JP5531728B2 - Fluid transmission device - Google Patents

Fluid transmission device Download PDF

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Publication number
JP5531728B2
JP5531728B2 JP2010082317A JP2010082317A JP5531728B2 JP 5531728 B2 JP5531728 B2 JP 5531728B2 JP 2010082317 A JP2010082317 A JP 2010082317A JP 2010082317 A JP2010082317 A JP 2010082317A JP 5531728 B2 JP5531728 B2 JP 5531728B2
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input
damper
output
turbine
turbine runner
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JP2011214635A (en
Inventor
一能 伊藤
章裕 長江
義英 森
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アイシン・エィ・ダブリュ株式会社
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/021Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type three chamber system, i.e. comprising a separated, closed chamber specially adapted for actuating a lock-up clutch
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0226Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers
    • F16H2045/0231Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means comprising two or more vibration dampers arranged in series
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0221Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means
    • F16H2045/0247Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type with damping means having a turbine with hydrodynamic damping means
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H45/00Combinations of fluid gearings for conveying rotary motion with couplings or clutches
    • F16H45/02Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type
    • F16H2045/0273Combinations of fluid gearings for conveying rotary motion with couplings or clutches with mechanical clutches for bridging a fluid gearing of the hydrokinetic type characterised by the type of the friction surface of the lock-up clutch
    • F16H2045/0284Multiple disk type lock-up clutch

Description

  The present invention includes a pump impeller connected to an input member connected to a prime mover, a turbine runner rotatable coaxially with the pump impeller, a damper mechanism connected to an output member connected to an input shaft of the transmission, The present invention relates to a fluid transmission device including a lock-up clutch capable of engaging an input member and an input element of a damper mechanism and releasing the engagement therebetween.

  Conventionally, a torque converter including a direct coupling clutch having a damper mechanism including a drive plate, an outer damper spring, an intermediate plate, and a driven plate is known as a fluid transmission device of this type (see, for example, Patent Document 1). In this torque converter, an existing member is connected by connecting a turbine of a torque converter that does not contribute to torque transmission when the direct coupling clutch is in an operating state to a member that contributes to torque transmission via an inner damper spring that is an elastic body. Dynamic damper function using is added.

JP-A-10-169756

  However, if an elastic body constituting the dynamic damper as in the above-described conventional example is provided for the fluid transmission device, the number of parts increases by that amount, resulting in an increase in cost and a reduction in the overall size of the device. It becomes difficult.

  Accordingly, the main object of the present invention is to provide a fluid transmission device with a dynamic damper function while suppressing an increase in cost and an increase in the size of the device.

  The fluid transmission device according to the present invention adopts the following means in order to achieve the above-mentioned main object.

A fluid transmission device according to the present invention comprises:
An input member coupled to the prime mover, an output member coupled to the input shaft of the transmission, a pump impeller connected to the input member, a turbine runner rotatable coaxially with the pump impeller, and the output member In a fluid transmission device comprising: a connected damper mechanism; and a lock-up clutch capable of engaging the input member and an input element of the damper mechanism and releasing the engagement between the two.
An elastic body disposed between the turbine runner and the first element which is one of a plurality of elements constituting the damper mechanism;
The turbine runner is disposed between the turbine runner and a second element other than the first element among the plurality of elements constituting the damper mechanism so that the turbine runner and the second element rotate together. An engagement mechanism that can be engaged;
It is characterized by providing.

  In this fluid transmission device, an elastic body is disposed between the turbine runner and the first element which is one of a plurality of elements constituting the damper mechanism so as to come into contact with both. Therefore, when the input member and the input element of the damper mechanism are engaged by the lock-up clutch, the elastic body is dynamic together with the turbine runner that serves as a mass that does not contribute to torque transmission between the input member and the output member. The damper is configured, and the vibration generated between the input member and the first element can be attenuated by the dynamic damper thus configured, and the transmission of the vibration from the first element to the output member can be suppressed. The fluid transmission device is configured to rotate the turbine runner and the second element integrally between the turbine runner and the second element other than the first element among the plurality of elements constituting the damper mechanism. An engagement mechanism that can be combined is arranged, and when the turbine runner and the second element are engaged by the engagement mechanism and rotated together, the elastic body between the turbine runner and the first element is input. It functions as a damper that absorbs torque between the member and the output member. Thus, in this fluid transmission device, the elastic body between the turbine runner and the first element can be used as an elastic body for the dynamic damper and an elastic body that absorbs excessive torque input from the prime mover to the input member. Therefore, it is not necessary to provide a dedicated elastic body for the damper mechanism that absorbs excessive torque input from the prime mover to the input member. As a result, it is possible to provide a dynamic damper function to the fluid transmission device while suppressing an increase in cost due to an increase in the number of parts and an increase in the size of the device. In addition, when the 1st element and 2nd element which comprise a damper mechanism consist of a several member, an elastic body is provided between any one of the several member which comprises a turbine runner and a 1st element. The engagement mechanism may be disposed between the turbine runner and any one of the plurality of members constituting the second element.

  The damper mechanism may include the input element and an output element connected to the output member, and the first element is one of the input element and the output element of the damper mechanism, The second element may be the other of the input element and the output element of the damper mechanism.

  Furthermore, the damper mechanism may include the input element, the intermediate element, and an output element connected to the output member, and the first element is one of the input element and the output element of the damper mechanism. The second element may be the other of the input element and the output element of the damper mechanism.

  The damper mechanism may include the input element, an intermediate element, and an output element connected to the output member, and the first element is the intermediate element of the damper mechanism, and the second element The element may be one of the input element and the output element of the damper mechanism.

  Furthermore, the engagement mechanism may engage the turbine runner and the second element when an excessive torque exceeding an allowable input torque of the damper mechanism is input to the input member.

  The fluid transmission device may further include a stator that rectifies the flow of the working fluid from the turbine runner to the pump impeller, and the pump impeller, the turbine runner, and the stator have a torque amplification function. A torque converter may be configured. The pump impeller and the turbine runner may constitute a fluid coupling that does not have a torque amplification function.

