Vibration reduction device and starting device

Abstract

The vibration damping device of the present invention includes: a first damper including a first elastic body for transmitting torque between an input member connected to an engine and an intermediate member; and a second damper including a second elastic body for transmitting torque between an intermediate member and an output member connected to a transmission, wherein the first elastic body or the like having a higher rigidity or hysteresis of the first damper and the second damper is supported between the input member and the intermediate member with a gap in the rotation direction when no torque is transmitted between the input member and the output member, and the second elastic body or the like of the other of the first damper and the second damper is arranged in a pre-compressed state between the intermediate member and the output member, etc. Thus, when the torque from the engine side and the torque from the transmission side are substantially equal, the vibration of the rotating member of the vibration damping device is well suppressed from being transmitted to the transmission side, and when the torque from the engine side is suddenly reduced.

Description

Technical Field

[0001] The present invention relates to a vibration damping device including an input member, an intermediate member and an output member, and a starting device equipped with the vibration damping device. Background Art

[0002] In the past, there is a known damping mechanism, which includes: a first rotating member (input member) connected to an engine, a second rotating member (intermediate member) capable of relative rotation with respect to the first rotating member, a third rotating member (output member) connected to a transmission and capable of relative rotation with respect to the second rotating member, a first damper having a plurality of first elastic members elastically connecting the first rotating member and the second rotating member in a rotational direction, and a second damper elastically connecting the second rotating member and the third rotating member in a rotational direction and starting to operate with a torque less than the minimum operating torque of the first damper (for example, refer to Patent Document 1). In this damping mechanism, the first damper has the characteristics of low rigidity and high hysteresis torque, and the second damper has the characteristics of low rigidity and low hysteresis torque. In addition, the first elastic member of the first damper is provided on either the first rotating member or the second rotating member in a state of being pre-compressed in the rotational direction. Thus, before the input torque transmitted from the engine to the first rotating member exceeds the minimum operating torque corresponding to the compressed state of the first elastic member, the first elastic member is not compressed, and only the second damper is operated to absorb / dampen torsional vibration. Then, if the input torque exceeds the minimum operating torque, the compression of the first elastic member, that is, the relative rotation of the first rotating member and the second rotating member begins, so that the first damper and the second damper operate in series. As a result, in the damping mechanism, a relatively large load acts in the direction of returning the relative positions of the first rotating member and the second rotating member to the initial state, so that the occurrence of return failure in the high rotation speed range can be suppressed. In addition, a plurality of window portions are formed in the third rotating member, and the plurality of window portions accommodate three types of second elastic bodies constituting the second damper in a manner of being located radially inside the first elastic body, and gaps of different lengths are ensured in the rotation direction between each second coil spring and the corresponding window portion, so that the second damper operates in three stages.

[0003] Patent Document 1: Japanese Patent No. 4755000

[0004] In the above-mentioned conventional damping mechanism, since the first elastic member is provided in a pre-compressed state on either the first rotating member or the second rotating member, when the torsion angle of the first damper is relatively small, the substantial rigidity of the first damper becomes high. Therefore, even when the rigidity of the second damper is low, when the input torque transmitted from the engine to the first rotating member is approximately equal to the torque (deceleration torque caused by resistance) transmitted from the transmission side to the third rotating member, there is a concern that only the vibration (vibration torque) from the engine is transmitted to the transmission side, causing noise, etc. In addition, when the input torque transmitted from the engine to the first rotating member is sharply reduced, there is also a concern that the vibration of the first rotating member to the third rotating member, especially the second rotating member, of the damping mechanism between the engine and the transmission is caused to vibrate, and the vibration of the second rotating member is transmitted to the transmission side, causing noise, etc. Summary of the invention

[0005] Therefore, the main object of the present invention is to provide a vibration damping device and a starting device equipped with the vibration damping device, which can effectively suppress the transmission of vibration from the engine to the transmission side when the torque transmitted from the engine to the input member is approximately equal to the torque transmitted from the transmission side to the output member, and the vibration of the rotating member when the torque transmitted from the engine to the input member suddenly decreases.

[0006] The vibration damping device of the present invention includes: a plurality of rotating members including an input member connected to an engine, an intermediate member, and an output member connected to a transmission; a first vibration damper including a first elastic body for transmitting torque between the input member and the intermediate member; and a second vibration damper including a second elastic body for transmitting torque between the intermediate member and the output member, wherein the first elastic body or the second elastic body having a higher rigidity or hysteresis of the first vibration damper and the second vibration damper is supported between the input member and the intermediate member or between the intermediate member and the output member with a gap in a rotational direction when no torque is transmitted between the input member and the output member, and the first elastic body or the second elastic body having a lower rigidity or hysteresis of the first vibration damper and the second vibration damper is arranged in a pre-compressed state between the intermediate member and the output member or between the input member and the intermediate member.

[0007] In the vibration damping device of the present invention, the first elastic body or the second elastic body of the first vibration damper or the second vibration damper with high rigidity or hysteresis is supported between the input member and the intermediate member or between the intermediate member and the output member with a gap in the rotation direction when no torque is transmitted between the input member and the output member. Thus, if the difference between the torque transmitted from the engine to the input member and the torque transmitted from the transmission side to the output member becomes extremely small, the first vibration damper or the second vibration damper with high rigidity or hysteresis is supported between the input member and the intermediate member or between the intermediate member and the output member with a gap in the rotation direction. Therefore, when the torque from the engine and the torque from the transmission side are approximately equal, by cutting off the torque transmission of the first vibration damper or the second vibration damper with high rigidity or hysteresis, the vibration from the engine can be suppressed from being transmitted to the transmission side. In addition, the first elastic body or the second elastic body of the first vibration damper or the second vibration damper with low rigidity or hysteresis is arranged in a pre-compressed state between the intermediate member and the output member or between the input member and the intermediate member. Thus, when the torsion angle (absolute value) of the other of the first and second dampers with low 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 member suddenly decreases, the vibration of the rotating member, especially the intermediate member, can be well suppressed. BRIEF DESCRIPTION OF THE DRAWINGS

[0008] Figure 1 It is a schematic structural diagram showing the starting device of the present invention.

[0009] Figure 2 It is a cross-sectional view showing the starting device of the present invention.

[0010] Figure 3 It is a front view showing the starting device of the present invention.

[0011] Figure 4 This is a graph showing the relationship between the torsion angle and the input torque in the first damper of the vibration damping device of the present invention.

[0012] Figure 5 This is a graph showing the relationship between the torsion angle and the input torque in the second damper of the vibration damping device of the present invention. DETAILED DESCRIPTION

[0013] Next, a mode for carrying out the present invention will be described with reference to the drawings.

[0014] Figure 1 1 is a schematic structural diagram showing a starting device 1 of the present invention. Figure 21 is a cross-sectional view showing a starting device 1. The starting device 1 shown in these figures 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 component connected to the crankshaft of the engine EG, a pump impeller (input-side fluid transmission component) 4 fixed to the front cover 3, a turbine (output-side fluid transmission component) 5 that can rotate coaxially with the pump impeller 4, a damper hub 7 as an output component connected to the transmission TM, a lock-up clutch 8, a damper device 10 connected to the damper hub 7, etc.

