Damper device and starting device

A damper device includes a dynamic damper that has third springs coupled to an intermediate member and that also has, as a mass body coupled to the third springs, a turbine runner and a coupling member etc. The third springs of the dynamic damper are disposed so as to overlap both in the axial and radial directions of the damper device second springs that have higher rigidity than first springs and that are disposed inward of the first springs to transfer torque between a drive member and a driven member.

CROSS REFERENCE TO RELATED APPLICATIONS

This application is a National Stage of International Application No. PCT/JP2014/052162 filed Jan. 30, 2014, claiming priority based on Japanese Patent Application No. 2013-015253, filed Jan. 30, 2013, the contents of all of which are incorporated herein by reference in their entirety.

TECHNICAL FIELD

The present subject matter relates to damper devices including an input element, an output element, first elastic bodies that transfer torque between the input element and the output element, and second elastic bodies that are disposed inward of the first elastic bodies to transfer the torque between the input element and the output element, and starting devices including such a damper device.

BACKGROUND ART

Conventionally, a damper device including a dynamic damper that has third elastic bodies coupled to any of the rotary elements forming the damper device and a mass body coupled to the third elastic bodies is known as this type of damper device (see, e.g., Patent Document 1). In this damper device, the third elastic bodies forming the dynamic damper are disposed radially outward or inward of the first and second elastic bodies that transfer torque between the input element and the output element or are disposed between the first and second elastic bodies in the radial direction.

RELATED ART DOCUMENT

Patent Document

SUMMARY OF THE INVENTION

However, in the case where the third elastic bodies of the dynamic damper are disposed at a different radial position from the first and second elastic bodies that transfer torque between the input element and the output element as in the above conventional damper device, the outer diameter of the damper device increases, and it is difficult to make the entire device compact.

It is a primary object to suppress an increase in outer diameter of a damper device including a dynamic damper to make the entire device compact.

The following measures are taken for a damper device and a starting device to achieve the above primary object.

A damper device includes an input element, an output element, first elastic bodies that transfer torque between the input element and the output element, and second elastic bodies that are disposed inward of the first elastic bodies to transfer the torque between the input element and the output element, in which the second elastic bodies have higher rigidity than the first elastic bodies, the damper device includes a dynamic damper having third elastic bodies that are coupled to any of the rotary elements forming the damper device and a mass body that is coupled to the third elastic bodies, and the third elastic bodies are disposed so as to overlap the second elastic bodies both in axial and radial directions of the damper device.

This damper device includes the dynamic damper having the third elastic bodies that are coupled to any of the rotary elements and the mass body that is coupled to the third elastic bodies. The third elastic bodies of the dynamic damper are disposed so as to overlap both in the axial and radial directions of the damper device the second elastic bodies that have higher rigidity than the first elastic bodies and that are disposed inward of the first elastic bodies to transfer the torque between the input element and the output element. This can suppress an increase in outer diameter of the damper device and can make the entire device more compact as compared to the case where the third elastic bodies of the dynamic damper are disposed radially outward or inward of the first elastic bodies and the second elastic bodies or disposed between the first and second elastic bodies in the radial direction. Moreover, in this damper device, the third elastic bodies can be placed without increasing the rigidity of the first elastic bodies. Namely, both the second and third elastic bodies can be placed while the low rigidity of the first elastic bodies is maintained which particularly affects damping capability. That is, reducing the rigidity of the first elastic bodies can reduce the overall rigidity of the damper device and can ensure satisfactory damping capability thereof even if the axial length (circumferential length) of the inner second elastic bodies is reduced. Accordingly, sufficient space can be secured to place the third elastic bodies of the dynamic damper, and the appropriate third elastic bodies according to vibration to be damped can be used. Namely, damping capability of the dynamic damper can be optimized. As a result, in this damper device, the overall damping capability of the device can be ensured, and reduction in size of the device can also be implemented.

The damper device may further include: a centrifugal pendulum vibration absorbing device having a support member that rotates together with any of the rotary elements forming the damper device, and a plurality of pendulum mass bodies that are swingably coupled to the support member. The first elastic bodies may be disposed so as to be shifted from the second elastic bodies in the axial direction, and the plurality of pendulum mass bodies of the centrifugal pendulum vibration absorbing device may be disposed outward of the second and third elastic bodies so as to surround the second and third elastic bodies. The entire damper device including the centrifugal pendulum vibration absorbing device can thus be made compact (in particular, an increase in axial length thereof can be suppressed), and vibration can be damped (absorbed) by the first and second elastic bodies, the dynamic damper including the third elastic bodies, and the centrifugal pendulum vibration absorbing device.

