JP2016179749A - Power output device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To realize miniaturization and cost reduction of a power output device without causing the deterioration of vibration by a torque variation in an engine.SOLUTION: A first drive plate 71 is rigidly joined to a crankshaft 60, and a second drive plate 72 is rigidly joined to an input side rotor 28, and the first drive plate 71 and the second drive plate 72 are rigidly joined, so that rigidity can be improved when directly connecting the crankshaft 60 and the input side rotor 28. The input side rotor 28 and the first and second drive plates 71 and 72 function as inertia on the engine 36 side, and the moment of inertia is increased by enlarging a radius of the first and second drive plates 71 and 72 larger than a counterweight radius of the crankshaft 60, so that the moment of inertia on the engine 36 side can be increased, and a rotational variation by a torque variation of the crankshaft 60 can be reduced.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a power output apparatus including an engine.

  In the following Patent Document 1, a flywheel damper is installed between the crankshaft of the engine and the input shaft of the transmission, thereby suppressing the torque fluctuation of the engine from being transmitted to the output shaft side of the transmission. .

JP2013-75541A JP 2012-57694 A

  In Patent Document 1, the installation of the flywheel damper is the cause of an increase in the physique and cost of the apparatus, so it is ideal to omit it. However, if the flywheel damper is omitted, vibration due to engine torque fluctuations will increase and cause damage to the crankshaft, or vibration due to engine torque fluctuations will be transmitted to the output shaft side of the transmission, causing vibration and noise. Since it causes deterioration, it is difficult to omit the flywheel damper. Further, in Patent Document 1, a flywheel damper is installed between a crankshaft of an engine and an input shaft of a transmission to constitute a two-inertia vibration system by the crankshaft and the transmission, and resonance of the two-inertia vibration system. Vibration in the frequency band increases.

  An object of the present invention is to realize a reduction in size and cost of a power output apparatus without causing deterioration of vibration due to engine torque fluctuation.

  The power output apparatus according to the present invention employs the following means in order to achieve the above-described object.

  A power output apparatus according to the present invention includes an engine having a crankshaft, an input-side rotor capable of rotating relative to each other, a rotating electrical machine capable of generating torque between the output-side rotor, and a first rigidly coupled to the crankshaft. A drive plate and a second drive plate rigidly connected to the input-side rotor, wherein the first drive plate and the second drive plate have a radius greater than a counterweight radius of the crankshaft. The gist of the invention is to output the engine power to the output side rotor by generating torque between the input side rotor and the output side rotor.

  In one aspect of the present invention, the first and second drive plates are accommodated inside the plate case, and the plate case is formed with an opening hole at a radial position corresponding to the rigid connection portion of the first and second drive plates. It is preferable that the inside of the plate case can communicate with the outside of the engine through the opening hole.

  In one aspect of the present invention, it is preferable that a rotor winding is disposed on the output-side rotor, and further includes a slip ring that is electrically connected to the rotor winding and rotates together with the output-side rotor.

  In one aspect of the present invention, it is preferable that the input-side rotor is disposed radially outside the output-side rotor.

  In one aspect of the present invention, it is preferable that one or more of the first and second drive plates have flexibility in the axial direction of the crankshaft.

  According to the present invention, a torque is generated between the input-side rotor and the output-side rotor to output engine power to the output-side rotor. Therefore, the flywheel damper for absorbing torque fluctuations in the crankshaft is provided. Even without the connection, it is possible to suppress the torque fluctuation of the crankshaft from being transmitted to the output side rotor. Then, the first drive plate is rigidly connected to the crankshaft, the second drive plate is rigidly connected to the input-side rotor, and the first drive plate and the second drive plate are rigidly connected. The rigidity at the time of directly connecting the child can be improved. Furthermore, the rotor on the input side and the first and second drive plates function as inertia on the engine side, and the inertia moment is increased by making the radius of the first and second drive plates larger than the counterweight radius of the crankshaft. The moment of inertia on the engine side can be increased, and the rotational fluctuation due to the torque fluctuation of the crankshaft can be reduced. As a result, the flywheel damper can be omitted without causing deterioration of vibration due to engine torque fluctuation, and the power output device can be reduced in size and cost.

