JP6296033B2 - Torque fluctuation reduction device - Google Patents

Description

  The present invention relates to a torque fluctuation reducing device, and more particularly to a torque fluctuation reducing device that reduces torque fluctuation generated on a rotating shaft such as an output shaft of an engine.

  In vehicles such as automobiles, torque fluctuations occur in the output shaft of the engine due to intermittent explosions in each cylinder of the engine. For example, in an in-line four-cylinder four-cycle engine, twice during one revolution of the engine output shaft. Torque fluctuation occurs, and secondary torque fluctuation occurs with respect to the output torque of the engine. This torque fluctuation can be transmitted to a drive system such as a transmission to cause vibration and noise.

  On the other hand, for example, Patent Document 1 discloses a torque fluctuation reducing device that reduces torque fluctuation generated on an output shaft of an engine. In this torque fluctuation reducing device, a plurality of circular recesses are formed in the circumferential direction on a flywheel attached to the output shaft of the engine, and the position of the center of gravity is deviated from the center line of the circular recess via a bearing in each of these circular recesses. By attaching the damper weight in a swingable manner, the torque fluctuation generated on the output shaft of the engine is reduced by the swinging motion of the damper weight.

Japanese Patent Laid-Open No. 11-2294

  By the way, in a vehicle such as an automobile, in order to improve the fuel efficiency of the engine, it is possible to switch between all-cylinder operation in which all of a plurality of cylinders are operated and reduced-cylinder operation in which only some of the plurality of cylinders are operated. An engine having an engine configured as described above is known.

  For example, when an in-line four-cylinder four-cycle engine is configured to be able to switch between all-cylinder operation that operates four cylinders and reduced-cylinder operation that operates only two cylinders, the engine output shaft rotates once during all-cylinder operation. Two torque fluctuations occur, and during the reduced cylinder operation, one torque fluctuation occurs during one revolution of the engine output shaft, and occurs on the engine output shaft during all cylinder operation and during the reduced cylinder operation. The torque fluctuation mode to be changed will change.

  In the torque fluctuation reducing device described in Patent Document 1, the center line of the circular recess, the gravity center position of the damper weight, and the like are set so as to effectively reduce the torque fluctuation generated on the output shaft of the engine during all cylinder operation. In this case, there is a possibility that the torque fluctuation generated on the output shaft of the engine during the reduced cylinder operation cannot be effectively reduced.

  Therefore, it is desirable to effectively reduce the torque fluctuation generated on the rotating shaft even when the torque fluctuation generated on the rotating shaft such as the output shaft of the engine has two modes.

  Therefore, an object of the present invention is to provide a torque fluctuation reducing device that can effectively reduce the torque fluctuation generated on the rotating shaft even when the torque fluctuation generated on the rotating shaft has two modes. .

  In order to solve the above problems, the present invention is configured as follows.

  In the first aspect of the present invention, the rotating shaft for transmitting torque, the weight supporting member that rotates integrally with the rotating shaft, and the weight supporting member are rotatably supported by the rotating shaft. A plurality of weight members arranged at equal intervals in the circumferential direction of the shaft, wherein the weight members are provided in parallel to the rotation shaft and are eccentric from a support shaft rotatably supported by the weight support member. A plurality of weight members having positions, coupled to the rotating shaft and coupled to the supporting shaft, the rotating shaft and the supporting shaft being connected to each other so that the rotating shaft and the supporting shaft have a predetermined rotation ratio. A torque fluctuation reducing device including a planetary gear mechanism configured to be interlocked, wherein the rotating shaft and the support shaft are interlocked with each other using the planetary gear mechanism, and the rotation shaft and the support shaft. Characterized in that it comprises a switching means for switching and a second state to a non-interlocking and.

  According to a second aspect of the present invention, in the torque fluctuation reducing device according to the first aspect, the switching means is a brake that fixes or releases a predetermined rotating element of the planetary gear mechanism to the case. It is configured.