[0015] In the present embodiment, the transmission TM is a mechanical continuously variable transmission (CVT), including: a main shaft PS as a driving side rotating shaft, a secondary shaft SS as a driven side rotating shaft extending in parallel with the main shaft PS, a primary pulley (not shown) provided on the main shaft PS, a secondary pulley (not shown) provided on the secondary shaft SS, and a transmission belt (not shown) wound around the primary pulley and the secondary pulley. The main shaft PS of the transmission TM is connected to the input shaft IS fixed to the damper hub 7 via a forward and reverse switching mechanism BF. The secondary shaft SS of the transmission TM is connected to the left and right drive shafts DS and the drive wheels DW via a gear mechanism and a differential DF not shown.

[0016] The forward / reverse switching mechanism BF includes a planetary gear mechanism (not shown) including a rotating member connected to the input shaft IS and a rotating member connected to the main shaft PS, a clutch C1 and a brake B1, both of which are hydraulic multi-plate friction engagement members. 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 transmitted to the main shaft PS of the transmission TM as it is. In addition, when the brake B1 is engaged and the clutch C1 is released, the main shaft PS rotates in the direction opposite to the rotation direction of the input shaft IS (engine EG). In addition, when both the clutch C1 and the brake B1 are released, the connection between the input shaft IS and the main shaft PS is released.

[0017] The pump impeller 4 of the starting device 1 includes a pump housing (not shown) tightly fixed to the front cover 3, and a plurality of pump blades (not shown) disposed on the inner surface of the pump housing. Figure 2 As shown, the turbine 5 includes a turbine shell 50 and a plurality of turbine blades 51 disposed on the inner surface of the turbine shell 50. The turbine 5 is disposed in a fluid chamber 9 defined by the front cover 3 and the pump impeller 4. The inner periphery of the turbine shell 50 is fixed to a turbine hub 52 supported by a vibration damping hub 7 so as to rotate freely by means of a plurality of rivets. The pump impeller 4 and the turbine 5 are disposed opposite to each other, and a guide vane 6 is coaxially disposed between the two (see FIG. Figure 1), the guide vane 6 rectifies the flow of the working oil (working fluid) from the turbine 5 to the pump 4. The guide vane 6 includes a plurality of guide vane blades, and the rotation direction of the guide vane 6 is set to only one direction by the one-way clutch 60. When the speed difference between the pump 4 and the turbine 5 is large, the pump 4, the turbine 5 and the guide vane 6 function as a torque converter through the action of the guide vane 6. If the speed difference between the two becomes smaller, they function as a hydraulic coupling. However, in the starting device 1, the guide vane 6 and the one-way clutch 60 may be omitted so that the pump 4 and the turbine 5 function only as a hydraulic coupling.

[0018] The lockup clutch 8 selectively performs locking and releasing of the pump impeller 4 and the turbine 5, that is, the front cover 3 and the damper hub 7 (input shaft IS) via the damper device 10 (mechanically). In the present embodiment, the lockup clutch 8 is a hydraulic single-plate friction clutch, which includes a lockup piston 80 disposed inside the front cover 3 and near the inner wall surface of the front cover 3 on the engine EG side so as to be freely movable in the axial direction relative to the input shaft IS, and a friction member 81 attached to the outer peripheral side of the lockup piston 80 and the surface on the front cover 3 side.

[0019] A locking chamber (release side oil chamber) not shown in the figure is defined between the locking piston 80 and the front cover 3 and is opposite to the fluid chamber 9 via the locking piston 80. The locking chamber is connected to a hydraulic control device not shown in the figure via an oil path formed on the input shaft IS or the like. The hydraulic pressure in the locking chamber is made lower than the hydraulic pressure in the fluid chamber 9 by the hydraulic control device, thereby enabling the locking clutch 8 to be engaged, and the front cover 3 is connected to the damping hub 7 via the damping device 10. In addition, the hydraulic oil in the fluid chamber 9 is discharged and the hydraulic oil (hydraulic pressure) is supplied to the locking chamber by the hydraulic control device, thereby enabling the locking clutch 8 to be released to release the connection between the front cover 3 and the damping hub 7. However, the locking clutch 8 may also be a hydraulic multi-plate friction clutch.

[0020] like Figure 1 and Figure 2 As shown, the vibration damping device 10 includes, as rotating members, a driving member (input member) 11, a first intermediate member (first intermediate member) 12, a second intermediate member (second intermediate member) 15, and a driven member (output member) 16. In addition, as torque transmission members (torque transmission elastic bodies), the vibration damping device 10 includes a plurality of (for example, two in this embodiment) outer springs (input-side elastic bodies) SP1 as first elastic bodies arranged close to the outer periphery of the vibration damping device 10, and a plurality of first inner springs (intermediate elastic bodies) SP21 and a second inner spring (output-side elastic body) SP22 as second elastic bodies arranged radially inwardly of the outer springs SP1 and having the same number (for example, three in this embodiment).

[0021] In the following description, unless otherwise specified, the term "axial direction" basically refers to the direction in which the central axis (axis center) of the starting device 1 or the vibration damping device 10 extends. In addition, unless otherwise specified, the term "radial direction" basically refers to the radial direction of the starting device 1 or the vibration damping device 10 or a rotating member of the vibration damping device 10 or the like, that is, the direction in which a straight line extending from the central axis of the starting device 1 or the vibration damping device 10 to a direction (radial direction) perpendicular to the central axis extends. In addition, unless otherwise specified, the term "circumferential direction" basically refers to the circumferential direction of the rotating member of the starting device 1 or the vibration damping device 10 or the like, that is, the direction along the rotation direction of the rotating member.

[0022] In the present embodiment, the outer spring SP1 is an arc-shaped coil spring, and the first inner spring SP21 and the second inner spring SP22 are linear coil springs having the same specifications. The plurality of outer springs SP1 act in parallel between the driving member 11 and the first intermediate member 12, thereby constituting the first damper D1 (see FIG. 1 ) of the damping device 10. Figure 1 ). In addition, the plurality of first inner springs SP21 act in parallel between the first intermediate component 12 and the second intermediate component 15, and the plurality of second inner springs SP22 act in parallel between the second intermediate component 15 and the driven component 16. In addition, the plurality of first inner springs SP21 and the plurality of second inner springs SP22 act in series via the second intermediate component 15 to form the second shock absorber D2 of the shock absorbing device 10. In addition, in the present embodiment, the spring constants of the outer springs SP1, the first inner springs SP21, and the second inner springs SP22 are determined such that the rigidity of the first shock absorber D1, that is, the combined spring constant of the plurality of outer springs SP1, is greater than the rigidity of the second shock absorber D2, that is, the combined spring constant of the plurality of first inner springs SP21 and the second inner springs SP22. As Figure 2 As shown, spring seats 90 are mounted (fitted) on both end portions of each outer spring SP1.

[0023] In addition, in the present embodiment, the hysteresis of the first damper D1, that is, the plurality of outer springs SP1, is greater than the hysteresis of the second damper D2, that is, the plurality of first inner springs SP21 and the second inner springs SP22. The hysteresis of the first damper D1 is quantified as the difference between the torque transmitted from the outer springs SP1 to the first intermediate member 12 when the relative displacement between the driving member 11 (input member) and the driven member 16 (output member) increases and the torque transmitted from the outer springs SP1 to the first intermediate member 12 when the relative displacement between the driving member 11 and the driven member 16 decreases. In addition, the hysteresis of the second damper D2 is quantified as the difference between the torque transmitted from the second inner springs SP22 to the driven member 16 when the relative displacement between the driving member 11 and the driven member 16 increases and the torque transmitted from the second inner springs SP22 to the driven member 16 when the relative displacement between the driving member 11 and the driven member 16 decreases. Furthermore, the specifications of the first inner spring SP21 and the second inner spring SP22 may be different from each other. In addition, the outer spring SP1 may be a linear coil spring, and the first inner spring SP21 and the second inner spring SP22 may be arc-shaped coil springs.