Moreover, the torque may be transferred from the second elastic bodies to the output element, and the output element may be used also as the support member of the centrifugal pendulum vibration absorbing device. The entire damper device including the dynamic damper and the centrifugal pendulum vibration absorbing device can thus be made compact.

The damper device may further include: an intermediate element that is coupled to the input element via the first elastic bodies and coupled to the output element via the second elastic bodies, and the third elastic bodies of the dynamic damper may be coupled to the intermediate element. Vibration of the intermediate member that tends to vibrate between the first and second elastic bodies and overall vibration of the damper device can thus be satisfactorily damped (absorbed) by both the dynamic damper and the centrifugal pendulum vibration absorbing device.

Moreover, the third elastic bodies of the dynamic damper may be coupled to the output element. In this configuration as well, overall vibration of the damper device can be satisfactorily damped (absorbed) by both the dynamic damper and the centrifugal pendulum vibration absorbing device.

A distance between an axis of the damper device and an axis of each of the second elastic bodies may be equal to a distance between the axis of the damper device and an axis of each of the third elastic bodies. This can more satisfactorily suppress an increase in outer diameter of the damper device.

Moreover, the axes of the second elastic bodies and the axes of the third elastic bodies may be included in a same plane perpendicular to the axis of the damper device. This can also suppress an increase in axial length of the damper device and therefore can make the entire device more compact.

The dynamic damper may include a coupling member having a fixed portion that is fixed to the mass body and a plurality of elastic body contact portions each extended from the fixed portion so as to contact an end of a corresponding one of the third elastic bodies, and the plane including the axes of the third elastic bodies and perpendicular to the axis of the damper device may be included in a range of a thickness of the elastic body contact portions in the axial direction of the damper device. Since the plane including the axes of the third elastic bodies and perpendicular to the axis of the damper device are included in the range of the thickness of the elastic body contact portions in the axial direction of the damper device, the third elastic bodies can be more appropriately extended and compressed along their axes, and vibration damping capability of the dynamic damper can further be improved.

A starting device described herein is a starting device including any of the above damper devices, a pump impeller, a turbine runner that together with the pump impeller forms a fluid transmission device, and a lockup clutch, wherein the mass body of the dynamic damper includes the turbine runner. This starting device can thus use the turbine runner as the mass body of the dynamic damper. This eliminates the need to separately provide a mass body of the dynamic damper, and can satisfactorily suppress an increase in overall size of the device.

PREFERRED EMBODIMENTS

A preferred embodiment is described below with reference to the accompanying drawings.

FIG. 1is a partial sectional view showing a starting device1including a damper device10according to an embodiment.FIG. 2is a plan view showing a main part of the damper device10. The starting device1shown in these figures is a device to be mounted on a vehicle including an engine (internal combustion engine) serving as a motor, and includes, in addition to the damper device10, a front cover3serving as an input member that is coupled to a crankshaft of the engine, a pump impeller (input-side fluid transmission element)4fixed to the front cover3, a turbine runner (output-side fluid transmission element)5capable of rotating coaxially with the pump impeller4, a damper hub7serving as an output member that is coupled to the damper device10and fixed to an input shaft IS (seeFIG. 3) of a transmission serving as an automatic transmission (AT) or a continuously variable transmission (CVT), a lockup clutch8as a hydraulic single-plate clutch, and a centrifugal pendulum vibration absorbing device20and a dynamic damper30which are coupled to the damper device10.

The pump impeller4has a pump shell40that is firmly fixed to the front cover3, and a plurality of pump blades41disposed on the inner surface of the pump shell40. The turbine runner5has a turbine shell50and a plurality of turbine blades51disposed on the inner surface of the turbine shell50. The turbine shell50is fixed to a turbine hub52via a plurality of rivets. The turbine hub52is rotatably supported by the damper hub7, and movement of the turbine hub52in the axial direction of the starting device1is restricted by a snap ring etc. attached to the damper hub7. The pump impeller4and the turbine runner5face each other, and a stator6that adjusts the flow of hydraulic oil (working fluid) from the turbine runner5to the pump impeller4is coaxially disposed between the pump impeller4and the turbine runner5. The stator6has a plurality of stator blades60, and the rotational direction of the stator6is set to only one direction by a one-way clutch61. The pump impeller4, the turbine runner5, and the stator6form a torus (annular flow path) in which the hydraulic oil is circulated, and function as a torque converter (fluid transmission device) having a torque amplifying function. In the starting device1, the stator6and the one-way clutch61may be omitted, and the pump impeller4and the turbine runner5may function as a fluid coupling.