It is sectional drawing which shows the fluid transmission apparatus 1 which concerns on the Example of this invention. 2 is a cross-sectional view showing a main part of the fluid transmission device 1. FIG. 3 is a schematic configuration diagram for explaining the operation of the fluid transmission device 1. FIG. 3 is a schematic configuration diagram for explaining the operation of the fluid transmission device 1. It is a schematic block diagram which shows the fluid transmission apparatus 1B which concerns on a modification. It is a schematic block diagram which shows 1 C of fluid transmission apparatuses which concern on a modification. It is a schematic block diagram which shows fluid transmission apparatus 1D which concerns on a modification. It is a schematic block diagram which shows the fluid transmission apparatus 1E which concerns on a modification. It is a schematic block diagram which shows the fluid transmission apparatus 1F which concerns on a modification.

  Next, the form for implementing this invention is demonstrated using an Example.

  FIG. 1 is a cross-sectional view showing a fluid transmission device 1 according to an embodiment of the present invention. A fluid transmission device 1 shown in the figure is a torque converter mounted as a starting device in a vehicle equipped with an engine as a prime mover, and an input side center piece (input member) 2 connected to a crankshaft of an engine (not shown) The front cover 3 fixed to the input side center piece 2, the pump impeller (input side fluid transmission element) 4 fixed to the front cover 3, and the turbine runner (output side fluid transmission) rotatable coaxially with the pump impeller 4 Element) 5, a stator 6 that rectifies the flow of hydraulic oil (working fluid) from the turbine runner 5 to the pump impeller 4, and an automatic transmission (AT) or a continuously variable transmission (CVT) (not shown). A damper hub (output member) 7 fixed to the input shaft IS, a damper mechanism 8 connected to the damper hub 7, and an input side And a centers piece 2 and the damper mechanism 8 and the lock-up clutch 9 of the multi-plate friction type capable of releasing both of the engagement (coupling) with the engaged (coupling).

  The pump impeller 4 includes a pump shell 40 that is tightly fixed to the front cover 3, and a plurality of pump blades 41 that are disposed on the inner surface of the pump shell 40. The turbine runner 5 has a turbine shell 50 fixed to the turbine hub and a plurality of turbine blades 51 disposed on the inner surface of the turbine shell 50, and the turbine shell 50 (turbine hub) is rotatable by the damper hub 7. Supported. The pump impeller 4 and the turbine runner 5 face each other, and a stator 6 that can rotate coaxially with the pump impeller 4 and the turbine runner 5 is disposed between the pump impeller 4 and the turbine runner 5. The stator 6 has a plurality of stator blades 60, and the rotation direction of the stator 6 is set in only one direction by the one-way clutch 61. The pump impeller 4, the turbine runner 5, and the stator 6 form a torus (annular flow path) for circulating hydraulic oil.

  The damper mechanism 8 can be disposed in the outer peripheral region in the oil chamber defined by the front cover 3 and the pump shell 40 of the pump impeller 4 and can be integrated with the input side center piece 2 in the rotational direction by the lockup clutch 9. An input element (drive element) 81; an output element (driven element) 82 that is disposed in an inner peripheral region of the oil chamber and is fixed to the damper hub 7 and rotatably supports the input element 81; and a plurality of first elements An annular intermediate element (intermediate plate) that engages with the input element 81 via a coil spring (first elastic member) 83 and engages with the output element 82 via a plurality of second coil springs (second elastic members) 84 85).

  As shown in FIG. 1, the input element 81 is disposed on the annular first input plate (drive plate) 811 disposed on the front cover 3 side (engine side) and on the pump shell 40 side (transmission device side). And an annular second input plate (drive plate) 812. The first input plate 811 has a plurality of spring accommodating portions that extend in the circumferential direction and accommodate the first coil springs 83 on the outer peripheral side, and has a plurality of splines that extend in the axial direction on the inner peripheral portion. In addition, an abutting portion (see a broken line in FIG. 1) that abuts against one end of the corresponding first coil spring 83 is formed at one end of each spring accommodating portion. The second input plate 812 is connected (fixed) to the first input plate 811 via a plurality of rivets (see FIG. 1), and the intermediate element 85 is interposed between the first input plate 811 and the second input plate 812. The outer peripheral part of is arranged so as to be rotatable around the axis. The second input plate 812 supports the first coil spring 83 housed in each spring housing portion of the first input plate 811 from the inside.

  The output element 82 includes an annular first output plate (driven plate) 821 disposed on the front cover 3 side (engine side) and an annular second output plate 822 disposed on the pump shell 40 side (transmission device side). Including. The first output plate 821 has a plurality of spring support portions that extend in the circumferential direction, and the second output plate 822 has a plurality of spring support portions that face the corresponding spring support portions of the first output plate 821, respectively. Have Each second coil spring 84 is held by a spring support portion of the first output plate 821 and a corresponding spring support portion of the second output plate 822, and one end of each second coil spring 84 has first and second ends. It abuts against a contact portion (not shown) formed on at least one of the output plates 821 and 822. And between the 1st output plate 821 and the 2nd output plate 822, the inner peripheral part of the intermediate element 85 is rotatably arrange | positioned around an axis | shaft, The inner peripheral part of the 1st and 2nd output plates 821 and 822 Are fixed to the damper hub 7 via rivets. The intermediate element 85 has a plurality of outer peripheral engaging portions that respectively contact the other ends of the corresponding first coil springs 83 held by the first and second input plates 811 and 812, and the first and second outputs. It has a plurality of inner peripheral side engaging portions that respectively contact the other ends of the corresponding second coil springs 84 held by the plates 821 and 822.