[0024] The driving member 11 of the vibration damping device 10 is formed in an annular shape and is fixed to the lock piston 80 in a manner located in the outer peripheral area of ​​the fluid chamber 9. Figure 2 As shown, the driving member 11 includes an annular fixing portion 111, a plurality of (for example, two in this embodiment) spring support portions 112 extending in an arc shape, and a plurality of (for example, four in this embodiment) torque transmission portions (elastic body abutment portions) 113. The fixing portion 111 is fixed to the lockup piston 80 of the lockup clutch 8 by means of a plurality of rivets. The plurality of spring support portions 112 extend axially outward from the outer periphery of the fixing portion 111 toward the pump impeller 4 and the turbine 5 in a manner that supports (guides) the inner periphery of the corresponding outer spring SP1.

[0025] The plurality of torque transmission parts 113 of the driving member 11 extend radially outwardly from the outer peripheral part of the fixing part 111 in a manner that every two of them are arranged in pairs in the circumferential direction at intervals. The two torque transmission parts 113 that are paired with each other are opposed to 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 mounted on both ends of the outer spring SP1. In addition, each torque transmission part 113 includes a claw part 113a that extends axially toward the pump impeller 4 and the turbine 5 at the radially outer side of the spring support part 112. In addition, in the present embodiment, an annular spring support part 80a is formed on the outer peripheral part of the lock piston 80, and the annular spring support part 80a supports the plurality of outer springs SP1 together with the spring support part 112 of the driving member 11.

[0026] The first intermediate member 12 includes an annular first plate member 13 and an annular second plate member 14. The first plate member 13 is disposed close to the turbine 5 and is rotatably supported by the damper hub 7. Figure 2 and Figure 3 As shown, the first plate component 13 includes: a plurality of (for example, 3 in the present embodiment) spring support portions 131, a plurality of (for example, 3 in the present embodiment) spring support portions 132, a plurality of (for example, 4 in the present embodiment) first outer torque transmission portions (outer elastic body abutment portions) 133o, and a plurality of (for example, 3 in the present embodiment) inner torque transmission portions (inner elastic body abutment portions) 133i.

[0027] A plurality of spring support portions 131 are formed on the first plate member 13 so as to be arranged at intervals (equally spaced) in the circumferential direction. A plurality of spring support portions 132 are formed on the first plate member 13 so as to be arranged at intervals (equally spaced) in the circumferential direction on the radially inner side of the plurality of spring support portions 131, and are radially opposed to the corresponding spring support portions 131 via window portions in the first plate member 13. A plurality of first outer torque transmission portions 133o are formed so as to be arranged in pairs of two at intervals in the circumferential direction on the outer peripheral portion of the first plate member 13. In addition, the two first outer torque transmission portions 133o that are paired with each other are opposed to each other at an interval that is a value longer than the sum of the natural length of the outer spring SP1 and the thickness of the spring seat 90 mounted on both ends of the outer spring SP1. In addition, as Figure 2 As shown, each first outer torque transmission portion 133o includes a claw portion 133a extending axially outward toward the lockup piston 80. One inner torque transmission portion 133i is provided between the spring support portions 131 and 132 (adjacent window portions) adjacent to each other in the circumferential direction.

[0028] 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 piston 80 (front cover 3), and is connected (fixed) to the first plate member 13 by a plurality of rivets. Figure 2As shown, the second plate member 14 includes: a plurality of (for example, three in this embodiment) spring support portions 141, a plurality of (for example, three in this embodiment) spring support portions 142, a plurality of (for example, three in this embodiment) torque transmission portions (elastic body contact portions) 143, and a short cylindrical portion 144. The plurality of spring support portions 141 are formed on the second plate member 14 in a manner of being arranged at intervals (equal intervals) in the circumferential direction. The plurality of spring support portions 142 are formed on the second plate member 14 in a manner of being arranged at intervals (equal intervals) in the circumferential direction on the radially inner side of the plurality of spring support portions 141, and are respectively opposed to the corresponding spring support portions 141 in the radial direction of the second plate member 14 via the window portions. The plurality of torque transmission portions 143 are each provided one between the spring support portions 141 and 142 (adjacent window portions) adjacent to each other in the circumferential direction.

[0029] The second intermediate member 15 is an annular plate body and includes a plurality of (for example, three in this embodiment) torque transmission portions (elastic body contact portions) 153 (see Figure 3 ). The plurality of torque transmission parts 153 extend radially inward from the inner circumference of the second intermediate member 15 and are arranged at intervals (equal intervals) in the circumferential direction. Figure 2 As shown, the second intermediate member 15 is disposed between the first plate member 13 and the second plate member 14 in the axial direction, and is rotatably supported (aligned) by the inner peripheral surface of the cylindrical portion 144 of the second plate member 14 .

[0030] The driven member 16 is an annular plate body, and includes a plurality of (for example, three in this embodiment) torque transmission parts (elastic body contact parts) 163 formed at intervals in the circumferential direction and extending radially outward. Figure 2 As shown, 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 (connected) to the damper hub 7 by a plurality of rivets.

[0031] The plurality of outer springs SP1 are supported (guided) by the spring support portion 80a of the lock piston 80 from the radially outer side and the turbine 5 side (transmission TM side), and are supported (guided) by the plurality of spring support portions 112 of the drive member 11 from the radially inner side. Thus, the plurality of outer springs SP1 are arranged in the outer peripheral area in the fluid chamber 9. In addition, in the mounted state of the vibration damping device 10, that is, in the state where the torque is not transmitted between the drive member 11 and the driven member 16, each torque transmission portion 113 of the drive member 11 abuts against the spring seat 90 mounted on the end of the corresponding outer spring SP1. Thus, in the mounted state of the vibration damping device 10, each outer spring SP1 is held by the two torque transmission portions 113 of the drive member 11 that form a pair with each other. In addition, the spring seat 90 may also be omitted from the vibration damping device 10.

[0032] In addition, when the first plate member 13 and the second plate member 14 are connected to each other, each spring support portion 131 of the first plate member 13 is opposed to the corresponding spring support portion 141 of the second plate member 14, and each spring support portion 132 of the first plate member 13 is opposed to the corresponding spring support portion 142 of the second plate member 14. In addition, the mutually opposed spring support portions 131, 141 and the spring support portions 132, 142 located radially inside the spring support portions 131, 141 respectively support (guide) one corresponding first inner spring SP21 and second inner spring SP22. Thus, the plurality of first inner springs SP21 and second inner springs SP22 are alternately arranged at intervals in the circumferential direction on the radial inside of the plurality of outer springs SP1 so as to overlap with the plurality of outer springs SP1 when viewed in the radial direction.

[0033] In addition, in the mounted state of the vibration damping device 10, each inner torque transmission portion 133i of the first plate member 13 of the first intermediate member 12 and each torque transmission portion 143 of the second plate member 14 abuts against the ends of the first inner spring SP21 and the second inner spring SP22 supported by different spring support portions 131, 132, 141, 142. In addition, each torque transmission portion 153 of the second intermediate member 15 abuts against the ends of the first inner spring SP21 and the second inner spring SP22 supported by the same spring support portions 131, 132, 141, 142. Thus, a set of the first inner spring SP21 and the second inner spring SP22 are connected in series via the torque transmission portion 153 of the second intermediate member 15, so that the second damper D2 arranged radially inside the outer spring SP1, that is, the first damper D1 can be made more rigid. In addition, spring seats (not shown) may be attached to the ends of each of the first inner springs SP21 and each of the second inner springs SP22.