  The invention according to claim 3 is the torque fluctuation reducing device according to claim 1 or 2, further comprising an engine configured to be able to switch between full cylinder operation and reduced cylinder operation, and the rotating shaft. Is an output shaft of the engine, and the switching means switches to the first state during the reduced-cylinder operation of the engine.

  According to a fourth aspect of the present invention, there is provided the torque fluctuation reducing apparatus according to the first or second aspect, further comprising an engine configured to be able to switch between full cylinder operation and reduced cylinder operation, and the rotating shaft. Is an output shaft of the engine, and the switching means switches to the second state when all cylinders of the engine are operated.

  According to the invention described in claim 1 of the present application, the torque fluctuation reducing device includes a weight support member that rotates integrally with a rotating shaft that transmits torque, and a weight support member that is disposed at equal intervals in the circumferential direction of the rotating shaft. A plurality of weight members having a center of gravity eccentric from a support shaft rotatably supported by the member, and the rotation shaft and the support shaft are configured to be interlocked so that the rotation shaft and the support shaft have a predetermined rotation ratio. And a switching means for switching between a first state in which the rotating shaft and the support shaft are interlocked using the planetary gear mechanism and a second state in which the rotation shaft and the support shaft are not interlocked. ing.

  As a result, a planetary gear mechanism configured so that the rotation shaft and the support shaft can be interlocked so as to have a predetermined rotation ratio that generates a fluctuation torque having a phase opposite to that of one mode of torque fluctuation generated on the rotation shaft is used. Thus, in the first state in which the rotating shaft and the support shaft are interlocked using the planetary gear mechanism, torque fluctuations in one mode generated on the rotating shaft can be reliably reduced.

  Further, in the second state in which the rotation shaft and the support shaft are not interlocked with each other, the swinging motion of the weight member rotatably supported by the weight support member that rotates integrally with the rotation shaft generates the rotation shaft. Torque fluctuations in a mode other than the mode can be effectively reduced.

  Therefore, even when the torque fluctuation generated on the rotating shaft has two modes, the torque fluctuation generated on the rotating shaft can be effectively reduced.

  According to the second aspect of the present invention, the switching means is constituted by a brake that fixes or releases a predetermined rotating element of the planetary gear mechanism to the case or releases the hydraulic pressure to the hydraulic chamber as a brake. When using a hydraulic brake that fastens a plurality of friction plates at the time of supply, the hydraulic chamber can be fixed to the case, so that the first state and the second state are compared to the case where a hydraulic clutch that rotates the hydraulic chamber is used. Can be performed with good responsiveness, and torque fluctuations generated on the rotating shaft can be effectively reduced. Further, there is no need to provide a centrifugal balance chamber for canceling the centrifugal force acting on the hydraulic oil in the hydraulic chamber as in the case of using a hydraulic clutch in which the hydraulic chamber rotates, and torque fluctuations can be achieved with a relatively simple configuration. It can be effectively reduced.

  According to the invention described in claim 3, the switching means switches to the first state during the reduced-cylinder operation of the engine configured to be able to switch between the all-cylinder operation and the reduced-cylinder operation, thereby reducing the engine cylinder reduction. By using a planetary gear mechanism that is configured so that the rotation shaft and the support shaft can be interlocked so as to have a predetermined rotation ratio that generates a torque fluctuation opposite in phase to the torque fluctuation that occurs on the output shaft of the engine during operation. The torque fluctuation generated on the output shaft of the engine during the reduced-cylinder operation can be reliably reduced.

  According to the invention as set forth in claim 4, the switching means is integrated with the rotary shaft by switching to the second state during the all-cylinder operation of the engine configured to be able to switch between all-cylinder operation and reduced-cylinder operation. The swinging motion of the weight member rotatably supported by the rotating weight support member can reduce the torque fluctuation generated on the output shaft of the engine during the entire cylinder operation of the engine.