  As shown in FIG. 1, the lockup clutch 9 is disposed inside the input element 81 and between the front cover 3 and the output element 82. The lock-up clutch 9 is supported by the input-side center piece 2 so as to be slidable in the axial direction. The lock-up clutch 9 faces the lock-up piston 90 and cannot move in the axial direction. A clutch hub 91 that is supported by the clutch, a return spring 92 that is disposed between the lock-up piston 90 and the clutch hub 91, and the input element 81 that is positioned between the lock-up piston 90 and the clutch hub 91. A plurality of first clutch plates 93 that are slidably supported in the axial direction by a single input plate 811 via a plurality of splines, and adjacent to the first clutch plate 93 between the lock-up piston 90 and the clutch hub 91 In this way, the clutch hub 91 can freely slide in the axial direction via a plurality of splines. And a plurality of second clutch plates 94 to be supported.

  The lock-up piston 90 is disposed close to the radially extending portion of the input side center piece 2 and the front cover 3, and between the back surface of the lock-up piston 90 and the input side center piece 2 and the front cover 3, A lockup chamber 95 is defined which is connected to a hydraulic control unit (not shown) through a hydraulic oil supply hole formed in the input side center piece 2 and an oil passage formed in the input shaft IS. Accordingly, when hydraulic oil (lock-up pressure) is supplied into the lock-up chamber 95 from a hydraulic control unit (not shown) through the hydraulic oil supply hole or the like, the lock-up piston 90 moves toward the clutch hub 91 and is locked. The first and second clutch plates 93 and 94 are sandwiched between the up piston 90 and the clutch hub 91, whereby the input side center piece 2 is connected to the damper hub 7 via the damper mechanism 8. It is transmitted to the input shaft IS of the transmission via the input side center piece 2, the damper mechanism 8 and the damper hub 7. If the introduction of the hydraulic oil into the lockup chamber 95 is stopped, the hydraulic oil in the lockup chamber 95 flows out from the hydraulic oil discharge hole formed in the input side center piece 2 to the oil passage of the input shaft IS. As a result, the lockup is released.

  Here, in the fluid transmission device 1 of the embodiment, as shown in FIG. 1, the turbine runner 5 and the input element 81 (first element) among the plurality of elements constituting the damper mechanism 8 are respectively applied to both. A plurality of third coil springs 86 (elastic bodies) are arranged so as to be in contact with each other, exceeding the range of torque (torque fluctuation) normally generated from the engine as the prime mover and exceeding the allowable input torque of the damper mechanism 8. An output element 82 other than the input element 81 (first element) among the plurality of elements constituting the turbine runner 5 and the damper mechanism 8 when an excessive torque of a predetermined value or more is input to the input side center piece 2 as an input member. The (second element) is configured to rotate integrally. That is, the input element 81 is arranged on the pump shell 40 side (transmission side) with respect to the second input plate 812 in addition to the first input plate 811 and the second input plate 812 described above, and via the rivet described above. A third input plate 813 connected (fixed) to the first and second input plates 811 and 812. The third input plate 813 includes a plurality of spring support portions that extend in the circumferential direction and support the third coil spring 86, and one end of the corresponding third coil spring 86 provided at one end of each spring support portion. A plurality of third coil springs 86 are held together with the second input plate 812. Further, the turbine shell 50 of the turbine runner 5 has an annular shape having a plurality of outer peripheral engagement portions that respectively contact the other ends of the corresponding third coil springs 86 held by the second and third input plates 812 and 813. The turbine connecting member 87 is fixed. The turbine connecting member 87 is engageable with the second output plate 822 constituting the output element 82 via the engagement mechanism 88 on the inner peripheral side thereof.

  As shown in FIG. 2, the engagement mechanism 88 is disposed on the inner peripheral portion of the turbine connecting member 87 at equal intervals and has a plurality of radial protrusions 871 extending inward in the radial direction, and the second output plate 822. Are arranged at equal intervals on the outer peripheral portion of the turbine connecting member 87 and extend in the axial direction and on the pump shell 40 side (transmission side) so as to be engageable with the radial protruding piece 871 of the turbine connecting member 87. (The same number as the pieces 871)) axial protrusion pieces 822a. Each axial protruding piece 822a of the second output plate 822 has a circumferential length shorter than the interval between adjacent radial protruding pieces 871 of the turbine connecting member 87, and as shown in FIG. Between the adjacent radial protrusions 871. Thereby, the turbine connecting member 87 (the turbine runner 5) and the second output plate 822 (the output element 82) are engaged with play. In the embodiment, the torque on the input side center piece 2 does not exceed the range of torque (torque fluctuation) normally generated from the engine as the prime mover in the input side center piece 2 and is not more than the allowable input torque of the damper mechanism 8. 2, as shown in FIG. 2, the radial protruding pieces 871 of the turbine connecting member 87 do not come into contact with any of the axial protruding pieces 822 a on both sides, and the axial protruding pieces 822 a on the upstream side in the rotational direction. The number of radial protrusions 871 and axial protrusions 822a, the interval between adjacent radial protrusions 871, and the interval between adjacent axial protrusions 822a are determined. That is, when the excessive torque as described above is not input to the input side center piece 2 from the engine, the engagement mechanism 88 basically has the turbine connecting member 87 (turbine runner 5) and the second output plate 822 (output element 82). Is not engaged.