[0034] In addition, the first plate member 13 of the first intermediate member 12 is arranged so that when the vibration reduction device 10 is installed, that is, when no torque is transmitted between the driving member 11 and the driven member 16, Figure 3 As shown in FIG. 1 , each first outer torque transmission portion 133o faces a spring seat 90 mounted on the end of the corresponding outer spring SP1 via a small gap G. That is, in the mounted state of the vibration damping device 10, at least one of the two first outer torque transmission portions 133o that form a pair of each other of the first plate member 13 does not abut against the spring seat 90 of the corresponding outer spring SP1. Figure 2 As shown in FIG. 1 , the claw portion 133 a of the first outer torque transmission portion 133 o of the first plate member 13 is arranged radially inward of the claw portion 113 a of the torque transmission portion 113 of the driving member 11 .

[0035] Furthermore, in the mounted state of the vibration damping device 10, each torque transmission portion 163 of the driven member 16 abuts against the ends of the first inner spring SP21 and the second inner spring SP22 supported by the different spring support portions 131, 132, 141, 142. Thus, the driven member 16 can be connected to the driving 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.

[0036] Furthermore, in the mounted state of the vibration damping device 10, that is, in the state where the torque is not transmitted between the driving member 11 and the driven member 16, each outer spring SP1 is arranged between the two torque transmission parts 113 of the driving member 11, which form a pair with each other, without being pre-compressed. In contrast, each first inner spring SP21 is arranged between the corresponding inner torque transmission part 133i of the first intermediate member 12, the torque transmission part 143, the corresponding torque transmission part 163 of the driven member 16, and the corresponding torque transmission part 153 of the second intermediate member 15, in a pre-compressed state. Similarly, in the mounted state of the vibration damping device 10, each second inner spring SP22 is arranged between the corresponding torque transmission part 153 of the second intermediate member 15, the corresponding torque transmission part 163 of the driven member 16, and the corresponding inner torque transmission part 133i of the first intermediate member 12, and the torque transmission part 143, in a pre-compressed state.

[0037] In addition, as a limiter for limiting the relative rotation between the driving member 11 and the driven member 16, the vibration reduction device 10 includes an input side limiter 17 for limiting the relative rotation between the driving member 11 and the first intermediate member 12, and an output side limiter 18 for limiting the relative rotation between the first intermediate member 12 and the driven member 16.

[0038] In the present embodiment, the input side stopper 17 is composed of a stopper 114 formed on the driving member 11 and a pair of stoppers formed on the outer peripheral portion of the second plate member 14 in a manner opposed to each other with the outer spring SP1 interposed therebetween. Figure 2 and Figure 3 As shown, the stopper 114 is formed by extending a part 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. Thus, the input-side stopper 17 is provided at two locations in the circumferential direction with respect to the vibration damper device 10.

[0039] In the mounted state of the vibration damping device 10, each stopper 114 of the driving member 11 is arranged so as not to abut against the side surface of each stopper between the corresponding pair of stoppers of the second plate member 14. Each stopper 114 of the driving member 11 abuts against the side surface of one of the pair of stoppers of the second plate member 14 located on both sides as the driving member 11 and the first intermediate member 12 rotate relative to each other. Thus, the relative rotation of the driving member 11 and the first intermediate member 12 and the torsion of each outer spring SP1 are restricted.

[0040] The output-side stopper 18 is composed of a stopper portion 134 extending outwardly from the inner circumference of the first plate member 13 in the axial direction and an arc-shaped opening portion 164 formed in the driven member 16 (see Figure 3 ). In the present embodiment, a plurality of limit portions 134 are provided on the first plate member 13 (for example, three in the present embodiment), and the same number of opening portions 164 as the limit portions 134 are provided on the driven member 16, and the output side limiter 18 is provided at a plurality of locations in the circumferential direction relative to the vibration damping device 10 (for example, three in the present embodiment). In the mounted state of the vibration damping device 10, each limit portion 134 of the first plate member 13 is inserted into the corresponding opening portion 164 of the driven member 16 without abutting against the inner wall surfaces on both sides dividing the opening portion 164. The limit portion 134 of the first plate member 13 (first intermediate member 12) abuts against one of the inner wall surfaces of the opening portion 164 located on both sides accompanying the relative rotation of the first intermediate member 12 and the driven member 16. Thus, the relative rotation of the first intermediate member 12 and the driven member 16 and the torsion of each first inner spring SP21 and each second inner spring SP22 are restricted.

[0041] In the present embodiment, the input-side stopper 17 (specifications of the driving member 11, the first intermediate member 12, and the outer spring SP1) and the output-side stopper 18 (specifications of the first intermediate member 12, the second intermediate member 15, the driven member 16, the first inner spring SP21, and the second inner spring SP22) are configured (set) such that when the torque transmitted to the front cover 3, that is, the input torque input to the driving member 11 increases, the output-side stopper 18 and the input-side stopper 17 are operated in this order. That is, in the vibration damping device 10, when the input torque input to the driving member 11 reaches a torque (first value: a predetermined value) T1 that is smaller than the torque T2 (second value) corresponding to the maximum torsion angle θmax of the vibration damping device 10, the relative rotation of the first intermediate member 12 and the driven member 16 (torsion of the first inner spring SP21) is restricted by the output-side stopper 18. When the input torque to the driving member 11 reaches the torque T2, the relative rotation between the driving member 11 and the first intermediate member 12 (torsion of the outer spring SP1) is restricted by the input-side stopper 17. Thus, the vibration damping device 10 has two-stage (two-level) damping characteristics.

[0042] In addition, if Figure 1 and Figure 2 As shown in FIG. 1 , a dynamic damper 20 is connected to the first intermediate member 12 of the rotating member (first rotating member) of the vibration damping device 10. The dynamic damper 20 includes a mass body 21 including the turbine 5, and a plurality of (for example, two in this embodiment) vibration absorbing springs (vibration absorbing elastic bodies) SPd disposed between the mass body 21 and the first intermediate member 12. Here, the "dynamic damper" is a mechanism that adds vibration of the opposite phase to the vibration body at a frequency (engine speed) that matches the resonance frequency of the vibration body to damp the vibration, and is formed by connecting the spring (elastic body) and the mass body in a manner that is not included in the transmission path of the torque (average torque) relative to the vibration body (the first intermediate member 12 in this embodiment). That is, by adjusting the rigidity of the vibration absorbing spring SPd and the weight of the mass body 21, the dynamic damper 20 can damp the vibration of the desired frequency.