It is sectional drawing of the torque fluctuation reduction apparatus which concerns on 1st Embodiment of this invention. It is sectional drawing of the torque fluctuation reduction apparatus along the Y2-Y2 line | wire in FIG. It is a perspective view of a torque fluctuation reducing device. It is another perspective view of a torque fluctuation reducing device. It is a graph which shows the fluctuation torque by the torque fluctuation reduction apparatus at the time of reduced-cylinder operation. It is explanatory drawing for demonstrating the fluctuation | variation torque by a torque fluctuation | variation reduction apparatus in case the rotation angle of a rotating shaft is 0 degree | times and 45 degree | times at the time of reduced cylinder operation. It is explanatory drawing for demonstrating the fluctuation | variation torque by a torque fluctuation | variation reduction apparatus in case the rotation angle of a rotating shaft is 90 degree | times and 135 degree | times at the time of reduced cylinder operation. It is sectional drawing of the torque fluctuation reduction apparatus which concerns on 2nd Embodiment of this invention. It is sectional drawing of the torque fluctuation reduction apparatus which concerns on 3rd Embodiment of this invention.

  Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

  1 is a cross-sectional view of the torque fluctuation reducing device according to the first embodiment of the present invention, FIG. 2 is a cross-sectional view of the torque fluctuation reducing device along line Y2-Y2 in FIG. 1, and FIG. FIG. 4 is a perspective view of the fluctuation reducing device, and FIG. 4 is another perspective view of the torque fluctuation reducing device. In FIGS. 3 and 4, the carrier of the planetary gear mechanism constituting the torque fluctuation reducing device and the brake provided between the carrier and the case are omitted.

  A torque fluctuation reducing device according to a first embodiment of the present invention is applied to a vehicle engine mounted on a vehicle such as an automobile, and torque generated on a rotating shaft that transmits torque such as a crankshaft that is an output shaft of the engine. It is configured to reduce fluctuations.

  In this embodiment, torque when applied to an in-line four-cylinder four-cycle engine configured to be switchable between all-cylinder operation for operating all four cylinders and reduced-cylinder operation for operating only two of the four cylinders. The fluctuation reducing device will be described.

  In the in-line four-cylinder four-cycle engine, torque fluctuation occurs twice during one revolution of the crankshaft during all cylinder operation, and torque fluctuation occurs once during one revolution of the crankshaft during reduced cylinder operation. The torque fluctuation mode changes between the all-cylinder operation and the reduced-cylinder operation. The torque fluctuation generated in the crankshaft of the engine becomes larger as the number of cylinders to be operated becomes smaller. Therefore, the torque fluctuation becomes larger in the reduced cylinder operation than in the all cylinder operation.

  The torque fluctuation reducing device according to the present embodiment reliably reduces torque fluctuation in one mode that occurs in the crankshaft during the reduced-cylinder operation, and has a mode different from the mode that occurs in the crankshaft during all-cylinder operation. The torque fluctuation is effectively reduced.

  As shown in FIGS. 1 to 4, the torque fluctuation reducing device 10 according to the first embodiment includes a crankshaft 1 that is an output shaft of an in-line four-cylinder four-cycle engine as a rotating shaft 1 that transmits torque, and rotates. A weight support member 11 that rotates integrally with the shaft 1 and four weight members 20 that are rotatably supported by the weight support member 11 are provided.

  Two weight support members 11 are provided apart from each other in the axial direction of the rotary shaft 1. The two weight support members 11 have the same shape and are similarly arranged apart from each other in the axial direction of the rotary shaft 1. The weight support member 11 has a predetermined thickness in the axial direction of the rotary shaft 1 and is formed in a substantially cross shape when viewed from the axial direction of the rotary shaft 1. The weight support member 11 is configured to rotate integrally with the rotary shaft 1 by spline-fitting the inner peripheral surface of a substantially circular opening 11 a formed at the center to the rotary shaft 1.