  On the other hand, when the excessive torque as described above is input to the input side center piece 2 from the engine as the prime mover, the input impeller 81 and the plurality of third coil springs 86 or the pump impeller 4 and the turbine When a large torque is input to the turbine connecting member 87 via the runner 5, the rotational speed of the turbine connecting member 87 is higher than the rotational speed of the second output plate 822, so that the turbine connecting member 87 moves relative to the second output plate 822. , The radial projecting piece 871 of the turbine connecting member 87 comes into contact with the axial projecting piece 822a on the downstream side in the rotation direction, whereby the turbine connecting member 87 and the second output plate 822, that is, the output element 82 rotate integrally. . That is, the engagement mechanism 88 causes the turbine connecting member 87 (the turbine runner 5) and the second output plate 822 (the output element 82) to move when the excessive torque as described above is input to the input side center piece 2 from the engine. Engage. The angle α that defines the distance between the radial protrusion 871 and the axial protrusion 822a on the downstream side in the rotation direction is the rigidity (spring constant) of the third coil spring 86 and the input of torque to the input side center piece 2. It is determined through experiments and analysis so that the radial protrusion 871 and the axial protrusion 822a on the downstream side in the rotation direction come into contact with each other at an appropriate timing based on the state. The angle β that defines the interval with the direction protrusion 822a is determined through experiments and analysis so that the radial protrusion 871 and the axial protrusion 822a on the upstream side in the rotational direction do not contact each other as much as possible due to normal explosion vibration of the engine. It is done.

  Next, the operation of the above-described fluid transmission device 1 will be described with reference to FIGS. 3 and 4. In the fluid transmission device 1, when the lockup clutch 9 does not engage the input side centerpiece 2 and the input element 81 of the damper mechanism 8, the power from the engine as the prime mover is as shown in FIG. Input side center piece 2, pump impeller 4, turbine runner 5, turbine connecting member 87, multiple third coil springs 86, input element 81, multiple first coil springs 83, intermediate element 85, and multiple second coil springs 84. The output element 82 and the damper hub 7 are transmitted to the input shaft IS of the transmission. At this time, the fluctuation of the torque input to the input side center piece 2 is mainly absorbed by the first and second coil springs 83 and 84 of the damper mechanism 8.

  When the lockup clutch 9 engages the input side center piece 2 and the input element 81 of the damper mechanism 8, the power from the engine as the prime mover is supplied by the input side centerpiece as shown in FIG. Via the path of the piece 2, the lockup clutch 9, the input element 81, the plurality of first coil springs 83, the intermediate element 85, the plurality of second coil springs 84, the output element 82, and the damper hub 7, to the input shaft IS of the transmission. Communicated. At this time, the fluctuation of the torque input to the input side center piece 2 is mainly absorbed by the first and second coil springs 83 and 84 of the damper mechanism 8. In the fluid transmission device 1 of the embodiment, the turbine runner 5, that is, the turbine connecting member 87 fixed to the turbine runner 5, includes the input element 81 and the plurality of third coil springs 86 among the plurality of elements constituting the damper mechanism 8. Since the plurality of third coil springs 86, which are elastic bodies, are engaged with each other through the shaft, the torque between the input side center piece (input member) 2 and the damper hub (output member) 7 when the lockup is on. A dynamic damper is configured together with the turbine runner 5 and the turbine connecting member 87 which are masses that do not contribute to transmission.

  As a result, in the fluid transmission device 1 of the embodiment, vibration generated between the input side center piece 2 and the input element 81 as the first element at the time of lock-up on is generated by the plurality of third coil springs 86 and the turbine runner as a mass. It is possible to suppress the transmission of vibration from the input element 81 to the damper hub 7 as an output member. That is, in the fluid transmission device 1 of the embodiment, the resonance frequency of the dynamic damper constituted by the plurality of third coil springs 86 and the turbine runner 5 and the turbine connecting member 87 as masses, that is, the rigidity of the third coil springs 86 ( The spring constant) and the weight (inertia) of the turbine runner 5 and the turbine connecting member 87 are adjusted based on the number of cylinders of the engine and the engine speed at the time of lock-up execution, so that the engine speed is relatively low. The vibration transmitted from the engine to the fluid transmission device 1, that is, the input side center piece 2 is effectively absorbed (damped) by the dynamic damper, and the vibration is effectively suppressed from being transmitted to the downstream side of the input element 81. It becomes possible to do. Therefore, in the fluid transmission device 1 of the embodiment, lockup is executed at a relatively low stage, for example, about 1000 rpm, to improve power transmission efficiency, and at the time of engagement of the lockup clutch 9 or after engagement. It is possible to satisfactorily attenuate vibrations that tend to occur when the rotational speed of the input side center piece 2 is relatively low.

  In the fluid transmission device 1, when an excessive torque as described above is input from the engine to the input side center piece 2, the turbine runner 5, that is, the turbine connecting member 87 fixed to the turbine runner 5 and the first element The plurality of third coil springs 86 between the input elements 81 function as dampers that absorb torque based on the excessive torque (the excessive torque itself or a large torque resulting from the excessive torque). That is, when an excessive torque is input from the engine to the input side center piece 2 at the time of lock-up off, a large torque resulting from the excessive torque is transmitted to the turbine runner 5, whereby the turbine connecting member 87 outputs the second output. When the radial protruding piece 871 of the turbine connecting member 87 contacts the axial protruding piece 822a on the downstream side in the rotation direction by rotating with respect to the plate 822, the turbine connecting member 87 and the second output plate 822, that is, the output element 82 are moved. It will rotate together. As a result, the turbine connecting member 87 fixed to the turbine runner 5 is substantially connected to the output element 82 of the damper mechanism 8 via the engaging mechanism 88 as shown by a dotted line in FIG. The three-coil spring 86, the input element 81, the plurality of first coil springs 83, the intermediate element 85, and the plurality of second coil springs 84 are substantially connected to the output element 82 of the damper mechanism 8. Therefore, by setting the rigidity (spring constant) of the third coil spring 86 to be higher than the rigidity (spring constant) of the first coil spring 83 and the second coil spring 84, the input side centerpiece can be used at the time of lock-up off. When excessive torque is input to the engine 2 from the engine 2, the third coil spring 86 can function as a damper that absorbs large torque resulting from the excessive torque.