[0043] The mass body 21 of the dynamic damper 20 includes, in addition to the turbine 5, an annular member 22 connected to the turbine 5. Figure 2As shown in FIG. 1 , the annular member 22 includes an annular connecting plate 220 and a plurality of (three in this embodiment) annular plates 221, 222, and 223. The inner peripheral portion of the connecting plate 220 is fixed to the turbine hub 52 together with the inner peripheral portion of the turbine shell 50 by a plurality of rivets in such a manner that the connecting plate 220 faces the back of the turbine 5 at a distance. In addition, the connecting plate 220 includes a plurality of (four in this embodiment, for example) torque transmission parts (elastic body contact parts) 225 extending axially at a distance from the outer peripheral portion. The plurality of torque transmission parts 225 are formed symmetrically with respect to the axis of the annular member 22 in such a manner that two (a pair) of two are close to each other. The two torque transmission parts 225 forming a pair face each other at a distance corresponding to the sum of the natural length of the vibration absorbing spring SPd and the thickness of the spring seat 91 fitted (fitted) at both ends of the vibration absorbing spring SPd.

[0044] The annular plates 221, 222, and 223 have the same outer diameter, overlap each other so that their outer peripheral surfaces form a single peripheral surface, and are fixed to the connecting plate 220 by a plurality of rivets. Figure 2 As shown, the inner diameter of the annular plate 222 is larger than that of the annular plate 221, and the inner diameter of the annular plate 223 is larger than that of the annular plate 222. Thus, the connecting plate 220 and the plurality of annular plates 221, 222, 223 can be arranged in the area near the outer periphery of the turbine 5 which is prone to become a dead space.

[0045] On the other hand, Figure 2 and Figure 3 As shown in FIG. 1 , the first plate member 13 of the first intermediate member 12 to which the dynamic damper 20 is connected includes a plurality of (for example, four in this embodiment) second outer torque transmission parts 135 protruding in a manner separated from the spring support part 131 in the radial direction outward at intervals in the circumferential direction. The plurality of second outer torque transmission parts 135 are formed symmetrically with respect to the axis of the first plate member 13 in a manner that two (a pair) of two are close to each other between the first outer torque transmission parts 133o adjacent to each other without the outer spring SP1 interposed therebetween, and each includes a claw part 135a extending in the axial direction toward the lockup piston 80. The two second outer torque transmission parts 135 (claw parts 135a) forming a pair of each other are opposed to each other at an interval corresponding to the sum of the natural length of the vibration absorbing spring SPd and the thickness of the spring seat 91 mounted at both ends of the vibration absorbing spring SPd.

[0046] In the present embodiment, each vibration absorbing spring SPd is a linear coil spring of the same specification. However, the vibration absorbing spring SPd may also be an arc-shaped coil spring. In the mounted state of the vibration damping device 10, each vibration absorbing spring SPd is arranged between a pair of torque transmission parts 225 of the connecting plate 220 (annular member 22) and between a pair of second outer torque transmission parts 135 of the first plate member 13 (first intermediate member 12). That is, the spring seats 91 mounted on both ends of each vibration absorbing spring SPd abut against the corresponding torque transmission part 225 and the second outer torque transmission part 135, respectively.

[0047] Thus, each vibration absorbing spring SPd, that is, the dynamic damper 20 is connected to the first intermediate member 12 of the vibration damping device 10. In addition, in the present embodiment, a plurality of vibration absorbing springs SPd are arranged between two adjacent outer springs SP1 in a manner arranged circumferentially on the same circumference as the outer springs SP1. In addition, each vibration absorbing spring SPd overlaps with the outer spring SP1 in both the axial direction and the circumferential direction of the starting device 1 and the vibration damping device 10. In addition, as Figure 2 As shown in FIG. 1 , the claws 135a of each second outer torque transmission portion 135 of the first plate member 13 and the torque transmission portion 225 of the connecting plate 220 are arranged in the radial direction of the vibration damper device 10. More specifically, the claws 135a of the second outer torque transmission portion 135 abut against the spring seats 91 of the corresponding vibration absorbing springs SPd at the radially inner side of the torque transmission portion 225 of the connecting plate 220. In addition, the spring seats 91 may be omitted from the dynamic damper 20.

[0048] In addition, the dynamic damper 20 (vibration damping device 10) includes a stopper 23 that limits the relative rotation between the annular member 22 (mass body 21) and the first plate member 13 (first intermediate member 12). In the present embodiment, the stopper 23 (specifications of the first intermediate member 12, the annular member 22, and the vibration absorbing springs SPd, etc.) is configured (set) to limit the relative rotation between the annular member 22 and the first intermediate member 12 before each vibration absorbing spring SPd is completely contracted. However, the stopper 23 may be omitted from the dynamic damper 20.

[0049] Furthermore, in the vibration damping device 10 including the above-mentioned dynamic vibration damper 20, an additional contact portion 113x is provided in the driving member 11 which is a rotating member (second rotating member) not connected to the dynamic vibration damper 20. The additional contact portion 113x is provided to contact with the spring seat 91 mounted on the end of the vibration absorbing spring SPd before the relative rotation between the driving member 11 and the driven member 16 is restricted by the input-side stopper 17 and the output-side stopper 18. In the present embodiment, the additional contact portion 113x is included in a plurality of (two in the present embodiment) torque transmission portions 113 which, in the mounted state of the vibration damping device 10, contact with the spring seat 90 mounted on the end of the outer spring SP1 which is located in the rotation direction (in the direction of rotation) when the driving member 11 is rotated by the power from the engine EG (when driven). Figure 3 In other words, in the mounted state of the vibration damping device 10, the plurality of torque transmission parts 113 (including the claw part 113a) abutting against the spring seat 90 mounted on the end part of the outer spring SP1 on the downstream side in the above-mentioned forward rotation direction are extended in the circumferential direction toward the downstream side in the forward rotation direction (the forward rotation direction side) to have a circumferential length longer than the circumferential length required in terms of strength, etc. In the present embodiment, the end part on the downstream side in the forward rotation direction of the torque transmission part 113 extended in the circumferential direction is used as the additional abutment part 113x.

[0050] In the mounted state of the vibration damper device 10, each additional contact portion 113x does not contact the spring seat 91 of the corresponding vibration absorbing spring SPd of the dynamic damper 20, but can contact the spring seat 91 of the corresponding vibration absorbing spring SPd by the rotation of the driving member 11 relative to the first intermediate member 12 in the forward rotation direction. In the present embodiment, the circumferences of the two torque transmission portions 113 (angles around the axis of the vibration damper device 10 defining the circumferences) are determined so that each additional contact portion 113x contacts the spring seat 91 of the corresponding vibration absorbing spring SPd before the relative rotation between the driving member 11 and the first intermediate member 12 is restricted by the input side stopper 17 and substantially at the same time when the input torque input to the driving member 11 reaches the torque T1 and the relative rotation between the first intermediate member 12 and the driven member 16 is restricted by the output side stopper 18. That is, the rotation angle of the driving component 11 relative to the first intermediate component 12 until each additional abutment portion 113x abuts against the spring seat 91 of the corresponding vibration absorbing spring SPd and the driving component 11 (the second rotating member) is connected to the vibration absorbing spring SPd is smaller than the rotation angle of the driving component 11 relative to the driven component 16 until both the input side limiter 17 and the output side limiter 18 are actuated.