The lockup clutch8can perform a lockup operation of coupling the front cover3to the damper hub7via the damper device10and can cancel the lockup. The lockup clutch8has a lockup piston80that is disposed in the front cover3at a position near an engine side (the right side in the figure) inner wall surface of the front cover3, and that is axially slidably and rotatably fitted on the damper hub7. As shown inFIG. 1, a friction material81is bonded to an outer peripheral portion of the surface of the lockup piston80which is located on the front cover3side. A lockup chamber85that is connected to a hydraulic control device, not shown, via a hydraulic oil supply hole and an oil passage formed in the input shaft IS is defined between the lockup piston80and the front cover3.

Hydraulic oil supplied from the hydraulic control device to the pump impeller4and the turbine runner5(torus) can flow into the lockup chamber85. Accordingly, when the pressure in a fluid transmission chamber accommodating the pump impeller4and the turbine runner5is kept equal to that in the lockup chamber85, the lockup piston80does not move toward the front cover3and does not frictionally engage with the front cover3. However, if the pressure in the lockup chamber85is reduced by the hydraulic control device, not shown, the lockup piston80moves toward the front cover3due to the pressure difference and frictionally engages with the front cover3. The front cover3is thus coupled to the damper hub7via the damper device10. The lockup clutch8may be configured as a hydraulic multi-plate clutch.

As shown inFIGS. 1 and 2, the damper device10includes as rotary elements a drive member (input element)11, an intermediate member (intermediate element)12, and a driven member (output element)15, and includes as power transmission elements a plurality of (in the present embodiment, four) first springs (first elastic bodies) SP1and a plurality of (in the present embodiment, two) second springs (second elastic bodies) SP2disposed inward of the first springs SP1. The intermediate member12is coupled to the drive member11via the plurality of first springs SP1, and the driven member15is coupled to the intermediate member12via the plurality of second springs SP2. In the present embodiment, the first springs SP1disposed on the outer peripheral side of the damper device10are arc springs each made of a metal material wound so as to have an axis extending in an arc shape when not subjected to a load. This can further reduce rigidity (reduce the spring constant) of the first springs SP1and can further reduce rigidity (implement a longer stroke) of the damper device10. The second springs SP2are coil springs each made of a metal material wound in a helical shape so as to have an axis extending straight when not subjected to a load. The second springs SP2have higher rigidity (spring constant) than the first springs SP1.

The drive member11has a plurality of spring contact portions11aeach contacting one end of a corresponding one of the first springs SP1, and a plurality of spring support portions11b. The drive member11is fixed to the lockup piston80of the lockup clutch8via a plurality of rivets, and is disposed in an outer peripheral region of a housing defined by the front cover3and the pump shell40of the pump impeller4. The intermediate member12includes an annular first plate13disposed on the front cover3(lockup piston80) side, and an annular second plate14disposed on the pump impeller4and turbine runner5side and coupled (fixed) to the first plate13via rivets.

As shown inFIG. 1, the first plate13of the intermediate member12has a plurality of first spring contact portions13aeach contacting the other end of a corresponding one of the first springs SP1, a plurality of second spring contact portions, not shown, each contacting one end of a corresponding one of the second springs SP2, and a plurality of spring support portions13bsupporting the first second springs SP2. In the present embodiment, each of the plurality of first spring contact portions13ais extended outward from an annular inner peripheral portion of the first plate13and is extended in the axial direction of the starting device1toward the front cover3. The second plate14has spring contact portions14a(seeFIG. 2) each contacting one end of a corresponding one of the second springs SP2, and a plurality of spring support portions14bfacing the spring support portions13bof the first plate13and supporting the second springs SP2. The first and second plates13,14hold the plurality of second springs SP2so that the plurality of second springs SP2are separated from the plurality of first springs SP1in the radial and axial directions of the starting device1. That is, in the present embodiment, the plurality of first springs SP1are disposed so as to be shifted from the plurality of inner second springs SP2toward the front cover3in the axial direction of the starting device1(damper device10).

The driven member15has a plate portion150disposed between the first plate13and the second plate14of the intermediate member12, and an inner peripheral portion of the plate portion150is fixed to the damper hub7by welding. The driven member15has a plurality of spring contact portions (output-side contact portions)15a(seeFIG. 2) each contacting the other end of a corresponding one of the second springs SP2. The driven member15further has a plurality of arc-shaped support holes15h(seeFIG. 2), and a roller16, which is rotatably supported by the rivet coupling the first plate13and the second plate14of the intermediate member12, is disposed in each support hole15hin a rollable manner. The intermediate member12(the first plate13and the second plate14) is thus movably supported around the axis of the starting device1and the damper device10by the driven member15via the support holes15hand the rollers16.