  Further, when the excessive torque as described above is input from the engine to the input side center piece 2 when the lockup is turned on, when the excessive torque is input to the input element 81 of the damper mechanism 8, the plurality of third coils The turbine connecting member 87 engaged with the input element 81 via the spring 86 rotates with respect to the second output plate 822, so that the radial protruding piece 871 of the turbine connecting member 87 is the axial protruding piece 822a on the downstream side in the rotation direction. Then, the turbine connecting member 87 and the second output plate 822, that is, the output element 82 rotate integrally. As a result, the input element 81 of the damper mechanism 8 is substantially connected to the output element 82 via the plurality of first coil springs 83, the intermediate elements 85, and the plurality of second coil springs 84, and in FIG. As shown in FIG. 6, the output element 82 is substantially connected through the plurality of third coil springs 86 and the turbine connecting member 87. Therefore, by setting the rigidity (spring constant) of the third coil spring 86 higher than the rigidity (spring constant) of the first coil spring 83 and the second coil spring 84, the input side centerpiece can be used when the lockup is on. Even when an excessive torque is input to the engine 2, the third coil spring 86 can function as a damper that absorbs the excessive torque.

  As described above, the rigidity, that is, the spring constant of the third coil spring 86 that functions as both the dynamic damper and the excessive torque absorbing damper is preferably determined by giving priority to the torque absorption characteristic based on the excessive torque. The vibration damping characteristics of the dynamic damper constituted by the spring 86, the turbine runner 5, and the turbine connecting member 87 are preferably adjusted by the mass of the turbine connecting member 87 and the mass of the weight attached to the turbine runner 5 or the turbine connecting member 87. .

  As described above, in the fluid transmission device 1, the turbine runner 5, that is, the turbine connecting member 87 fixed to the turbine runner 5 and the input as the first element which is one of a plurality of elements constituting the damper mechanism 8. A plurality of third coil springs 86 are disposed between the element 81 and the element 81 so as to contact each other. Accordingly, when the lockup clutch 9 engages the input side centerpiece 2 as the input member and the input element 81 of the damper mechanism 8 by the lockup clutch 9, the gap between the input element 81 and the turbine runner 5, that is, the turbine connecting member 87 is set. The plurality of third coil springs 86 constitute a dynamic damper together with the turbine runner 5 and the turbine connecting member 87 that serve as masses that do not contribute to torque transmission between the input side center piece 2 and the damper hub 7 as the output member. The dynamic damper configured in this way attenuates vibration generated between the input side center piece 2 and the input element 81 as the first element, and suppresses transmission of vibration from the input element 81 to the damper hub 7 as the output member. it can. That is, by adjusting the resonance frequency of the dynamic damper constituted by the plurality of third coil springs 86 and the turbine runner 5 and the turbine connecting member 87 as masses, the engine as a prime mover when the engine speed is relatively low Is effectively absorbed (damped) by the dynamic damper so that the vibration is effectively prevented from being transmitted to the downstream side of the input element 81. It becomes possible to do.

  The fluid transmission device 1 includes the turbine runner 5 and the output element 82 (second element) other than the input element 81 (first element) among the plurality of elements constituting the damper mechanism 8. An engagement mechanism 88 that can be engaged with the output element 82 so as to rotate integrally is disposed. When the turbine runner 5 and the output element 82 are engaged by the engagement mechanism 88 and rotated integrally, The plurality of third coil springs 86 between the turbine runner 5 and the input element 81 function as dampers that absorb torque between the input side center piece 2 and the damper hub 7. Accordingly, in the fluid transmission device 1, the plurality of third coil springs 86 between the turbine runner 5 and the input element 81 are excessively input to the input side center piece 2 from the elastic body for the dynamic damper and the engine as the prime mover. Therefore, it is not necessary to provide a dedicated elastic body for absorbing excessive torque input from the engine to the input member for the damper mechanism. As a result, it is possible to give the fluid transmission device 1 a dynamic damper function while suppressing an increase in cost due to an increase in the number of parts and an increase in the size of the device.

  Further, in the fluid transmission device 1 according to the embodiment, the turbine connecting member 87 fixed to the turbine runner 5 is a lockup-on among a plurality of elements constituting the damper mechanism 8, and the rotational speed of the input side centerpiece 2 is particularly high. When the (engine speed) is relatively low, the input element 81 having a larger vibration energy than the intermediate element 85 and the output element 82 is engaged with the plurality of third coil springs 86 (elastic body), The vibration is absorbed by the dynamic damper on the upstream side of the power transmission path from the input side center piece 2 to the transmission device to which power is transmitted. Thus, when the lockup is on, the vibration transmitted from the engine as the prime mover to the fluid transmission device 1, that is, the input side center piece 2, is damped before being attenuated by the element downstream of the input element 81 of the damper mechanism 8. It is possible to satisfactorily suppress the vibration from being effectively absorbed (damped) by the damper and transmitted to the downstream side of the input element 81.

  FIG. 5 is a schematic configuration diagram illustrating a fluid transmission device 1B according to a modification. The fluid transmission device 1B shown in FIG. 1 abuts both between a turbine connecting member 87B fixed to the turbine runner 5 and an output element 82B (first element) among a plurality of elements constituting the damper mechanism 8B. Other than the plurality of third coil springs 86 (elastic body), the turbine connecting member 87B fixed to the turbine runner 5 and the output element 82B (first element) among the plurality of elements constituting the damper mechanism 8B The turbine connecting member 87B and the input element 81B can be engaged with each other so that the turbine runner 5 and the input element 81B rotate integrally with each other. And a combination mechanism 88B.