[0051] In addition, in the mounted state of the vibration damping device 10, the claw portion 113a included in the additional contact portion 113x is partially arranged in the radial direction (overlapped) with the torque transmission portion 225 of the annular member 22 on the radially outer side. Thus, in the mounted state of the vibration damping device 10, the claw portion 135a of the second outer torque transmission portion 135 of the first plate member 13, the torque transmission portion 225 of the annular member 22, and the claw portion 113a (end portion thereof) included in the additional contact portion 113x are arranged in this order from the inside to the outside. In addition, in the vibration damping device 10, as described above, the claw portion 133a of the first outer torque transmission portion 133o of the first plate member 13 contacts the spring seat 90 of the corresponding outer spring SP1 on the radially inner side than the claw portion 113a of the torque transmission portion 113 of the drive member 11. Thus, it is possible to eliminate interference between the claw 113a of the additional contact portion 113x, the torque transmission portion 225 of the annular member 22, and the claw 135a of the second outer torque transmission portion 135 of the first plate member 13, and it is possible to eliminate interference between the claw 113a of the torque transmission portion 113 of the drive member 11 and the claw 133a of the first outer torque transmission portion 133o of the first plate member 13. As a result, it is possible to ensure a good stroke of the outer spring SP1 and the vibration absorbing spring SPd arranged in the circumferential direction.

[0052] Next, the operations of the starting device 1 and the vibration damping device 10 will be described.

[0053] During the period when the lockup clutch 8 of the starting device 1 is locked and the input-side stopper 17 and the output-side stopper 18 are not in operation, Figure 1 It can be seen that the torque from the engine EG is transmitted to the input shaft IS via the front cover 3, the lock-up clutch 8, the driving member 11, the first damper D1, i.e., the plurality of outer springs SP1, the first intermediate member 12, the second damper D2, i.e., the first inner spring SP21, the second intermediate member 15 and the plurality of second inner springs SP22, the driven member 16, and the damping hub 7. At this time, the fluctuation of the torque transmitted from the engine EG to the front cover 3 is mainly attenuated (absorbed) by the first damper D1 and the second damper D2 of the damping device 10 that act in series, i.e., the outer spring SP1, the first inner spring SP21, and the second inner spring SP22 that act in series.

[0054] In addition, when the torque from the engine EG is transmitted to the first intermediate member 12 when the lock is executed, the mass body 21 (turbine 5 and annular member 22) swings relative to the first intermediate member 12 in accordance with the variable torque transmitted to the first intermediate member 12. As a result, the vibration of the first intermediate member 12 can be damped by adding the vibration of the opposite phase from the swinging mass body 21 to the first plate member 13. As a result, in the starting device 1, the vibration from the engine EG can also be damped (absorbed) by the dynamic damper 20. More specifically, the peak value of the vibration can be divided into two, and the overall vibration level can be reduced, so that the vibration damping performance of the vibration damping device 10 can be further improved.

[0055] In the vibration damping device 10 of the starting device 1, when the input torque input to the driving member 11 reaches the torque T1, the relative rotation between the first intermediate member 12 and the driven member 16 and the torsion of the first inner spring SP21 and the second inner spring SP22 are restricted by the output side stopper 18. In addition, substantially simultaneously with the operation of the output side stopper 18, each additional contact portion 113x of the driving member 11 contacts the spring seat 91 of the corresponding vibration absorbing spring SPd, thereby connecting the driving member 11 and each vibration absorbing spring SPd. When the driving member 11 and each vibration absorbing spring SPd are connected, the first damper D1, that is, the plurality of outer springs SP1 and the plurality of vibration absorbing springs SPd, act in parallel between the driving member 11 and the first intermediate member 12, and function as an elastic body that transmits torque between the two.

[0056] Thus, after the relative rotation between the first intermediate member 12 and the driven member 16 is restricted by the output side stopper 18, the torque from the engine EG is transmitted to the input shaft IS via the front cover 3, the lock-up clutch 8, the drive member 11, the outer spring SP1 (first damper D1) and the vibration absorbing spring SPd acting in parallel, the first intermediate member 12, the second damper D2 with limited deflection (the first inner spring SP21 with limited deflection, the second intermediate member 15, the second inner spring SP22 with limited deflection), the output side stopper 18 arranged in parallel with the second damper D2, the driven member 16, and the damping hub 7. At this time, the fluctuation of the torque input to the front cover 3 is attenuated (absorbed) by the outer spring SP1 and the vibration absorbing spring SPd of the damping device 10 acting in parallel.

[0057] As a result, in the vibration damping device 10 of the starting device 1, the torque (shared torque) that the outer spring SP1 that transmits torque between the driving member 11 and the first intermediate member 12 should bear can be reduced, and a higher torque can be allowed to be input to the driving member 11. In addition, when the input torque input to the driving member 11 becomes higher, the vibration absorbing spring SPd is made to function as an elastic body that transmits torque between the driving member 11 and the first intermediate member 12, thereby making the second damper D2, that is, the first inner spring SP21 and the second inner spring SP22, further lower in rigidity.

[0058] As described above, the plurality of outer springs SP1 (first elastic body) included in the first damper D1 having higher rigidity and hysteresis among the first damper D1 and the second damper D2 of the damper device 10 are supported between the driving member 11 and the first intermediate member 12 with a gap in the rotation direction (a gap of up to twice the gap G) in the mounted state, that is, in the state where no torque is transmitted between the driving member 11 and the driven member 16. Therefore, during the locking period, for example, when the accelerator pedal of the vehicle V is slowly stepped on on a downhill road, if the torque (driving torque) transmitted from the engine EG to the driving member 11 (front cover 3) and the torque (deceleration torque) transmitted from the driving wheel DW to the driven member 16 via the transmission TM etc. according to the road resistance etc. are substantially equal, the outer springs SP1 of the first damper D1 are supported between the driving member 11 and the first intermediate member 12 with a gap in the rotation direction.

[0059] That is, Figure 4 As shown, the first damper D1 of the damping device 10 has a so-called idling interval (blind zone), and when the difference between the torque transmitted from the engine EG to the driving member 11 and the torque transmitted from the transmission TM to the driven member 16 becomes extremely small, Figure 4 As can be seen from the characteristics of the first damper D1 shown, the torque is not substantially transmitted through the first damper D1, that is, the plurality of outer springs SP1. Therefore, in the starting device 1, when the torque from the engine EG is approximately equal to the torque from the transmission TM side, by cutting off the torque transmission by the first damper D1, that is, the plurality of outer springs SP1, the vibration (variable torque) from the engine EG can be suppressed from being transmitted to the input shaft IS (forward-reverse switching mechanism BF and transmission TM) side. As a result, the vibration of the friction plate and the release plate caused by the vibration (variable torque) from the engine EG in the clutch C1 and the brake B1 of the forward-reverse switching mechanism BF, and the noise generated in the spline fitting part can be well suppressed. In addition, the gap G during the assembly of the outer spring SP1 has been made suitable in advance through experiments and analysis.

[0060] In the vibration damping device 10, the first inner spring SP21 and the second inner spring SP22 included in the second vibration damper D2 having lower rigidity and hysteresis than the first vibration damper D1 are arranged in a pre-compressed state between the first intermediate member 12 and the driven member 16, that is, between the first intermediate member 12 and the second intermediate member 15 or between the second intermediate member 15 and the driven member 16. Figure 5 As can be seen from the characteristics of the second shock absorber D2 shown in FIG. 1 , when the torsion angle (absolute value) of the second shock absorber D2 (between the first intermediate member 12 and the driven member 16) is relatively small, the substantial rigidity of the second shock absorber D2, which is lower in rigidity than the first shock absorber D1, can be increased ( Figure 5 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 is suddenly reduced (for example, when crossing zero torque), the vibration of the rotating member of the vibration damping device 10, especially the first intermediate member 12, can be well suppressed, thereby well suppressing the generation of noise and the like caused by the vibration. In addition, the compressive loads of the first inner spring SP21 and the second inner spring SP22 during assembly are made appropriate in advance through experiments and analysis.