  As shown in FIG. 2, the weight support member 11 also has four circular openings 11b having a center at a radius r1 from the axis C1 of the rotating shaft 1. The four openings 11b have the same shape and are provided at equal intervals in the circumferential direction of the rotating shaft 1 every 90 degrees. The weight member 20 is rotatably supported by the weight support member 11 through the opening 11 b of the weight support member 11.

  The weight member 20 includes a support shaft 21 provided in parallel with the rotary shaft 1 and a weight 22 fixed to the support shaft 21, and the support shaft 21 is provided on both sides of the weight 22. The support shaft 21 is formed in a columnar shape, has a shaft center C2 provided in parallel with the shaft center C1 of the rotation shaft 1, and is rotatably supported by the weight support member 11. As shown in FIG. 2, the weight 22 is not limited to a central angle from the axial center C2 toward the radially outer side when viewed from the axial direction of the axial center C2 of the support shaft 21, but is 120 degrees. It is formed in a substantially fan shape that spreads out.

  In the weight member 20, the support shaft 21 and the weight 22 are integrally formed. As shown in FIG. 2, the weight member 20 has a center of gravity C3 that is offset from the axis C2 of the support shaft 21 by a distance r2, and is symmetrical with respect to a plane that connects the center C2 of the support shaft 21 and the center of gravity C3. Is formed. The four weight members 20 have the same shape and are arranged at equal intervals in the circumferential direction of the rotating shaft 1 every 90 degrees. In the present embodiment, the weight 22 is formed in a substantially fan shape, but the weight member 20 may be formed in another shape having a center of gravity that is eccentric from the axis C <b> 2 of the support shaft 21.

  The torque fluctuation reducing device 10 also includes a support shaft driven gear 25 provided on the support shaft 21 of the weight member 20 and a support shaft drive gear 26 that meshes with the support shaft driven gear 25 to drive the support shaft 21 of the weight member 20. And a planetary gear mechanism 30 configured to be able to interlock the rotating shaft 1 and the support shaft 21 of the weight member 20.

  The support shaft 21 of the weight member 20 includes an extending portion 21 a that is supported by a weight support member 11 disposed on one axial side of the rotary shaft 1 and extends to the one axial side than the weight support member 11. The support shaft driven gear 25 is fixedly coupled to the extended portion 21a. The support shaft drive gear 26 meshes with the support shaft driven gear 25 on one side of the weight support member 11 in the axial direction, and is rotatably supported by the rotary shaft 1 via the bearing 5.

  The planetary gear mechanism 30 is disposed on one axial side of the rotating shaft 1 of the supported driven gear 25 and the support shaft driving gear 26. The planetary gear mechanism 30 is a double pinion type planetary gear mechanism, and includes a sun gear 31, three inner pinions 33 that mesh with the sun gear 31, three outer pinions 34 that mesh with the inner pinion 33, an inner pinion 33, and an outer pinion, respectively. It comprises a carrier 35 that rotatably supports 34, and a ring gear 32 that meshes with the outer pinion 34.

  A power transmission member 32a is integrally formed on one side of the ring gear 32 in the axial direction. The power transmission member 32 a extends from the ring gear 32 inward in the radial direction of the rotary shaft 1, and an inner peripheral side thereof is splined to the rotary shaft 1. As a result, the ring gear 32 of the planetary gear mechanism 30 is connected to the rotating shaft 1.

  The carrier 35 fixes an inner pinion shaft 35a that rotatably supports the inner pinion 33, an outer pinion shaft (not shown) that rotatably supports the outer pinion 34, and both ends of the inner pinion shaft 35a and the outer pinion shaft. And a carrier main body 35b for supporting.

  The carrier main body 35b includes a first side plate portion 35c and a second side plate portion 35d that respectively support the end portions of the inner side pinion shaft 35a and the outer side pinion shaft on one side and the other side in the axial direction of the rotary shaft 1, respectively. It is comprised by the connection part which is not shown in figure which connects the plate part 35c and the other side plate part 35d.