  In the fluid transmission device 1B configured as described above, when the lockup clutch 9 engages the input side center piece 2 as the input member and the input element 81B of the damper mechanism 8B by the lockup clutch 9, the output element 82B and the turbine A plurality of third coil springs 86 between the connecting member 87B and the turbine runner 5 and the turbine connecting member 87B that serve as masses that do not contribute to torque transmission between the input side center piece 2 and the damper hub 7 serving as the output member are dynamic. A damper is configured, and the vibration generated between the input side center piece 2 and the output element 82B as the first element is damped by the dynamic damper thus configured, and the vibration is transmitted from the output element 82B to the damper hub 7 as the output member. Can be suppressed. In the hydraulic power transmission device 1B, the turbine coupling member 87B and the input element 81B are engaged by the engagement mechanism 88B when the excessive torque as described above is input to the input side center piece 2 from the engine as the prime mover. When the turbine runner 5 and the input element 81B rotate together, the plurality of third coil springs 86 between the turbine runner 5 and the output element 82B generate torque between the input side center piece 2 and the damper hub 7. Functions as a damper to absorb. Thereby, also in the fluid transmission device 1B, when an excessive torque is input to the input side center piece 2 from the engine as a prime mover, a dedicated elastic body (coil spring) that absorbs the torque based on the excessive torque is provided with the damper mechanism 8B. It is not necessary to provide for As a result, it is possible to provide a dynamic damper function to the fluid transmission device 1B while suppressing an increase in cost due to an increase in the number of parts and an increase in the size of the device.

  FIG. 6 is a schematic configuration diagram showing a fluid transmission device 1C according to a modification. The fluid transmission device 1 </ b> C shown in FIG. 1 abuts between a turbine connecting member 87 </ b> C fixed to the turbine runner 5 and an intermediate element 85 </ b> C (first element) among a plurality of elements constituting the damper mechanism 8 </ b> C. Other than the plurality of third coil springs 86 (elastic body), the turbine connecting member 87C fixed to the turbine runner 5 and the intermediate element 85C (first element) among the plurality of elements constituting the damper mechanism 8C The turbine connecting member 87C and the output element 82C can be engaged with each other so that the turbine runner 5 and the output element 82C rotate integrally with each other. And a combination mechanism 88C.

  In the fluid transmission device 1 </ b> C configured as described above, the intermediate element 85 </ b> C and the turbine are in a lockup-on state where the input side centerpiece 2 as the input member and the input element 81 </ b> C of the damper mechanism 8 </ b> C are engaged by the lockup clutch 9. A plurality of third coil springs 86 between the connecting member 87C and the turbine runner 5 and the turbine connecting member 87C that serve as masses that do not contribute to torque transmission between the input side center piece 2 and the damper hub 7 as the output member are dynamic. A damper is configured, and the vibration generated between the input side center piece 2 and the intermediate element 85C as the first element is damped by the dynamic damper thus configured, and the vibration is transmitted from the intermediate element 85C to the damper hub 7 as the output member. Can be suppressed. In the hydraulic power transmission device 1C, the turbine coupling member 87C and the output element 82C are engaged by the engagement mechanism 88C when the excessive torque as described above is input to the input side center piece 2 from the engine as the prime mover. When the turbine runner 5 and the output element 82C rotate together, the plurality of third coil springs 86 between the turbine runner 5 and the intermediate element 85C generate torque between the input side center piece 2 and the damper hub 7. Functions as a damper to absorb. Thereby, also in the fluid transmission device 1C, when an excessive torque is input to the input side center piece 2 from the engine as a prime mover, a dedicated elastic body (coil spring) that absorbs the torque based on the excessive torque is used as the damper mechanism 8C. It is not necessary to provide for As a result, it is possible to provide a dynamic damper function to the fluid transmission device 1C while suppressing an increase in cost due to an increase in the number of parts and an increase in the size of the device.

  FIG. 7 is a schematic configuration diagram showing a fluid transmission device 1D according to a modification. The fluid transmission device 1D shown in the figure is disposed between a turbine connecting member 87D fixed to the turbine runner 5 and an intermediate element 85D among a plurality of elements constituting the damper mechanism 8D so as to abut both of them. A plurality of third coil springs 86 (elastic body), a turbine connecting member 87D fixed to the turbine runner 5, and an input element 81D (other than an intermediate element 85D (first element) among a plurality of elements constituting the damper mechanism 8D) An engaging mechanism 88D that is disposed between the turbine connecting member 87D and the input element 81D so that the turbine runner 5 and the input element 81D rotate integrally. Prepare.

  In the fluid transmission device 1 </ b> D configured as described above, the intermediate element 85 </ b> D and the turbine are in the lockup-on state where the input side centerpiece 2 as the input member and the input element 81 </ b> D of the damper mechanism 8 </ b> D are engaged by the lockup clutch 9. A plurality of third coil springs 86 between the connecting member 87D and the turbine runner 5 and the turbine connecting member 87D that serve as masses that do not contribute to torque transmission between the input side center piece 2 and the damper hub 7 as the output member are dynamic. The damper is configured, and the vibration generated between the input side center piece 2 and the intermediate element 85D as the first element is attenuated by the dynamic damper thus configured, and the vibration is transmitted from the intermediate element 85D to the damper hub 7 as the output member. Can be suppressed. In the fluid transmission device 1D, the turbine coupling member 87D and the input element 81D are engaged by the engagement mechanism 88D when the excessive torque as described above is input to the input side center piece 2 from the engine as the prime mover. When the turbine runner 5 and the input element 81D rotate together, the plurality of third coil springs 86 between the turbine runner 5 and the intermediate element 85C generate torque between the input side center piece 2 and the damper hub 7. Functions as a damper to absorb. Thereby, also in the fluid transmission device 1D, when an excessive torque is input to the input side center piece 2 from the engine as the prime mover, a dedicated elastic body (coil spring) that absorbs the torque based on the excessive torque is used as the damper mechanism 8D. It is not necessary to provide for As a result, it is possible to provide a dynamic damper function to the fluid transmission device 1D while suppressing an increase in cost due to an increase in the number of parts and an increase in the size of the device.