The centrifugal pendulum vibration absorbing device20is formed by the driven member15serving as a support member, which is the rotary element of the damper device10, and a plurality of (e.g., three to four) pendulum mass bodies21swingably supported by the driven member15and adjoining each other in the circumferential direction. As shown inFIG. 1, the driven member15is formed in an annular shape so as to extend radially outward from the center side, and a plurality of guide holes15g, which is, e.g., substantially arc-shaped elongated holes, are formed at regular intervals in an outer peripheral portion of the driven member15. Each pendulum mass body21is formed by two metal plates (weights)21aand a support shaft (roller)22that is inserted through the guide hole15gof the driven member15in a rollable manner and that has the metal plates21afixed to both ends thereof. The driven member15is thus used also as a support member of the centrifugal pendulum vibration absorbing device20, and as shown inFIGS. 1 and 2, the pendulum mass bodies21are disposed between the turbine runner5and the first springs SP1of the damper device10at the positions outward of the second springs SP2so as to surround the plurality of second springs SP2.

In the centrifugal pendulum vibration absorbing device20configured as described above, the plurality of pendulum mass bodies21swing in the same direction with respect to the driven member15when the driven member15serving as the support member supporting the pendulum mass bodies21rotates. Vibration having the opposite phase to that of vibration of the driven member15of the damper device10is thus applied to the driven member15. In this manner, the centrifugal pendulum vibration absorbing device20can reduce the overall vibration level of the damper device10. The configuration of the centrifugal pendulum vibration absorbing device20is not limited to that described above, and any configuration may be used. In the present embodiment, the centrifugal pendulum vibration absorbing device20also uses the driven member15as the support member supporting the pendulum mass bodies21, and is therefore coupled to the driven member15of the damper device10. However, the centrifugal pendulum vibration absorbing device20may be provided with a dedicated support member, and this support member may be coupled to the driven member15or the intermediate member12or the drive member11so as to rotate together therewith.

The dynamic damper30includes a plurality of (in the present embodiment, two) third springs (third elastic bodies) SP3and a coupling member31that is coupled to the third springs SP3and that together with the turbine runner5and the turbine hub52forms a mass body (seeFIG. 2). The “dynamic damper” is a mechanism that applies vibration of the opposite phase to a vibrating body at the same frequency (engine speed) as the resonance frequency of the vibrating body to damp vibration, and is formed by coupling the springs and the mass body to the vibrating body so that the springs and the mass body are not included in a torque transmission path. The dynamic damper can be operated at a desired frequency by adjusting the rigidity of the springs and the weight of the mass body.

Arc springs or coil springs are used as the third springs SP3of the dynamic damper30. The plurality of third springs SP3are supported by the coupling member31and disposed one by one between adjoining ones of the second springs SP2so as to lie in the same radial plane of the starting device1and the damper device10. That is, the third springs SP3lie along the same axial position as the second springs SP2as viewed in the radial direction of the starting device1and the damper device10(as viewed in the direction shown by a white arrow inFIG. 1), and do not overlap the second springs SP2as viewed in the axial direction of the starting device1and the damper device10(as viewed in the direction shown by a thick black arrow inFIG. 1). This can suppress an increase in outer diameter of the damper device10as compared to the case where the third springs SP3of the dynamic damper30are disposed radially outward or inward of the second springs SP2or disposed between the first and second springs SP1, SP2in the radial direction.

In the present embodiment, the plurality of second springs SP2and the plurality of third springs SP3are disposed on a concentric circle as shown inFIG. 2, and the distance r2 between the axis of the starting device1and the damper device10and the axis of each second spring SP2is the same as the distance r3 between the axis of the starting device1and the damper device10and the axis of each third spring SP3. This can more satisfactorily suppress an increase in outer diameter of the damper device10. Moreover, in the present embodiment, the second springs SP2and the third springs SP3are disposed so that their axes are included in the same plane PL (seeFIG. 1) perpendicular to the axis of the starting device1and the damper device10. This can also suppress an increase in axial length of the damper device10.