  In the present embodiment, the other side plate portion 35 d of the carrier body 35 b extends outward in the radial direction of the rotating shaft 1, and its outer peripheral side is fixed to the case 3 disposed on the outer peripheral side of the rotating shaft 1 or from the case 3. When released, the carrier 35 of the planetary gear mechanism 30 is fixed to the case 3 or released from the case 3.

  The sun gear 31 is rotatably supported on the rotary shaft 1 via the bearing 5. In the present embodiment, the sun gear 31 is integrally formed with a support shaft drive gear 26 disposed on the other side in the axial direction of the rotary shaft 1 of the sun gear 31.

  The torque fluctuation reducing device 10 also uses the planetary gear mechanism 30 to link the rotary shaft 1 and the support shaft 21 of the weight member 20 with each other and the rotary shaft 1 and the support shaft 21 of the weight member 20 are not interlocked. Switching means 40 for switching between the second state and the brake means 40 for fixing the carrier 35 of the planetary gear mechanism 30 to the case 3 or releasing it from the case 3, although not limited thereto. It is constituted by.

  As shown in FIG. 1, the brake 40 has a plurality of rotating friction plates 41 whose inner peripheral portions are engaged with splines 35 e formed on the outer peripheral surface of the other plate portion 35 d of the carrier 35 of the planetary gear mechanism 30. And a plurality of fixed-side friction plates 42 whose outer peripheral portions are engaged with splines 3 a formed on the inner peripheral surface of the case 3, and the fixed-side friction plates 41 and the rotation-side friction plates 42 are alternately arranged. Has been.

  On one side in the axial direction of the rotation-side friction plate 41 and the fixed-side friction plate 42, a cylinder 43 provided integrally with the case 3, and the rotation-side friction plate 41 and the fixed-side friction plate 42 housed in the cylinder 43. And a piston 44 and a cylinder 43 form a hydraulic chamber 45.

  A retaining plate 46 fixed to the case 3 is provided on the other axial side of the rotation side friction plate 41 and the fixed side friction plate 42, and the rotation side friction plate 41 and the fixed side friction plate 42 are on the other side in the axial direction. It is prevented from coming off.

  In addition, a control unit (not shown) for controlling the hydraulic pressure supply to the hydraulic chamber 45 is provided, and when the control unit supplies the hydraulic pressure to the hydraulic chamber 45, the rotation side friction plate 41 and the fixed side are fixed. When the side friction plate 42 becomes relatively incapable of rotation and the carrier 35 is fixed to the case 3 and the control for discharging the hydraulic pressure from the hydraulic chamber 45 is performed, the rotation side friction plate 41 and the fixed side friction plate 42 become relatively rotatable. Then, the carrier 35 is released from the case 3.

  Thus, the brake 40 fixes the carrier 35 of the planetary gear mechanism 30 to the case 3 or releases it from the case 3, and fixes the carrier 35 to the case 3 and uses the planetary gear mechanism 30 to rotate the rotating shaft 1 and the weight member. The first state in which the support shaft 21 of 20 is interlocked and the second state in which the carrier 35 is released from the case 3 and the rotation shaft 1 and the support shaft 21 of the weight member 20 are not interlocked are switched. Yes.

  In this embodiment, the brake 40 is switched to a first state in which the carrier 35 is fixed to the case 3 and the planetary gear mechanism 30 is used to interlock the rotary shaft 1 and the support shaft 21 of the weight member 20 during the reduced cylinder operation. During the entire cylinder operation, the carrier 35 is released from the case 3 and switched to the second state in which the rotary shaft 1 and the support shaft 21 of the weight member 20 are not interlocked.