  FIG. 8 is a schematic configuration diagram illustrating a fluid transmission device 1E according to a modification. The damper mechanism 8E of the fluid transmission device 1E shown in the figure does not have an intermediate element (intermediate plate), and is configured such that an input element 81E and an output element 82E are engaged via a spring 83E. . In the fluid transmission device 1E, the turbine connecting member 87E fixed to the turbine runner 5 and the input element 81E (first element) among the plurality of elements constituting the damper mechanism 8E are in contact with each other. Outputs other than the input element 81E (first element) among the plurality of third coil springs 86 (elastic body) arranged, the turbine connecting member 87E fixed to the turbine runner 5 and the plurality of elements constituting the damper mechanism 8E An engagement mechanism disposed between the element 82E (second element) and capable of engaging the turbine connecting member 87E and the output element 82E so that the turbine runner 5 and the output element 82E rotate integrally. 88E.

  In the fluid transmission device 1E configured as described above, when the lockup clutch 9 is engaged with the input side center piece 2 as the input member and the input element 81E of the damper mechanism 8E by the lockup clutch 9, the input element 81E and the turbine A plurality of third coil springs 86 between the connecting member 87E and the turbine runner 5 and the turbine connecting member 87E that serve as masses that do not contribute to torque transmission between the input side center piece 2 and the damper hub 7 as the output member are dynamic. The damper is configured, and the vibration generated between the input side center piece 2 and the input element 81E as the first element is damped by the dynamic damper thus configured, and the vibration is transmitted from the input element 81E to the damper hub 7 as the output member. Can be suppressed. In the fluid transmission device 1E, as the excessive torque exceeding the torque generated by the engine as the prime mover is input to the input side center piece 2, the turbine coupling member 87E and the output element 82E are engaged by the engagement mechanism 88E. When the turbine runner 5 and the output element 82E rotate together, the plurality of third coil springs 86 between the turbine runner 5 and the input element 81E are torqued between the input side center piece 2 and the damper hub 7. It functions as a damper that absorbs water. Thereby, also in the fluid transmission device 1E, when an excessive torque is input to the input side center piece 2 from the engine as the prime mover, a dedicated elastic body (coil spring) that absorbs the torque based on the excessive torque is used as the damper mechanism 8E. It is not necessary to provide for As a result, it is possible to provide a dynamic damper function to the fluid transmission device 1E while suppressing an increase in cost due to an increase in the number of parts and an increase in the size of the device.

  FIG. 9 is a schematic configuration diagram illustrating a fluid transmission device 1F according to a modification. The damper mechanism 8F of the fluid transmission device 1F shown in the figure also has an intermediate element (intermediate plate), and is configured such that the input element 81F and the output element 82F are engaged via a spring 83F. . In the fluid transmission device 1F, the turbine connection member 87F fixed to the turbine runner 5 and the output element 82F (first element) among the plurality of elements constituting the damper mechanism 8F are in contact with each other. A plurality of third coil springs 86 (elastic body) arranged, a turbine connecting member 87F fixed to the turbine runner 5 and an input other than the output element 82F (first element) among the plurality of elements constituting the damper mechanism 8F An engagement mechanism that is disposed between the element 81F (second element) and can engage the turbine connecting member 87F and the input element 81F so that the turbine runner 5 and the input element 81F rotate together. 88F.

  In the fluid transmission device 1 </ b> F configured as described above, the output element 82 </ b> F and the turbine are in the lockup-on state where the input side centerpiece 2 as the input member and the input element 81 </ b> F of the damper mechanism 8 </ b> F are engaged by the lockup clutch 9. A plurality of third coil springs 86 between the connecting member 87F and the turbine runner 5 and the turbine connecting member 87F that serve as masses that do not contribute to torque transmission between the input side center piece 2 and the damper hub 7 as the output member are dynamic. The damper is configured, and the vibration generated between the input side center piece 2 and the output element 82F as the first element is attenuated by the dynamic damper thus configured, and the vibration is transmitted from the output element 82F to the damper hub 7 as the output member. Can be suppressed. In the fluid transmission device 1F, the turbine coupling member 87F and the input element 81F are engaged by the engagement mechanism 88F as the excessive torque as described above is input to the input side center piece 2 from the engine as the prime mover. When the turbine runner 5 and the input element 81F rotate together, the plurality of third coil springs 86 between the turbine runner 5 and the output element 82F cause torque between the input side center piece 2 and the damper hub 7. Functions as a damper to absorb. Thereby, also in the fluid transmission device 1F, when an excessive torque is input to the input side center piece 2 from the engine as a prime mover, a dedicated elastic body (coil spring) that absorbs the torque based on the excessive torque is used as the damper mechanism 8F. It is not necessary to provide for As a result, it is possible to provide a dynamic damper function to the fluid transmission device 1F while suppressing an increase in cost due to an increase in the number of parts and an increase in the size of the device.

  Note that at least the fluid transmission device 1 described above is configured as a torque converter having a torque amplification function including a stator 6 that rectifies the flow of hydraulic oil from the turbine runner 5 to the pump impeller 4. The transmission may be configured as a stator 6, that is, a fluid coupling that does not have a torque amplification function.

  Here, the correspondence between the main elements of the embodiment and the modification and the main elements of the invention described in the column of means for solving the problems will be described. That is, in the above-described embodiments and modifications, the input side center piece 2 connected to the engine as the prime mover corresponds to the “input member”, and the damper hub 7 connected to the input shaft IS of the transmission is the “output member”. Correspondingly, the pump impeller 4 connected to the input side center piece 2 corresponds to a “pump impeller”, and a turbine runner 5 rotatable coaxially with the pump impeller 4 corresponds to a “turbine runner” and is connected to a damper hub 7. The damper mechanisms 8 to 8F correspond to “damper mechanisms”, and a lock-up clutch 9 that engages the input side center piece 2 and the input elements 81 to 81F of the damper mechanisms 8 to 8F and releases the engagement between the two is provided. A first element corresponding to a “lock-up clutch” and being one of a plurality of elements constituting the turbine runner 5 and the damper mechanisms 8 to 8F The third coil spring 86 disposed so as to be in contact with both corresponds to an “elastic body”, and the third coil spring 86 other than the first element among the plurality of elements constituting the turbine runner 5 and the damper mechanisms 8 to 8F. The engagement mechanisms 88 to 88F that are disposed between the two elements and can engage the turbine runner 5 and the second element so as to rotate together correspond to the “engagement mechanism”.