The coupling member31of the dynamic damper30has an annular shape, and an inner peripheral portion (annular fixed portion)31aof the coupling member31together with the turbine shell50is fixed to the turbine hub52(and the turbine runner5) via rivets such that the inner peripheral portion31acontacts the back surface (the front cover3side surface) of an inner peripheral portion of the turbine shell50of the turbine runner5. The coupling member31together with the turbine shell50and the turbine hub52is therefore rotatably supported by the damper hub7. The coupling member31has a plurality of spring support portions31bthat face the spring support portions13bof the first plate13of the intermediate member12and support the second springs SP2. A plurality of spring contact portions (elastic body contact portions serving as engagement portions)31ceach contacting (engaging with) one end of a corresponding one of the third springs SP3are extended outward from the inner peripheral portion31aof the coupling member31toward the front cover3. That is, as shown inFIGS. 1 and 2, each of the plurality of spring contact portions31cis extended from the inner peripheral portion31avia a bent portion31fso as to extend away from the inner peripheral portion31ain the axial direction (extend toward the front cover3) and to extend radially outward. In the present embodiment, as shown inFIG. 2, the coupling member31has, e.g., two pairs of spring contact portions31cdisposed symmetrically with respect to the axis of the starting device1and the damper device10such that each pair of (two) spring contact portions31cface each other at an interval according to the natural length of the third spring SP3.

Moreover, as shown inFIG. 2, the plate portion150of the driven member15has a plurality of (in the present embodiment, two) openings (holes or cutouts)15oformed at regular intervals about the axis of the starting device1and the damper device10. Each pair of spring contact portions31cand the third spring SP3supported by the pair of spring contact portions31care placed in a corresponding one of the openings15o. That is, as shown inFIG. 2, the plurality of spring contact portions31cof the coupling member31are placed pair by pair in the openings15oformed in the plate portion150of the driven member15, and each pair of spring contact portions31csupport the third spring SP3such that the third spring SP3is located next to the second springs SP2in the circumferential direction. The spring contact portions31care thus made to overlap the driven member15in the axial direction (are placed so as to overlap the driven member15as viewed in the radial direction). This can suppress an increase in axial length of the damper device10, and allows the spring contact portions31cof the coupling member31to contact (engage with) the centers (the central portions in the lateral direction, i.e., in the axial direction of the damper device10) of the ends of the third springs SP3. That is, as can be seen fromFIGS. 1 and 2, the plane PL including the axes of the third springs SP3and perpendicular to the axis of the damper device10is included in the range of the thickness of the spring contact portions31cof the coupling member31in the axial direction of the damper device10, and the inner peripheral portion (fixed portion)31aof the coupling member is fixed to the turbine runner5at a position shifted in the axial direction from the plane PL (on the left side inFIG. 1). In other words, the coupling member31is fixed to the turbine runner5serving as the mass body so that end faces (contact surfaces) of the spring contact portions31cwhich contact the third springs SP3cross the plane PL. Like the plurality of second springs SP2, the plurality of third springs are also surrounded by the plurality of pendulum mass bodies21of the centrifugal pendulum vibration absorbing device20which are disposed between the turbine runner5and the first springs SP1of the damper device10at the positions outward of the third springs.

In the present embodiment, as shown inFIG. 2, the second plate14of the intermediate member12has second spring contact portions (second intermediate-side contact portions)14ceach contacting one end of a corresponding one of the third springs SP3, and the first plate13facing the second plate14with the driven member15interposed therebetween has third spring contact portions (first intermediate-side contact portions)13ceach contacting one end of a corresponding one of the third springs SP3. Accordingly, when the engine is rotated and the intermediate member12is rotated by the torque from the engine, each of the third spring contact portions13cof the first plate13and each of the second spring contact portions14cof the second plate14presses the one end of a corresponding one of the third springs SP3, and the other end of each of the third springs SP3presses one spring contact portion31cof a corresponding one of the pairs of spring contact portions31cof the coupling member31. As a result, when the turbine runner5is not involved in power (torque) transmission, the dynamic damper30is formed by the third springs SP3being extended and compressed between the intermediate member12and the coupling member31(turbine runner5), and the dynamic damper30including the plurality of third springs SP3, the turbine runner5serving as the mass body, etc. is coupled to the intermediate member12of the damper device10.

Moreover, since the plate portion150of the driven member15, the spring contact portions31cof the coupling member31, the second springs SP2, and the third springs SP3are disposed as described above, the centerlines in the thickness direction of the spring contact portions15aof the plate portion150and the spring contact portions31cand the axes of the second springs SP2and the third springs SP3are included in the plane PL perpendicular to the axis of the damper device10. The plate portion150(spring contact portion15a) of the driven member15and the spring contact portions31cof the coupling member31are placed between the first plate13and the second plate14of the intermediate member12, and each spring contact portion31cis placed between the spring contact portion13cof the first plate13and the spring contact portion14cof the second plate14which face each other, namely in the middle in the axial direction of the damper device10between the spring contact portion13cand the spring contact portion14cwhich face each other.

Operation of the starting device1configured as described above will be described below with reference toFIG. 3.