It is a figure showing a schematic structure of a power output device concerning an embodiment of the present invention. It is sectional drawing which shows the structural example of an engine and a rotary electric machine. It is sectional drawing which shows the structural example of an engine and a rotary electric machine. It is an enlarged view of the A section of FIG. It is a figure explaining the procedure which rigidly connects an input side rotor and a crankshaft. It is a figure explaining the procedure which rigidly connects an input side rotor and a crankshaft. It is a figure explaining operation | movement when axial direction vibration generate | occur | produces in a crankshaft.

  DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments for carrying out the present invention (hereinafter referred to as embodiments) will be described with reference to the drawings.

  1-4 is a figure which shows the outline of a structure of the power output device which concerns on embodiment of this invention. 1 shows an outline of the overall configuration, FIGS. 2 and 3 show sectional views of configuration examples of the engine 36 and the rotating electrical machine 10, and FIG. 4 shows an enlarged view of a portion A in FIG. The power output apparatus according to this embodiment includes an engine (internal combustion engine) 36 capable of generating power (mechanical power), and a rotating electrical machine 10 provided between the engine 36 and a drive shaft 37. The power output apparatus according to this embodiment is mounted on a vehicle in order to drive the vehicle, for example.

  The engine 36 includes a crankshaft 60, a cylinder block 70, and an oil pan 80. 2 and 3 show examples of a three-cylinder engine, the number of cylinders of the engine 36 can be arbitrarily set. The cylinder block 70 and the oil pan 80 form an outer wall of the engine 36. The crankshaft 60 is a crank journal 61 that is rotatably supported by a cylinder block 70 via a bearing (metal), and a crankpin that is provided for each cylinder, and to which a connecting rod 68 is attached via a bearing (metal). 62, a crank arm 63 connecting the crank journal 61 and the crank pin 62, and a counterweight 64 formed integrally with the crank arm 63. A flange portion 65 is provided at one end portion in the axial direction of the crankshaft 60, and the flange portion 65 is rotatably supported by the cylinder block 70 via an oil seal 66. The engine 36 generates power on the crankshaft 60 by burning fuel in each cylinder.

  The rotating electrical machine 10 includes an input-side rotor 28 and an output-side rotor 18 that are disposed on one side in the axial direction (the side on which the flange portion 65 is provided) from the engine 36 and that can rotate relative to each other. The input-side rotor 28 and the output-side rotor 18 are arranged to face each other with a predetermined gap in the radial direction orthogonal to the rotor rotation axis. In the example of FIGS. Located outside.

  The input-side rotor 28 includes a rotor core 53 and a permanent magnet 33 that is disposed along the circumferential direction of the rotor core 53 and generates a field magnetic flux. The permanent magnet 33 is disposed on the inner peripheral portion of the rotor core 53 so as to face the output-side rotor 18. The output-side rotor 18 includes a rotor core 52 and a plurality of (for example, three-phase) rotor windings 30 disposed on the rotor core 52 along the circumferential direction thereof. When a plurality of phases (for example, three phases) of alternating current flows through the rotor windings 30 of the plurality of phases, a rotating magnetic field that rotates in the rotor circumferential direction is generated in the output-side rotor 18.

  In the case 15, an input-side rotor support member 83 is rigidly connected to one end portion in the axial direction of the input-side rotor 28, and an input-side rotor support member 84 is rigidly connected to the other end portion in the axial direction of the input-side rotor 28. It is tied. Since the crankshaft 60 is rigidly connected to the input side rotor support member 84, the input side rotor 28 and the crankshaft 60 are rigidly connected. A configuration example for rigidly connecting the input side rotor 28 (input side rotor support member 84) and the crankshaft 60 will be described later.

  In the case 15, the output-side rotor 18 is disposed at a position on the outer peripheral side of the output shaft 24 with a space from the output shaft 24. The inner peripheral side end of the output side rotor support member 81 is mechanically engaged with the output shaft 24, and the outer peripheral side end of the output side rotor support member 81 is mechanically connected to the output side rotor 18. The output side rotor 18 and the output shaft 24 are mechanically engaged. Further, the output gear 86 and the slip ring 95 are mechanically engaged with the output shaft 24, whereby the output side rotor 18, the output gear 86 and the slip ring 95 are mechanically engaged. In the example of FIGS. 1 to 3, the output gear 86 is arranged on one side in the axial direction from the output side rotor 18, and the slip ring 95 is arranged on one side in the axial direction from the output gear 86. The rotation center axes of the input side rotor 28 and the output side rotor 18 coincide with the rotation center axis of the output shaft 24, and the rotation center axis of the output shaft 24 (the rotation center axis of the input side rotor 28 and the output side rotor 18) is This coincides with the rotation center axis of the crankshaft 60 (crank journal 61).