  In the torque fluctuation reducing device 10 configured as described above, the carrier 35 is fixed to the case 3 during the reduced cylinder operation, and the rotating shaft 1 rotates around the axis C1 in the R1 direction as shown in FIGS. Then, the rotation of the rotating shaft 1 is input to the ring gear 32 of the planetary gear mechanism 30 via the power transmission member 32a, and the sun gear 31 is moved around the axis C1 of the rotating shaft 1 via the outer pinion 34 and the inner pinion 33. It is rotated in the R1 direction.

  When the sun gear 31 is rotated in the R1 direction around the axis C1 of the rotary shaft 1, the support shaft drive gear 26 formed integrally with the sun gear 31 is also rotated in the R1 direction around the axis C1 of the rotary shaft 1, The supported driven gear 25 is rotated around the axis C2 of the spindle 21 of the weight member 20 in the R2 direction opposite to the R1 direction, and the weight member 20 is rotated around the axis C2 of the spindle 21 in the R2 direction. The The weight member 20 is also supported by a weight support member 11 that is rotated integrally with the rotary shaft 1, and when the rotary shaft 1 is rotated around the axis C <b> 1 in the direction R <b> 1, together with the rotary shaft 1, It is rotated in the R1 direction around the axis C1.

  As described above, the planetary gear mechanism 30 is connected to the rotating shaft 1 during the reduced-cylinder operation and is connected to the supporting shaft 21 of the weight member 20 via the supporting shaft driving gear 26 and the supporting shaft driven gear 25. 1 and the support shaft 21 of the weight member 20 are interlocked. In the torque fluctuation reducing device 10, the planetary gear mechanism 30 has a predetermined rotation that generates a fluctuation torque having an opposite phase to the torque fluctuation generated on the rotating shaft 1 by the rotating shaft 1 and the support shaft 21 of the weight member 20 during the reduced cylinder operation. The rotating shaft 1 and the support shaft 21 of the weight member 20 are interlocked so as to obtain a ratio.

  In this embodiment, the number of teeth of the support shaft driven gear 25 and the support shaft drive gear 26 is both set to 40, and the number of teeth of the sun gear 31 and the ring gear 32 constituting the planetary gear mechanism 30 is 50 and 100, respectively. Is set to In addition, the number of teeth of the sun gear 31 and the ring gear 32 constituting the support shaft driven gear 25, the support shaft drive gear 26, and the planetary gear mechanism 30 is not limited to this, and the rotation shaft 1 and the weight member 20 It can be appropriately set so that the support shaft 21 has a predetermined rotation ratio that generates a torque fluctuation opposite in phase to the torque fluctuation generated in the rotary shaft 1.

  FIG. 5 is a graph showing the fluctuation torque by the torque fluctuation reduction device during the reduced cylinder operation. In FIG. 5, the rotation angle that is the angular position of the rotary shaft 1 is represented on the horizontal axis, and the variable torque generated on the rotary shaft 1 by the torque fluctuation reduction device 10 is taken on the vertical axis. Some cases are displayed upward, and the case opposite to the rotation direction of the rotary shaft 1 is displayed downward.

  In FIG. 5, the torque fluctuation generated in the rotating shaft 1 during the reduced-cylinder operation of the in-line four-cylinder four-cycle engine is indicated by a broken line L2, but the torque fluctuation reducing device 10 is indicated by a solid line L1 in FIG. Then, a torque fluctuation L1 having a phase opposite to that of the torque fluctuation L2 generated in the rotating shaft 1 is generated.

  In the present embodiment, the rotating shaft 1 is a crankshaft of an in-line four-cylinder four-cycle engine in which two cylinders on both ends and four cylinders on the center side among the four cylinders are arranged with a phase difference of 180 degrees. During operation, the torque variation occurs once during one rotation of the crankshaft, and the planetary gear mechanism 30 causes the torque variation generated in the rotation shaft 1 when the rotation shaft 1 and the support shaft 21 of the weight member 20 are reduced. And a predetermined rotation ratio that generates a fluctuating torque having an opposite phase.

