and the intermediate element or between the intermediate element and the output element. Therefore, when the torque from the engine and the torque from the transmission side become approximately equal, the torque transmission by one of the first and second dampers with higher rigidity or hysteresis is cut off, and vibrations from the engine are reduced. It becomes possible to suppress transmission to the transmission side. Further, the first or second elastic body of the other one of the first and second dampers having lower rigidity or hysteresis is in a pre-compressed state between the intermediate element and the output element or between the input element and the intermediate element. It will be placed in Thereby, when the torsion angle (absolute value) of the other of the first and second dampers, which has lower rigidity or hysteresis, is relatively small, the substantial rigidity of the other can be increased. Therefore, when the torque transmitted from the engine to the input element suddenly decreases, it is possible to satisfactorily suppress the vibration of the rotating element, especially the intermediate element.

Further, the first damper (D1) may include a plurality of first elastic bodies (SP1), and the second damper (D2) may include a plurality of second elastic bodies (SP21, SP22). ), and the composite spring constant of the plurality of first elastic bodies (SP1) may be larger than the composite spring constant of the plurality of second elastic bodies (SP21, SP22). . That is, when no torque is transmitted between the input element and the output element, the first elastic body of the first damper, which has higher rigidity than the second damper, is connected between the input element and the intermediate element in the rotational direction. The second elastic body of the second damper, which has lower rigidity than the first damper, may be disposed in a pre-compressed state between the intermediate element and the output element.

Furthermore, the second damper (D2) may be arranged inside the first damper (D1) in the radial direction of the damper device (10). This makes it possible to reduce the hysteresis of the second damper (second elastic body) while increasing the substantial rigidity when the torsion angle of the second damper is relatively small.

Further, the intermediate element may include a first intermediate element (12) and a second intermediate element (15) included in the second damper (D2), and the second elastic body is an intermediate elastic body (SP21) disposed in a pre-compressed state between the first intermediate element (12) and the second intermediate element (15); and the second intermediate element (15) and the output element. (16) and an output side elastic body (SP22) disposed in a pre-compressed state between the output side elastic body (SP22) and the output side elastic body (SP22). As a result, when the torsion angle of the second damper is relatively small, the substantial rigidity of the second damper is increased, and when the torsion angle increases, the rigidity of the second damper is made smaller, thereby reducing the vibration of the damper device. It becomes possible to further improve damping performance.

A starting device of the present disclosure includes an input member (3) connected to the engine (EG), the output element (16), and the speed changer in a starting device (1) including any one of the damper devices (10) described above. An output member (7) connected to the machine (TM), a pump impeller (4) that rotates together with the input member (3), and a turbine runner ( 5) and a lock-up clutch (8) capable of performing lock-up and release of the lock-up for connecting the input member (3) and the output member (7) via the damper device (10). and the damper device (10) is arranged between a mass body (21) including the turbine runner (5) and between the mass body (21) and one of the input element (11) and the intermediate element (12). the other of the input element (11) and the intermediate element (12) is arranged such that the torque transmitted from the engine (EG) to the input element (11) is predetermined. It is connected to the vibration absorbing elastic body (SPd) when the value is equal to or greater than the value (T1).

In the starting device of the present disclosure, when the lockup clutch executes lockup and the torque transmitted from the engine to the input element is less than a predetermined value, the mass body including the turbine runner and the vibration absorbing elastic body A dynamic damper is configured to apply antiphase vibration to one of the intermediate elements. Thereby, the vibration damping performance of the damper device can be further improved. Furthermore, when lock-up is executed by the lock-up clutch and the torque transmitted from the engine to the input element is greater than or equal to a predetermined value, the other of the input element and the intermediate element is connected to the vibration-absorbing elastic body, and the vibration-absorbing elastic body The body acts as an elastic body that transmits torque between the input element and the intermediate element. This makes it possible to reduce the torque (shared torque) that at least the first elastic body of the first damper should handle, while allowing higher torque to be input to the input element. On the other hand, in such a starting device, when the lockup clutch is released, the input member and the output member are connected via the torque transmission system from the turbine runner to the output member including the vibration absorbing elastic body and the second damper. Torque is transmitted, but at this time, there is a risk that resonance will occur in the torque transmission system. On the other hand, in the starting device of the present disclosure, the rigidity of the second elastic body of the second damper can be adjusted without changing the rigidity etc. (specifications) of the vibration absorbing elastic body according to the demand for the dynamic damper. The resonance frequency can be shifted to the high frequency (high rotation) side. This ensures good vibration damping performance of the dynamic damper while effectively suppressing resonance in the torque transmission system including the vibration absorbing elastic body and the second damper when the lockup is released. becomes possible.