  The input side rotor support member 84 is rotatably supported by the case 15 via a bearing 91, and the output shaft 24 is rotatably supported by the input side rotor support member 84 via a bearing 92. The output gear 86 is rotatably supported by the case 15 via a bearing 93 and is further rotatably supported by the input-side rotor support member 83 via a bearing 94. The input side rotor 28 rotates integrally with the input side rotor support members 83 and 84 and the crankshaft 60. The output-side rotor 18 rotates together with the output-side rotor support member 81, the output shaft 24, the output gear 86, and the slip ring 95. The rotation center axis of the output shaft 24 and the rotation center axis of the drive shaft 37 are arranged in parallel to each other. The output gear 87 is mechanically engaged with the drive shaft 37, and the output gear 86 and the output gear 87 are engaged with each other. The diameter of the output gear 87 is larger than the diameter of the output gear 86.

  The slip ring 95 is electrically connected to each phase of the rotor winding 30. The brush 96 whose rotation is fixed is pressed against the slip ring 95 to be in electrical contact. The slip ring 95 rotates with the output-side rotor 18 while sliding with respect to the brush 96 (while maintaining electrical contact with the brush 96).

  The chargeable / dischargeable power storage device 42 provided as a direct current power source can be constituted by a secondary battery, for example, and stores electrical energy. An inverter 41 provided as a power conversion device that performs power conversion between the power storage device 42 and the rotor winding 30 includes a switching element and a diode (rectifier element) connected in reverse parallel to the switching element. It can be realized by the configuration, and the DC power from the power storage device 42 is converted into AC (for example, three-phase AC) by the switching operation of the switching element, and is transferred to each phase of the rotor winding 30 via the brush 96 and the slip ring 95. It is possible to supply. Furthermore, the inverter 41 can also perform power conversion in a direction in which an alternating current flowing in each phase of the rotor winding 30 is converted into a direct current. At that time, the AC power of the rotor winding 30 is extracted by the slip ring 95 and the brush 96, and the extracted AC power is converted into DC by the inverter 41 and collected by the power storage device 42. Thus, the inverter 41 can perform bidirectional power conversion between the power storage device 42 and the rotor winding 30.

  As the input side rotor 28 rotates relative to the output side rotor 18, a rotational difference occurs between the input side rotor 28 (permanent magnet 33) and the output side rotor 18 (rotor winding 30). An induced electromotive force is generated at 30, and an induced current (alternating current) flows through the rotor winding 30 due to the induced electromotive force, thereby generating a rotating magnetic field. Then, torque can be applied from the input side rotor 28 to the output side rotor 18 by the electromagnetic interaction between the rotating magnetic field generated by the induced current of the rotor winding 30 and the field flux of the permanent magnet 33. It can be rotated. Thus, the permanent magnet 33 of the input side rotor 28 and the rotor winding 30 of the output side rotor 18 are electromagnetically coupled, so that the rotating magnetic field generated in the rotor winding 30 acts on the input side rotor 28. Accordingly, torque (magnet torque) acts between the input-side rotor 28 and the output-side rotor 18. Therefore, power (mechanical power) can be transmitted between the input-side rotor 28 and the output-side rotor 18, and the input-side rotor 28 and the output-side rotor 18 can function as an induction electromagnetic coupling unit.

  When the torque (electromagnetic coupling torque) is generated between the input side rotor 28 and the output side rotor 18 by the induced current of the rotor winding 30, the induced current is allowed to flow through the rotor winding 30. Then, the switching operation of the inverter 41 is performed. In that case, the electromagnetic coupling torque acting between the input side rotor 28 and the output side rotor 18 can be controlled by controlling the alternating current flowing through the rotor winding 30 by the switching operation of the inverter 41. . On the other hand, by maintaining the switching element of the inverter 41 in the OFF state and stopping the switching operation, the induced current does not flow through the rotor winding 30, and torque acts between the input side rotor 28 and the output side rotor 18. Disappear.