  FIG. 6 is an explanatory diagram for explaining the fluctuation torque by the torque fluctuation reduction device when the rotation angle of the rotary shaft is 0 degree and 45 degrees during the reduced cylinder operation, and FIG. 6 (a) and FIG. 6 (b). ) Respectively show states when the rotation position of the rotary shaft 1 is 0 degree and 45 degrees. FIG. 7 is an explanatory diagram for explaining the fluctuation torque by the torque fluctuation reduction device when the rotation angle of the rotary shaft is 90 degrees and 135 degrees during the reduced-cylinder operation, and FIG. 7 (a) and FIG. 7 (b) ) Show the states when the rotation angles of the rotary shaft 1 are 90 degrees and 135 degrees, respectively.

  6 and 7 schematically show the weight member 20, the support shaft driven gear 25, and the support shaft drive gear 26 of the torque fluctuation reducing device 10, and centrifugal force F <b> 1 acting on the weight member 20 is respectively shown in the weight member 20. This is indicated for the axis C2.

  As shown in FIG. 6 (a), when the rotation angle of the rotary shaft 1 is 0 degrees, for example, when the piston of the first cylinder of the in-line four-cylinder four-cycle engine is at top dead center during the reduced cylinder operation. The four weight members 20 are positioned so that the lines connecting the axis C2 of the support shaft 21 and the center of gravity C3 pass through the axis C1 of the rotary shaft 1, respectively.

  When the rotary shaft 1 is rotated once in the R1 direction around the axis C1, the support shaft driving gear 26 is rotated twice in the R1 direction around the axis C1 of the rotation shaft 1, and the support shaft driven gear 26 is weighted. The weight member 20 is rotated twice in the R2 direction around the axis C2 of the member 20 and once in the R1 direction around the axis C1 of the rotating shaft 1, and the weight member 20 is rotated in the R2 direction around the axis C2 of the weight member 20. It is rotated and rotated once in the R1 direction around the axis C1 of the rotating shaft 1.

  In the present embodiment, when the rotary shaft 1 is rotated once in the R1 direction around the axis C1, the weight member 20 is rotated twice in the direction opposite to the R1 direction around the axis C2 of the weight member 20 and rotated. Around the axis C1 of the shaft 1 is rotated once in the R1 direction, the rotation shaft 1 and the support shaft 21 of the weight member 20 are rotated in opposite directions, and the rotation shaft 1 and the support shaft 21 of the weight member 20 are The rotation ratio is set to 1: -1. In addition, when the rotation direction is the opposite direction, it is represented as minus (−).

  When the rotating shaft 1 is rotated around the axis C1, the centrifugal force F1 acts on the weight member 20 in the direction connecting the axis C2 of the support shaft 21 and the center of gravity C3, and acts on the weight member 20. Centrifugal force F <b> 1 is transmitted from the support shaft 21 of the weight member 20 to the weight support member 11.

  As shown in FIG. 6A, when the rotation angle of the rotary shaft 1 is 0 degree, the centrifugal force F1 acts on the weight member 20 in the direction connecting the axis C2 of the support shaft 21 and the center of gravity C3. And this centrifugal force F1 has only the force F1 which goes to the radial direction outer side of the rotating shaft 1, and the force of the circumferential direction of the rotating shaft 1 becomes zero.

  The centrifugal force F1 acting on each of the four weight members 20 transmitted to the weight support member 11 is equal to the centrifugal force F1 acting on the rotation shaft 1 because the forces F1 directed radially outward of the rotation shaft 1 cancel each other. The radial force due to the torque becomes zero, and the circumferential force of the rotating shaft 1 due to the centrifugal force F1 acting on the rotating shaft 1 becomes zero, so that a fluctuation torque is generated by the torque fluctuation reducing device 10 indicated by S1 in FIG. .