When lockup is cancelled by the lockup clutch8of the starting device1, torque (power) from the engine serving as a motor is transferred to the input shaft IS of the transmission through a path of the front cover3, the pump impeller4, the turbine runner5, the coupling member31, the third springs SP3, the intermediate member12, the second springs SP2, the driven member15, and the damper hub7. In the present embodiment, the third springs SP3are disposed so as to overlap the second springs SP2both in the axial and radial directions of the damper device10etc. This can further reduce rigidity (reduce the spring constant) of the first springs SP1disposed outward of the second and third springs SP2, SP3and thus further improve damping capability of the damper device10, and can also ensure a sufficient size (outer diameter) of the second and third springs SP2, SP3and thus satisfactorily maintain rigidity (durability) of the second and third springs SP2, SP3, as compared to the case where the first to third springs SP1, SP2, SP3are disposed next to each other in the radial direction of the damper device10. Accordingly, in the starting device1, torque can be satisfactorily transferred from the front cover3to the input shaft IS of the transmission even if the second springs SP2and the third springs SP3are included in the power transmission path from the front cover3to the input shaft IS of the transmission when the lockup is cancelled.

On the other hand, when a lockup operation is performed by the lockup clutch8of the starting device1, torque (power) from the engine serving as a motor is transferred to the input shaft IS of the transmission device through a path of the front cover3, the lockup clutch8, the drive member11, the first springs SP1, the intermediate member12, the second springs SP2, the driven member15, and the damper hub7, as can be seen fromFIG. 2. At this time, fluctuations in torque applied to the front cover3are damped (absorbed) mainly by the first and second springs SP1, SP2of the damper device10. In this case, since the pump impeller4and the turbine runner5(fluid transmission device) are not involved in the torque transmission between the front cover3and the input shaft IS of the transmission, the dynamic damper30including the plurality of third springs SP3, the turbine runner5serving as the mass body, etc. is coupled to the intermediate member12of the damper device10. Vibration of the intermediate member12that tends to vibrate between the first and second springs SP1, SP2can thus be satisfactorily damped (absorbed) by the dynamic damper30.

Moreover, in the starting device1, when the damper device10coupled to the front cover3by the lockup operation of the lockup clutch8rotates together with the front cover3, the driven member15of the damper device10also rotates about the axis of the starting device1. As the driven member15rotates, the pendulum mass bodies21of the centrifugal pendulum vibration absorbing device20swing in the same direction with respect to the driven member15. Vibration having the opposite phase to vibration (resonance) of the driven member15is thus applied from the centrifugal pendulum vibration absorbing device20to the driven member15, whereby vibration can also be damped (absorbed) between the front cover3and the damper hub7by the centrifugal pendulum vibration absorbing device20.

As described above, the damper device10of the starting device1includes the dynamic damper30that has the third springs SP3coupled to the intermediate member12and that also has, as the mass body coupled to the third springs SP3, the turbine runner5, the coupling member31, and the turbine hub52. The third springs SP3of the dynamic damper30are disposed so as to overlap both in the axial and radial directions of the damper device10the second springs SP2that have higher rigidity than the first springs SP1and that are disposed inward of the first springs SP1to transfer torque between the drive member11and the driven member15. In the damper device10, the plane PL including the axes of the third springs SP3and perpendicular to the axis of the damper device10is included in the range of the thickness in the axial direction of the spring contact portions31cof the coupling member31.

This can suppress an increase in outer diameter of the damper device10and can make the entire device more compact as compared to the case where the third springs SP3of the dynamic damper30are disposed radially outward or inward of the first springs SP1and the second springs SP2or disposed between the first and second springs SP1, SP2in the radial direction. Moreover, since the plane PL including the axes of the third springs SP3and perpendicular to the axis of the damper device10is included in the range of the thickness in the axial direction of the spring contact portions31cof the coupling member31, the third springs SP3can be more appropriately extended and compressed along their axes, and vibration damping capability of the dynamic damper30can further be improved. In addition, in the damper device10, the third springs SP3can be placed without increasing the rigidity of the first springs SP1. Namely, both the second and third springs SP2, SP3can be placed while the low rigidity of the first springs SP1is maintained which particularly affects the damping capability. That is, reducing the rigidity of the first springs SP1can reduce the overall rigidity of the damper device10and can ensure satisfactory damping capability thereof even if the axial length (circumferential length) of the inner second springs SP2is reduced. Accordingly, sufficient space can be secured to place the third springs SP3of the dynamic damper30, and the appropriate third springs SP3according to vibration to be damped can be used. Namely, the damping capability of the dynamic damper can be optimized. As a result, in the damper device10, the overall damping capability of the device can be ensured, and reduction in size of the device can also be implemented.