  When the engine 36 is generating power, the power of the engine 36 is transmitted to the input side rotor 28, and the input side rotor 28 is rotationally driven in the engine rotation direction. When the rotational speed of the input side rotor 28 becomes higher than the rotational speed of the output side rotor 18, an induced electromotive force is generated in the rotor winding 30. By performing the switching operation of the inverter 41 so as to allow the induction current to flow through the rotor winding 30, the electromagnetic wave interaction between the induction current of the rotor winding 30 and the field flux of the permanent magnet 33 causes the input side rotor 28 to Electromagnetic coupling torque in the engine rotation direction acts on the output-side rotor 18 to drive the output-side rotor 18 to rotate in the engine rotation direction. As described above, the power transmitted from the engine 36 to the input side rotor 28 is output to the output side rotor 18 by electromagnetic coupling between the permanent magnet 33 of the input side rotor 28 and the rotor winding 30 of the output side rotor 18. The The power transmitted to the output side rotor 18 is transmitted to the drive shaft 37 after being decelerated by the output gears 86 and 87, and used for forward driving of the load such as forward driving of the vehicle. Therefore, the drive shaft 37 can be rotationally driven in the forward direction using the power of the engine 36, and the vehicle can be driven in the forward direction. Further, since the rotational difference between the input side rotor 28 and the output side rotor 18 can be allowed, the engine 36 does not stall even if the rotation of the drive shaft 37 is stopped. Therefore, the rotating electrical machine 10 can function as a starting device, and there is no need to separately provide a starting device such as a friction clutch or a torque converter.

  In the engine 36, torque fluctuation occurs in the crankshaft 60 due to intermittent combustion or the like in each cylinder. When the torque fluctuation of the crankshaft 60 is transmitted to the output shaft 24, vibration due to the torque fluctuation occurs in the drive shaft 37, which causes a deterioration in the riding comfort of the vehicle, a booming sound, and the like. On the other hand, in the present embodiment, the crankshaft 60 and the output shaft 24 are not mechanically engaged, and the output is output from the crankshaft 60 by the electromagnetic coupling torque acting between the input side rotor 28 and the output side rotor 18. Torque is transmitted to the shaft 24. Therefore, transmission of torque fluctuation of the crankshaft 60 to the output shaft 24 can be suppressed without connecting a flywheel damper for absorbing torque fluctuation to the crankshaft 60. Therefore, in this embodiment, the flywheel damper is omitted and the input side rotor 28 and the crankshaft 60 are rigidly connected. Hereinafter, a configuration example for that purpose will be described.

  As shown in FIGS. 2 and 4, a flange portion 73 is provided at one axial end of the outer wall (cylinder block 70 and oil pan 80) in the engine 36, and the axial other end of the case 15 in the rotating electrical machine 10. The part is provided with a flange part 74 facing the flange part 73. A plate case 75 is formed by fastening the flange portion 73 and the flange portion 74 together.

  Inside the plate case 75, the substantially disk-shaped first drive plate 71 is rigidly connected to the flange portion 65 (one end portion in the axial direction) of the crankshaft 60 by a plurality of bolts 76 arranged in the circumferential direction. Yes. The substantially disk-shaped second drive plate 72 is rigidly connected to the input-side rotor 28 by being rigidly connected to the input-side rotor support member 84 by a plurality of bolts 77 arranged in the circumferential direction. Yes. Further, the first drive plate 71 and the second drive plate 72 are rigidly connected by a plurality of bolts 78 arranged in the circumferential direction. Thus, the input side rotor 28 and the crankshaft 60 are rigidly connected by the rigid connection between the first and second drive plates 71 and 72 housed in the plate case 75.

  The radii of the first and second drive plates 71 and 72 are larger than the crank radius (the distance between the central axis 61a of the crank journal 61 and the central axis of the crank pin 62), and the radius of the counterweight 64 (the crankshaft 60). Maximum radius) larger than Rw. The fastening locations of the first drive plate 71 and the second drive plate 72 by the bolts 78 are the fastening locations of the first drive plate 71 and the flange portion 65 by the bolts 76, and the bolts of the second drive plate 72 and the input side rotor support member 84. 77 is located on the outer peripheral side from the fastening location. The first and second drive plates 71, 72 are flexible in the axial direction of the crankshaft 60, and are located on the inner peripheral side from the fastening position by the bolt 78 between the first drive plate 71 and the second drive plate 72. Has voids.