Furthermore, the transmission (TM) may be a continuously variable transmission connected to the output member (7) via a forward/reverse switching mechanism (BF) including frictional engagement elements (C1, B1). . In such a starting device, when the difference between the torque transmitted from the engine to the input element and the torque transmitted from the transmission side to the output element becomes relatively small, vibrations from the engine reduce the friction coefficient of the forward/reverse switching mechanism. It becomes possible to satisfactorily suppress vibration and noise from occurring in the coupling element.

It goes without saying that the invention of the present disclosure is not limited to the above-described embodiments, and that various changes can be made within the scope of the present disclosure. Furthermore, the above-mentioned mode for carrying out the invention is merely one specific form of the invention described in the column of means for solving the problem; It is not intended to limit the elements of the invention.

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

1 Starting device, 3 Front cover, 4 Pump impeller, 5 Turbine runner, 50 Turbine shell, 51 Turbine blade, 52 Turbine hub, 6 Stator, 60 One-way clutch, 7 Damper hub, 8 Lock-up clutch, 80 Lock-up piston, 80a Spring Support part, 81 Friction material, 9 Fluid chamber, 10 Damper device, 11 Drive member, 111 Fixing part, 112 Spring support part, 113 Torque transmission part, 113a Claw part, 113x Additional contact part, 114 Stopper part, 12 First intermediate member, 13 first plate member, 131 spring support section, 132 spring support section, 133a, 135a claw section, 133i inner torque transmission section, 133o first outer torque transmission section, 134 stopper section, 135 second outer torque transmission section , 14 second plate member, 141 spring support part, 142 spring support part, 143 torque transmission part, 144 cylindrical part, 15 second intermediate member, 153 torque transmission part, 16 driven member, 163 torque transmission part, 164 opening part , 17 input side stopper, 18 output side stopper, 20 dynamic damper, 21 mass body, 22 annular member, 220 connection plate, 221, 222, 223 annular plate, 225 torque transmission section, 23 stopper, 90, 91 spring seat, B1 Brake, BF forward/backward switching mechanism, C1 clutch, D1 1st damper, D2 2nd damper, DF differential gear, DS drive shaft, DW drive wheel, EG engine, G gap, IS input shaft, PS primary shaft, SP1 outer spring , SP21 first inner spring, SP22 second inner spring, SPd vibration absorption spring, SS secondary shaft, V vehicle.

Claims (5)

a plurality of rotating elements including an input element connected to an engine, an intermediate element, and an output element connected to a transmission; a first elastic body including a first elastic body that transmits torque between the input element and the intermediate element; A damper device including a damper and a second damper including a second elastic body that transmits torque between the intermediate element and the output element,
Of the first and second dampers, one of the first and second elastic bodies, which has a higher rigidity or hysteresis, is configured to act on the input element when no torque is transmitted between the input element and the output element. and the intermediate element or between the intermediate element and the output element with a gap in the rotation direction,
The first or second elastic body, which is the other one of the first and second dampers with lower rigidity or hysteresis, is preliminarily connected between the intermediate element and the output element or between the input element and the intermediate element. placed in a compressed state ,
The first damper includes a plurality of the first elastic bodies,
The second damper includes a plurality of the second elastic bodies,
A composite spring constant of the plurality of first elastic bodies is larger than a composite spring constant of the plurality of second elastic bodies . The damper device according to claim 1 ,
The second damper is a damper device arranged inside the first damper in the radial direction of the damper device. The damper device according to claim 1 or 2 ,
The intermediate element includes a first intermediate element and a second intermediate element included in the second damper,
The second elastic body is an intermediate elastic body disposed in a pre-compressed state between the first intermediate element and the second intermediate element, and an intermediate elastic body disposed in a pre-compressed state between the second intermediate element and the output element. A damper device including an output side elastic body arranged in a compressed state. A starting device including the damper device according to any one of claims 1 to 3 ,
an input member connected to the engine;
an output member coupled to the output element and the transmission;
a pump impeller that rotates together with the input member;
a turbine runner rotatable as the pump impeller rotates;
a lockup clutch capable of locking up the input member and the output member via the damper device and releasing the lockup;
The damper device includes:
a mass body including the turbine runner;
a vibration absorbing elastic body disposed between the mass body and one of the input element and the intermediate element;
The other of the input element and the intermediate element is a starting device that is connected to the vibration absorbing elastic body when the torque transmitted from the engine to the input element is equal to or greater than a predetermined value. The starting device according to claim 4 ,
In the starting device, the transmission is a continuously variable transmission connected to the output member via a forward/reverse switching mechanism including a frictional engagement element.

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