In the damper device10, the coupling member31has the inner peripheral portion (fixed portion)31athat is fixed to the turbine runner5serving as the mass body at the position shifted in the axial direction from the plane PL including the axes of the third springs SP3and perpendicular to the axis of the damper device10. Each of the plurality of spring contact portions31cis extended from the inner peripheral portion31avia the bent portion31f. The spring contact portions31care thus shifted from the inner peripheral portion31ain the axial direction of the damper device10. Accordingly, even though the third springs SP3of the dynamic damper30are disposed so as to be shifted from the turbine runner5as the mass body in the axial direction of the damper device10, an increase in overall size of the device can be suppressed, and the third springs SP3and the turbine runner5can be fixed with respect to each other.

Moreover, in the damper device10, the driven member15includes the plate portion150having the plurality of spring contact portions (output-side contact portions)15aeach contacting the end of a corresponding one of the second springs SP2. The plurality of spring contact portions31cof the coupling member31are disposed pair by pair in the openings15oformed in the plate portion150of the driven member15, and each pair of spring contact portions31csupport the third spring SP3so that the third spring SP3is located next to the second springs SP2in the circumferential direction. The plate portion150of the driven member15, the spring contact portions31cof the coupling member31, the second springs SP2, and the third springs SP3are disposed so that the centerlines in the thickness direction of the plate portion150(spring contact portions15a) and the spring contact portions31cand the axes of the second springs SP2and the third springs SP3are included in the same plane PL perpendicular to the axis of the damper device10.

Since the spring contact portions31cof the coupling member31are thus disposed in the openings15oformed in the plate portion150of the driven member15, the plate portion150and the spring contact portions31cof the coupling member31are made not to be located next to each other in the axial direction of the damper device10. This can suppress an increase in axial length of the damper device10and can make the entire device compact. In addition, since the centerlines in the thickness direction of the plate portion150(spring contact portions15a) and the spring contact portions31cand the axes of the second and third springs SP2, SP3are included in the same plane PL perpendicular to the axis of the damper device10, the second springs SP2and the third springs SP3can be more appropriately extended and compressed along their axes, and vibration damping capability of the damper device10including the dynamic damper30can further be improved. However, the centerlines in the thickness direction of the spring contact portions15aand the spring contact portions31cand the axes of the second and third springs SP2, SP3are not necessarily completely included in the same plane PL perpendicular to the axis of the damper device10. That is, the plate portion150of the driven member15, the coupling member31, and the second and third springs SP2, SP3need only to be placed so that the plane PL including the axes of the third springs SP3and perpendicular to the axis of the damper device10is included in the range of the thicknesses of the spring contact portions15aof the plate portion150and the spring contact portions31cof the coupling member31in the axial direction of the damper device10.

Moreover, in the damper device10, the intermediate member12includes the first and second plates13,14that are coupled to each other, and the plate portion150of the driven member15and the spring contact portions31cof the coupling member31are disposed between the first plate13and the second plate14. This can suppress an increase in axial length of the damper device10. The first plate13of the intermediate member12has the plurality of spring contact portions (first intermediate-side contact portions)13ceach contacting the end of a corresponding one of the third springs SP3, and the second plate14has the plurality of spring contact portions (second intermediate-side contact portions)14ceach contacting the end of a corresponding one of the third springs SP3. Each spring contact portion31cof the coupling member31is disposed between the spring contact portion13cand the spring contact portion14c. This has an effect similar to the case where the intermediate member is formed by a single plate member and the plane PL including the axes of the third springs SP3and perpendicular to the axis of the damper device10is included in the range of the thickness of contact portions of the intermediate member with the third springs SP3in the axial direction of the damper device10(the intermediate member is made to contact the central portions of the ends of the third springs SP3in the lateral direction, i.e., in the axial direction of the damper device10). As a result, the third springs SP3can be more appropriately extended and compressed along their axes between the intermediate member12(first and second plates13,14) and the coupling member31, and vibration damping capability of the damper device10can further be improved.

An increase in outer diameter of the damper device10can be more satisfactorily suppressed by making the distance r2 between the axis of the damper device10and the axis of each second spring SP2the same as the distance r3 between the axis of the damper device10and the axis of each third spring SP3as in the above embodiment. Moreover, an increase in axial length of the damper device10can also be suppressed because the axes of the second springs SP2and the axes of the third springs SP3are included in the same plane PL perpendicular to the axis of the damper device10in the above embodiment. This can make the entire starting device1more compact.