[0061] In addition, in the vibration damper device 10, the first inner spring SP21 and the second inner spring SP22 of the second vibration damper D2 located radially inward of the first vibration damper D1 (outer spring SP1) are arranged between the first intermediate member 12 and the driven member 16 in a pre-compressed state. As a result, the hysteresis of the second vibration damper D2 can be reduced, and the substantial rigidity of the second vibration damper D2 when the torsion angle is relatively small can be improved. In addition, the second vibration damper D2 includes the second intermediate member 15, the first inner spring SP21 (intermediate elastic body) arranged between the first intermediate member 12 and the second intermediate member 15 in a pre-compressed state, and the second inner spring SP22 (output-side elastic body) arranged between the second intermediate member 15 and the driven member 16 in a pre-compressed state. Thus, the substantial rigidity of the second damper D2 can be increased when the torsion angle of the second damper D2 is relatively small, and the rigidity of the second damper D2 can be further reduced when the torsion angle increases, thereby further improving the vibration damping performance of the vibration damping device 10. However, the second intermediate member 15 and one of the first inner spring SP21 and the second inner spring SP22 may be omitted from the vibration damping device 10, that is, the second damper D2.

[0062] On the other hand, when the lockup is released by the lockup clutch 8 of the starting device 1, Figure 1It is known that the torque (power) transmitted from the engine EG to the front cover 3 is transmitted to the input shaft IS via the pump impeller 4, the turbine 5, the annular member 22 (connecting plate 220), the vibration absorbing spring SPd, the first intermediate member 12, the second damper D2, i.e., the first inner spring SP21, the second intermediate member 15, the second inner spring SP22, the driven member 16, and the vibration damping hub 7. Thus, when the torque is transmitted from the engine EG to the input shaft IS via the pump impeller 4 and the turbine 5, the driven member 16 and the turbine 5 rotate in the same direction (will) until the above-mentioned stopper 23 is actuated, while the annular member 22 fixed to the turbine 5 and the driven member 16 rotate relatively, thereby each vibration absorbing spring SPd expands and contracts.

[0063] Therefore, in the starting device 1, when the lockup is released by the lockup clutch 8 and the stopper 23 is not actuated, there is a possibility that resonance of the torque transmission system from the turbine 5 to the damper hub 7 including the vibration absorbing spring SPd and the second damper D2 occurs. In contrast, in the starting device 1, the frequency of the resonance can be shifted to the high frequency (high speed) side or the low frequency (low speed) side by adjusting the rigidity, i.e., spring constant, of the vibration absorbing spring SPd corresponding to the requirements of the dynamic damper 20 without changing the rigidity, i.e., spring constant, of the first inner spring SP21 and the second inner spring SP22 of the second damper D2. As a result, the vibration damping performance of the dynamic damper 20 can be well ensured, and when the lockup is released, the resonance of the torque transmission system including the vibration absorbing spring SPd and the second damper D2 can be well suppressed from becoming apparent. In addition, when a relatively large torque is transmitted from the engine EG to the front cover 3 in the unlocked state, the stopper 23 is actuated. This can suppress the torque from being transmitted from the turbine runner 5 to the first intermediate member 12 in a state where each vibration absorbing spring SPd is completely contracted, thereby further improving the durability of each vibration absorbing spring SPd.

[0064] In the above-mentioned vibration damping device 10, the outer spring SP1 of the first vibration damper D1 having higher rigidity and hysteresis than the second vibration damper D2 is supported between the driving member 11 and the first intermediate member 12 with a gap in the rotation direction when no torque is transmitted between the driving member 11 and the driven member 16, and the first inner spring SP21 and the second inner spring SP22 of the second vibration damper D2 having lower rigidity and hysteresis than the first vibration damper D1 are arranged in a pre-compressed state between the first intermediate member 12 and the driven member 16, but the present invention is not limited thereto. That is, the elastic body of the first vibration damper D1 and the second vibration damper D2 having higher rigidity may be supported between the corresponding rotating members with a gap in the rotation direction when no torque is transmitted between the driving member 11 and the driven member 16, and the elastic body of the other having lower rigidity may be arranged in a pre-compressed state between the corresponding rotating members. In addition, it is also possible that the elastic body with higher hysteresis in the first shock absorber D1 and the second shock absorber D2 is supported between the corresponding rotating components in a manner with a gap in the rotation direction when no torque is transmitted between the driving component 11 and the driven component 16, and the elastic body with lower hysteresis is arranged between the corresponding rotating components in a pre-compressed state.

[0065] In the above-mentioned embodiment, the driving member 11 (second rotating member) may be connected to the vibration absorbing spring SPd by, for example, contacting the torque transmission portion 225 of the annular member 22 through the additional contact portion 113x. In addition, the additional contact portion 113x and the output-side stopper 18 may be configured to restrict 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 absorbing spring SPd. In addition, the additional contact portion 113x may be separated from the torque transmission portion 113 in a manner arranged in the circumferential direction with the torque transmission portion 113. In addition, the rotating member (first rotating member) to which the dynamic damper 20 is connected may be, for example, a rotating member other than the first intermediate member 12 such as the driving member 11, and the rotating member (second rotating member) to which the dynamic damper 20 is not connected but connected to the vibration absorbing spring SPd may be, for example, a rotating member other than the driving member 11 such as the first intermediate member 12. Furthermore, the transmission TM may be a step-variable transmission including at least one friction engagement element that does not require the forward / reverse switching mechanism BF.

[0066] As described above, the vibration damping device of the present invention comprises: a plurality of rotating members including an input member (11) connected to an engine (EG), an intermediate member (12), and an output member (16) connected to a transmission (TM); a first vibration damper (D1) including a first elastic body (SP1) for transmitting torque between the input member (11) and the intermediate member (12); and a second vibration damper (D2) including a second elastic body (SP21, SP22) for transmitting torque between the intermediate member (12) and the output member (16), wherein in the vibration damping device (10), the first elastic body having a higher rigidity or hysteresis between the first vibration damper (D1) and the second vibration damper (D2) is The elastic body (SP1) or the second elastic body (SP21, SP22) is supported between the input member (11) and the intermediate member (12) or between the intermediate member (12) and the output member (16) in a manner with a gap in the rotational direction when no torque is transmitted between the input member (11) and the output member (16), and the first elastic body (SP1) or the second elastic body (SP21, SP22) of the other side of the first shock absorber (D1) and the second shock absorber (D2) having low rigidity or hysteresis is arranged in a pre-compressed state between the intermediate member (12) and the output member (16) or between the input member (11) and the intermediate member (12).

[0067] In the vibration damping device of the present invention, the first elastic body or the second elastic body of the first vibration damper or the second vibration damper with high rigidity or hysteresis is supported between the input member and the intermediate member or between the intermediate member and the output member with a gap in the rotation direction when no torque is transmitted between the input member and the output member. Thus, if the difference between the torque transmitted from the engine to the input member and the torque transmitted from the transmission side to the output member becomes extremely small, the first vibration damper or the second vibration damper with high rigidity or hysteresis is supported between the input member and the intermediate member or between the intermediate member and the output member with a gap in the rotation direction. Therefore, when the torque from the engine and the torque from the transmission side are approximately equal, by cutting off the torque transmission of the first vibration damper or the second vibration damper with high rigidity or hysteresis, the vibration from the engine can be suppressed from being transmitted to the transmission side. In addition, the first elastic body or the second elastic body of the first vibration damper or the second vibration damper with low rigidity or hysteresis is arranged in a pre-compressed state between the intermediate member and the output member or between the input member and the intermediate member. Thus, when the torsion angle (absolute value) of the other of the first and second dampers with low 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 member suddenly decreases, the vibration of the rotating member, especially the intermediate member, can be well suppressed.