  As shown in FIGS. 2 and 4, in the plate case 75 (flange portion 73), the opening hole 79 has a diameter corresponding to a fastening position (rigid connection position) of the first and second drive plates 71 and 72 by the bolt 78. It is formed at a directional position. That is, in the axial direction, the fastening portion of the first and second drive plates 71 and 72 by the bolt 78 faces the opening hole 79 of the flange portion 73. The lower wall of the oil pan 80 that forms the outer wall of the engine 36 is a lower wall portion that is located radially inward from the opening hole 79 of the flange portion 73 (the fastening portion by the bolt 78 of the first and second drive plates 71 and 72). 80 a is provided on one side in the axial direction (side on which the flange portion 65 is provided), and the inside of the plate case 75 can communicate with the outside of the engine 36 through the opening hole 79.

  When the input-side rotor 28 and the crankshaft 60 are rigidly connected, as shown in FIG. 5, the first drive plate 71 is rigidly connected to the flange portion 65 of the crankshaft 60 by a plurality of bolts 76 to support the input-side rotor. The second drive plate 72 is rigidly connected to the member 84 by a plurality of bolts 77. Then, the first and second drive plates 71 and 72 are accommodated in the plate case 75 by fastening the flange portion 73 and the flange portion 74, and as shown in FIG. 6, the first drive plate 71 and the second drive plate 72 is rigidly connected by a plurality of bolts 78. At that time, a bolt fastening tool is inserted into the plate case 75 from the outside of the engine 36 through the opening hole 79, and the first and second drive plates 71 and 72 are rotated and fastened with the bolts 78. Thereby, the workability at the time of fastening the first drive plate 71 and the second drive plate 72 with the bolts 78 can be improved. After the first drive plate 71 and the second drive plate 72 are rigidly connected, the opening hole 79 of the flange portion 73 is covered so that the inside of the plate case 75 and the outside of the engine 36 do not communicate with each other through the opening hole 79. .

  As described above, in this embodiment, even if the flywheel damper is omitted, it is possible to suppress the torque fluctuation of the crankshaft 60 from being transmitted to the output shaft 24. By omitting the flywheel damper and directly connecting the crankshaft 60 and the input-side rotor 28, the power output device can be reduced in size and cost. At this time, however, if the torsional rigidity (rigidity in the rotational direction) between the crankshaft 60 and the input side rotor 28 is low, a two-inertia torsional vibration system by the crankshaft 60 and the input side rotor 28 is configured on the engine 36 side. The torsional vibration on the engine 36 side increases in the resonance frequency (for example, about 10 Hz) band of the two inertia vibration system.

  On the other hand, in this embodiment, the crankshaft 60 and the first drive plate 71 are rigidly connected in the rotational direction, and the input-side rotor 28 and the second drive plate 72 are rigidly connected in the rotational direction. By rigidly connecting the second drive plate 72 in the rotational direction, the crankshaft 60 and the input-side rotor 28 can be rigidly connected by a non-twisted member, and the torsional rigidity (rotation) between the crankshaft 60 and the input-side rotor 28 can be achieved. Direction rigidity). As a result, the engine 36 side has a rigid structure that does not substantially have a resonance mode with respect to torsional vibration, and torsional vibration due to resonance can be reduced. In order to further improve the torsional rigidity between the crankshaft 60 and the input side rotor 28, the crankshaft 60 (flange portion 65) and the input side rotor 28 are within a range in which the engine 36 and the rotor winding 30 can be insulated. It is preferable to shorten the axial distance.

  Further, when the flywheel damper is omitted, if the rotational fluctuation due to the torque fluctuation of the crankshaft 60 increases, it causes a humming noise and unpleasant vibration. On the other hand, in the present embodiment, not only the input side rotor 28 and the input side rotor support members 83 and 84 but also the first and second drive plates 71 and 72 function as rotational inertia on the engine 36 side. The inertia moment on the engine 36 side can be increased by increasing the inertia moment by making the radius of the second drive plates 71 and 72 larger than the radius of the counterweight 64 (the maximum radius of the crankshaft 60) Rw. As a result, rotation fluctuation due to torque fluctuation of the crankshaft 60 can be reduced, and muffled noise and unpleasant vibration can be reduced. Furthermore, in the present embodiment, the moment of inertia of the input-side rotor 28 can be increased by disposing the input-side rotor 28 on the outer peripheral side (radially outward) from the output-side rotor 18. As a result, the moment of inertia on the engine 36 side can be further increased, and rotation fluctuation due to torque fluctuation of the crankshaft 60 can be further reduced.