  However, the correspondence relationship between the main elements of the embodiment and the main elements of the invention described in the column of means for solving the problem is described in the column of means for the embodiment etc. to solve the problem. The embodiment for carrying out the invention is an example for specifically explaining the embodiment, and does not limit the elements of the invention described in the column of means for solving the problem. In other words, the examples and the like are merely specific examples of the invention described in the column of means for solving the problem, and the interpretation of the invention described in the column of means for solving the problem is not limited to that column. This should be done based on the description.

  The embodiments of the present invention have been described above using the embodiments. However, the present invention is not limited to the above embodiments, and various modifications can be made without departing from the scope of the present invention. Needless to say.

  The present invention can be used in the field of manufacturing fluid transmission devices.

  1, 1B, 1C, 1D, 1E, 1F Fluid transmission device, 2 Input side center piece, 3 Front cover, 4 Pump impeller, 5 Turbine runner, 6 Stator, 7 Damper hub, 8, 8B, 8C, 8D, 8E, 8F Damper mechanism, 9 Lock-up clutch, 40 Pump shell, 41 Pump blade, 50 Turbine shell, 51 Turbine blade, 60 Stator blade, 61 One-way clutch, 81, 81B, 81C, 81D, 81E, 81F Input element, 82, 82B, 82C, 82D, 82E, 82F Output element, 83 1st coil spring, 83E, 83F spring, 84 2nd coil spring, 85, 85C, 85D Intermediate element, 86 3rd coil spring, 87, 87B, 87C, 87D, 87E , 87F Turbi Connecting member, 88, 88B, 88C, 88D, 88E, 88F engagement mechanism, 90 lock-up piston, 91 clutch hub, 92 return spring, 93 first clutch plate, 94 second clutch plate, 95 lock-up chamber, 811 1st input plate, 812 2nd input plate, 813 3rd input plate, 821 1st output plate, 822 2nd output plate, 822a Axial protrusion, 871 Radial protrusion.

Claims (5)

  1. An input member coupled to the prime mover, an output member coupled to the input shaft of the transmission, a pump impeller connected to the input member, a turbine runner rotatable coaxially with the pump impeller, and the output member In a fluid transmission device comprising: a connected damper mechanism; and a lock-up clutch capable of engaging the input member and an input element of the damper mechanism and releasing the engagement between the two.
    An elastic body disposed between the turbine runner and the first element which is one of a plurality of elements constituting the damper mechanism;
    The turbine runner is disposed between the turbine runner and a second element other than the first element among the plurality of elements constituting the damper mechanism so that the turbine runner and the second element rotate together. An engagement mechanism that can be engaged;
    Equipped with a,
    When the input member and the input element of the damper mechanism are engaged by the lock-up clutch, the elastic body between the turbine runner and the first element includes the input member and the output member. When a dynamic damper is configured together with a turbine runner that does not contribute to torque transmission between the turbine runner and the second element, the turbine runner and the first element are engaged with each other by the engagement mechanism. the elastic body, a fluid transmission device characterized that you function as a damper that absorbs the torque between the input member and the output member.
  2. The fluid transmission device according to claim 1,
    The damper mechanism includes the input element and an output element connected to the output member, the first element is one of the input element and the output element of the damper mechanism, and the second element is The fluid transmission device is the other of the input element and the output element of the damper mechanism.
  3. The fluid transmission device according to claim 1,
    The damper mechanism includes the input element, an intermediate element, and an output element connected to the output member, and the first element is one of the input element and the output element of the damper mechanism, Two elements are the other of the input element and the output element of the damper mechanism.
  4. The fluid transmission device according to claim 1,
    The damper mechanism includes the input element, an intermediate element, and an output element connected to the output member, the first element is the intermediate element of the damper mechanism, and the second element is the damper. A fluid transmission device, wherein the fluid transmission device is one of the input element and the output element of a mechanism.
  5. In the fluid transmission device according to any one of claims 1 to 4,
    The fluid transmission device, wherein the engagement mechanism engages the turbine runner and the second element when an excessive torque exceeding an allowable input torque of the damper mechanism is input to the input member.
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DE102012205797A1 (en) * 2012-04-10 2013-10-10 Zf Friedrichshafen Ag Torsional vibration damping arrangement
CN104169611B (en) * 2012-04-26 2017-03-08 爱信艾达株式会社 Apparatus for starting
DE102012212125A1 (en) * 2012-07-11 2014-01-16 Zf Friedrichshafen Ag Torsional vibration damper
JP6209345B2 (en) * 2012-08-14 2017-10-04 株式会社エフ・シー・シー Power transmission device
WO2014148138A1 (en) * 2013-03-19 2014-09-25 株式会社エフ・シ-・シ- Power transmission device
JP2014070647A (en) * 2012-09-27 2014-04-21 Aisin Aw Co Ltd Starting device
JP5792216B2 (en) * 2013-03-13 2015-10-07 富士重工業株式会社 damper device
JP2015098930A (en) * 2013-11-20 2015-05-28 株式会社エクセディ Torque converter lock-up device
DE112015000319T5 (en) 2014-02-28 2016-10-27 Aisin Aw Co., Ltd. Damper device
JP6477154B2 (en) * 2014-04-30 2019-03-06 アイシン・エィ・ダブリュ株式会社 Damper device
US10072726B2 (en) 2014-08-05 2018-09-11 Aisin Aw Co., Ltd. Damper device
JP6287763B2 (en) * 2014-10-31 2018-03-07 アイシン・エィ・ダブリュ株式会社 Starting device
JP6308193B2 (en) * 2014-11-07 2018-04-11 トヨタ自動車株式会社 Vehicle control device
US10323716B2 (en) 2014-12-25 2019-06-18 Aisin Aw Co., Ltd. Damper device

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