[0068] In addition, the first damper (D1) may include a plurality of the first elastic bodies (SP1), the second damper (D2) may include a plurality of the second elastic bodies (SP21, SP22), and the composite spring constant of the plurality of the first elastic bodies (SP1) may be greater than the composite spring constant of the plurality of the second elastic bodies (SP21, SP22). That is, when no torque is transmitted between the input member and the output member, the first elastic body of the first damper having a higher rigidity than the second damper may be supported between the input member and the intermediate member with a gap in the rotation direction, and the second elastic body of the second damper having a lower rigidity than the first damper may be arranged between the intermediate member and the output member in a pre-compressed state.

[0069] In addition, the second damper (D2) may be arranged inside the first damper (D1) in the radial direction of the damping device (10), thereby reducing the hysteresis of the second damper (second elastic body) and improving the substantial rigidity of the second damper when the torsion angle is relatively small.

[0070] In addition, the intermediate member may include a first intermediate member (12) and a second intermediate member (15) included in the second damper (D2), and the second elastic body may include an intermediate elastic body (SP21) arranged in a pre-compressed state between the first intermediate member (12) and the second intermediate member (15), and an output-side elastic body (SP22) arranged in a pre-compressed state between the second intermediate member (15) and the output member (16). Thus, the substantial rigidity of the second damper can be increased when the torsion angle of the second damper is relatively small, and the rigidity of the second damper can be further reduced when the torsion angle increases, thereby further improving the vibration attenuation performance of the damping device.

[0071] The starting device of the present invention comprises any one of the above-mentioned damping devices (10), wherein the starting device (1) comprises: an input member (3) connected to the above-mentioned engine (EG); an output member (7) connected to the above-mentioned output member (16) and the above-mentioned transmission (TM); a pump wheel (4) rotating integrally with the above-mentioned input member (3); a turbine wheel (5) rotating along with the rotation of the above-mentioned pump wheel (4); and a lock-up clutch (8) capable of performing a locking operation of connecting the above-mentioned input member (3) to the above-mentioned engine (EG) via the above-mentioned damping device (10). The vibration damping device (10) includes a mass body (21) including the turbine (5), and a vibration absorbing elastic body (SPd) arranged between the mass body (21) and one of the input member (11) and the intermediate member (12), and the other of the input member (11) and the intermediate member (12) is connected to the vibration absorbing elastic body (SPd) when the torque transmitted from the engine (EG) to the input member (11) is greater than a specified value (T1).

[0072] In the starting device of the present invention, when the locking is performed by the lockup clutch and the torque transmitted from the engine to the input member is less than a specified value, a dynamic damper is formed by a mass body including a turbine and a vibration absorbing elastic body to add vibration of the opposite phase to one of the input member and the intermediate member. As a result, the vibration attenuation performance of the damping device can be further improved. In addition, when the locking is performed by the lockup clutch and the torque transmitted from the engine to the input member is greater than a specified value, the other of the input member and the intermediate member is connected to the vibration absorbing elastic body, and the vibration absorbing elastic body functions as an elastic body that transmits torque between the input member and the intermediate member. As a result, the torque (shared torque) that the first elastic body of the first damper should bear can be at least reduced, and a higher torque can be input relative to the input member. On the other hand, in the starting device, when the locking is released by the lockup clutch, the torque is transmitted between the input member and the output member via the torque transmission system from the turbine to the output member including the vibration absorbing elastic body and the second damper, but at this time, there is a concern that resonance of the torque transmission system will occur. In contrast, in the starting device of the present invention, the rigidity of the vibration absorbing elastic body corresponding to the requirements of the dynamic vibration damper is not changed (specifications), and the frequency of the resonance can be shifted to the high frequency (high speed) side by adjusting the rigidity of the second elastic body of the second vibration damper. As a result, the vibration attenuation performance of the dynamic vibration damper can be well ensured, and when the lock is released, the resonance of the torque transmission system including the vibration absorbing elastic body and the second vibration damper can be well suppressed from becoming apparent.

[0073] In addition, the transmission (TM) may be a continuously variable transmission connected to the output member (7) via a forward / reverse switching mechanism (BF) including friction engagement members (C1, B1). In the starting device, when the difference between the torque transmitted from the engine to the input member and the torque transmitted from the transmission side to the output member is relatively small, vibration and noise generated in the friction engagement member of the forward / reverse switching mechanism due to vibration from the engine can be well suppressed.

[0074] Moreover, the present invention is not limited by the above-mentioned embodiment at all, and various changes can be made within the scope of the gist of the present invention. In addition, the method for implementing the above-mentioned invention is always only a specific method of the invention recorded in the invention content column, and does not limit the elements of the invention recorded in the invention content column.

[0075] Industrial Applicability

[0076] The present invention can be used in the fields of manufacturing vibration damping devices and starting devices, and the like.

Claims

1. A vibration reduction device, comprising: A plurality of rotating members including an input member connected to an engine, an intermediate member, and an output member connected to a transmission; a first damper including a first elastic body for transmitting torque between the input member and the intermediate member; and a second damper including a second elastic body for transmitting torque between the intermediate member and the output member. The vibration reduction device is characterized in that: The first elastic body or the second elastic body of the first damper or the second damper having a higher rigidity or hysteresis is supported between the input member and the intermediate member or between the intermediate member and the output member with a gap in the rotation direction when no torque is transmitted between the input member and the output member. The first elastic body or the second elastic body of the first damper or the second damper having lower rigidity or hysteresis is arranged in a pre-compressed state between the intermediate member and the output member or between the input member and the intermediate member. The first vibration absorber includes a plurality of first elastic bodies. The second vibration absorber includes a plurality of the second elastic bodies. A combined spring constant of the plurality of first elastic bodies is greater than a combined spring constant of the plurality of second elastic bodies.

2. The vibration reduction device according to claim 1, characterized in that: The second damper is arranged on the inner side of the first damper in the radial direction of the vibration damping device.

3. The vibration damping device according to claim 1 or 2, characterized in that: The intermediate member includes a first intermediate member and a second intermediate member included in the second shock absorber. The second elastic body includes an intermediate elastic body disposed in a pre-compressed state between the first intermediate member and the second intermediate member, and an output-side elastic body disposed in a pre-compressed state between the second intermediate member and the output member.

4. A starting device comprising the vibration reduction device according to any one of claims 1 to 3, The starting device is characterized by comprising: an input member connected to the engine; an output component connected to the output member and the transmission; a pump impeller that rotates integrally with the input member; a turbine capable of rotating along with the rotation of the pump impeller; as well as a lock-up clutch capable of locking and releasing the input member and the output member connected to each other via the damper device, The vibration damping device includes a mass body including the turbine and a vibration absorbing elastic body disposed between the mass body and one of the input member and the intermediate member. The other of the input member and the intermediate member is connected to the vibration absorbing elastic body when the torque transmitted from the engine to the input member is equal to or greater than a predetermined value.

5. The starting device according to claim 4, characterized in that: The transmission is a continuously variable transmission connected to the output member via a forward / reverse switching mechanism including a friction engagement element.

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