  Further, when vibration due to torque fluctuation of the crankshaft 60 is transmitted to the slip ring 95, wear of the brush 96 is likely to increase due to vibration of the slip ring 95. In contrast, in the present embodiment, the transmission of vibration from the crankshaft 60 to the slip ring 95 can be suppressed by providing the rotor winding 30 on the output side rotor 18 and providing the slip ring 95 on the output shaft 24 side. This can reduce wear of the brush 96.

  In addition, when vibration is generated in the crankshaft 60, if the axial component of the vibration cannot be released, the crankshaft 60 may be damaged. On the other hand, in this embodiment, since the first and second drive plates 71 and 72 are flexible in the axial direction, even if axial vibration occurs in the crankshaft 60, for example, as shown in FIG. Since the first and second drive plates 71 and 72 are bent and deformed in the axial direction, the axial vibration of the crankshaft 60 can be released. As a result, damage to the crankshaft 60 can be prevented. Even if only the first drive plate 71 of the first and second drive plates 71 and 72 is flexible in the axial direction, the axial vibration of the crankshaft 60 is caused in the axial direction of the first drive plate 71. It is possible to escape by bending deformation. Even when only the second drive plate 72 of the first and second drive plates 71, 72 has flexibility in the axial direction, the axial vibration of the crankshaft 60 is caused in the axial direction of the second drive plate 72. It is possible to escape by bending deformation.

  Therefore, according to the present embodiment, the flywheel damper can be omitted without deteriorating the vibration due to the torque fluctuation of the engine 36, and the power output device can be reduced in size and cost.

  As mentioned above, although the form for implementing this invention was demonstrated, this invention is not limited to such embodiment at all, and it can implement with a various form in the range which does not deviate from the summary of this invention. Of course.

  DESCRIPTION OF SYMBOLS 10 Rotating electric machine, 15 Case, 18 Output side rotor, 28 Input side rotor, 30 Rotor winding, 33 Permanent magnet, 36 Engine, 37 Drive shaft, 41 Inverter, 42 Power storage device, 52, 53 Rotor core, 60 Crankshaft, 61 Crank journal, 62 Crank pin, 63 Crank arm, 64 Counter weight, 65, 73, 74 Flange, 66 Oil seal, 68 Connecting rod, 70 Cylinder block, 71 First drive plate, 72 Second drive plate, 75 Plate case , 76, 77, 78 bolt, 79 opening hole, 80 oil pan, 80a lower wall part, 81 output side rotor support member, 83, 84 input side rotor support member, 86, 87 output gear, 91, 92, 93, 94 Bearing, 9 Slip ring, 96 brush.

Claims (5)

An engine having a crankshaft;
A rotating electrical machine capable of generating torque between an input-side rotor and an output-side rotor that can rotate relative to each other;
A first drive plate rigidly connected to the crankshaft;
A second drive plate rigidly connected to the input side rotor;
With
The radius of the first and second drive plates is greater than the counterweight radius of the crankshaft,
The first drive plate and the second drive plate are rigidly connected,
A power output apparatus that outputs engine power to an output-side rotor by generating torque between an input-side rotor and an output-side rotor. The power output device according to claim 1,
The first and second drive plates are housed inside the plate case;
In the plate case, an opening hole is formed at a radial position corresponding to the rigid connection portion of the first and second drive plates,
A power output device in which the inside of the plate case can communicate with the outside of the engine through an opening hole. The power output device according to claim 1 or 2,
A rotor winding is disposed on the output side rotor,
A power output apparatus further comprising a slip ring that is electrically connected to the rotor winding and rotates with the output-side rotor. The power output device according to any one of claims 1 to 3,
A power output device in which the input-side rotor is disposed radially outside the output-side rotor. The power output device according to any one of claims 1 to 4,
A power output apparatus in which any one or more of the first and second drive plates are flexible in the axial direction of the crankshaft.

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