In the above embodiment, the driven member15of the damper device10together with the plurality of pendulum mass bodies21swingably coupled to the driven member15forms the centrifugal pendulum vibration absorbing device20. The first springs SP1are disposed so as to be shifted from the second springs SP2in the axial direction. The plurality of pendulum mass bodies21of the centrifugal pendulum vibration absorbing device20are disposed outward of the second and third springs SP2, SP3so as to surround the second and third springs SP2, SP3located next to each other in the circumferential direction. Accordingly, an increase in overall size of the damper device10including the centrifugal pendulum vibration absorbing device20can be more satisfactorily suppressed (in particular, an increase in axial length thereof can be suppressed), and vibration can be damped (absorbed) by the first and second springs SP1, SP2, the centrifugal pendulum vibration absorbing device20, and the dynamic damper30including the third spring SP3.

The damper device10includes the intermediate member12that is coupled to the drive member11via the first springs SP1and that is coupled to the driven member15via the second springs SP2. The third springs SP3of the dynamic damper30are coupled to the intermediate member12, and the driven member15is used also as the support member of the centrifugal pendulum vibration absorbing device20. The entire damper device10including the centrifugal pendulum vibration absorbing device20and the dynamic damper30can thus be made compact, and vibration of the intermediate member12that tends to vibrate between the first and second springs SP1, SP2and overall vibration of the damper device10can be satisfactorily damped (absorbed) by both the centrifugal pendulum vibration absorbing device20and the dynamic damper30. Instead of coupling the third springs SP3of the dynamic damper30to the intermediate member12(coupling the coupling member31to the intermediate member12via the third springs SP3), the third springs SP3of the dynamic damper30may be coupled to the driven member15(the coupling member31may be coupled to the driven member15via the third springs SP3), as in a damper device10B of a starting device1B shown inFIG. 4. In this configuration as well, overall vibration of the damper device10B can be satisfactorily damped (absorbed) by both the centrifugal pendulum vibration absorbing device20and the dynamic damper30.

In the starting device1, the dynamic damper30includes the coupling member31that has the inner peripheral portion31afixed to the turbine runner5and the spring contact portions31cserving as the engagement portions (elastic body contact portions) extended outward from the inner peripheral portion31ato contact (engage with) one ends of the third springs SP3. The turbine runner5is rotatably supported by the damper hub7to which the driven member15is fixed, and is coupled to the third springs SP3via the coupling member31. The driven member15has the openings15oin which the spring contact portions31cof the coupling member31and the third springs SP3are disposed. Accordingly, in the starting device1, the turbine runner5can be used as the mass body of the dynamic damper30, and the spring contact portions31cof the coupling member31can be made to contact (engage with) the third springs SP3more appropriately while an increase in axial length is suppressed.

In the above damper devices10,10B, the first springs SP1and the second springs SP2operate in series via the intermediate member12. However, the damper devices10,10B may be configured so that the first springs SP1and the second springs SP2operate in parallel. That is, the damper devices10,10B may be configured either as a series damper device having a drive member, an intermediate member, and a driven member as rotary elements or as a parallel damper device having a drive member, an intermediate member, and a driven member as rotary elements. As described above, the turbine runner5can be used as the mass body of the dynamic damper30by fixing the coupling member31to the turbine runner5. An increase in size of the starting device1can thus be satisfactorily suppressed. However, the dynamic damper30may be configured to include a dedicated mass body other than the turbine runner5. Moreover, in the case where the turbine runner5is not used as the mass body of the dynamic damper30, the turbine runner5may be connected (fixed) to any of the drive member, the intermediate member, and the driven member.

In the preferred embodiment, the damper device10,10B including the drive member11serving as the input element, the driven member15serving as the output element, the first springs SP1serving as the first elastic bodies that transfer torque between the drive member11and the driven member15, and the second springs SP2serving as the second elastic bodies that are disposed inward of the first springs SP1to transfer torque between the drive member11and the driven member15corresponds to the “damper device.” The dynamic damper30having the third springs SP3serving as the third elastic bodies coupled to the intermediate member12of the damper device10,10B, the turbine runner5serving as the mass body coupled to the third springs SP3, etc. corresponds to the “dynamic damper.” The centrifugal pendulum vibration absorbing device20having the driven member15serving as the support member and the plurality of pendulum mass bodies21swingably coupled to the driven member15corresponds to the centrifugal pendulum vibration absorbing device.” The coupling member31having the inner peripheral portion31afixed to the turbine runner5and the spring contact portions31cserving as the elastic body contact portions extended outward from the inner peripheral portion31ato engage with one ends of the third springs SP3corresponds to the “coupling member.”

Although a preferred embodiment is described above, it should be understood that t various modifications can be made.

INDUSTRIAL APPLICABILITY

The subject matter described herein is applicable to the manufacturing industry of damper devices and starting devices including the same, etc.