  When the rotating shaft 1 is rotated about the axis C1 and the rotating angle of the rotating shaft 1 is 45 degrees as shown in FIG. 6B, the weight member 20 has an axis C2 and a center of gravity of the supporting shaft 21, respectively. A centrifugal force F1 acts in a direction connecting the position C3, and this centrifugal force F1 is applied to a force F2 directed radially outward of the rotating shaft 1 and a circumferential force F3 opposite to the rotating direction of the rotating shaft 1. Disassembled.

  When the rotation angle of the rotary shaft 1 is 45 degrees, the centrifugal force F1 acting on each of the four weight members 20 transmitted to the weight support member 11 cancels out the force F2 directed radially outward of the rotary shaft 1 respectively. Accordingly, the radial force due to the centrifugal force F1 acting on the rotating shaft 1 becomes zero, while the circumferential force due to the centrifugal force F1 acting on the rotating shaft 1 is in the circumferential direction opposite to the rotating direction of the rotating shaft 1. Each of the forces F3 acts to generate a fluctuation torque by the torque fluctuation reduction device 10 indicated by S2 in FIG.

  When the rotation shaft 1 is further rotated around the axis C1 and the rotation angle of the rotation shaft 1 is 90 degrees as shown in FIG. 7A, the weight member 20 has an axis C2 of the support shaft 21 respectively. Centrifugal force F1 acts in the direction connecting the center of gravity position C3, and this centrifugal force F1 has only a circumferential force F1 opposite to the rotational direction of the rotary shaft 1, and the radial force of the rotary shaft 1 is It becomes zero.

  When the rotation angle of the rotation shaft 1 is 90 degrees, the centrifugal force F1 acting on each of the four weight members 20 transmitted to the weight support member 11 is the diameter of the rotation shaft 1 due to the centrifugal force F1 acting on the rotation shaft 1. While the direction force becomes zero, the circumferential force F1 in the direction opposite to the rotation direction of the rotation shaft 1 acts as the circumferential force due to the centrifugal force F1 acting on the rotation shaft 1, and is indicated by S3 in FIG. A fluctuation torque is generated by the torque fluctuation reduction device 10.

  When the rotation shaft 1 is further rotated around the axis C1 and the rotation angle of the rotation shaft 1 is 135 degrees as shown in FIG. 7B, the weight member 20 has an axis C2 of the support shaft 21 and Centrifugal force F1 acts in a direction connecting the center of gravity C3, and this centrifugal force F1 includes a force F2 directed radially inward of the rotating shaft 1 and a circumferential force F3 opposite to the rotating direction of the rotating shaft 1. Is broken down into

  When the rotation angle of the rotating shaft 1 is 135 degrees, the centrifugal force F1 acting on each of the four weight members 20 transmitted to the weight support member 11 cancels the force F2 directed radially inward of the rotating shaft 1 respectively. Accordingly, the radial force due to the centrifugal force F1 acting on the rotating shaft 1 becomes zero, while the circumferential force due to the centrifugal force F1 acting on the rotating shaft 1 is in the circumferential direction opposite to the rotating direction of the rotating shaft 1. Each of the forces F3 acts to generate a fluctuation torque by the torque fluctuation reduction device 10 indicated by S4 in FIG.

  Thus, when the rotating shaft 1 is rotated once in the R1 direction around the axis C1, the weight member 20 is rotated twice in the R2 direction around the axis C2 of the weight member 20, and the axis of the rotating shaft 1 is rotated. Centrifugal force F1 acting on the weight member 20 by rotating once around the C1 in the R1 direction is transmitted to the weight support member 11 via the support shaft 21 of the weight member 20, and as shown by a solid line L1 in FIG. The fluctuation reducing device 10 generates a fluctuation torque having a phase opposite to that of the torque fluctuation L2 generated in the rotating shaft 1 during the reduced cylinder operation.

  As a result, the spindle of the rotary shaft 1 and the weight member 20 has a predetermined rotation ratio that generates a fluctuation torque having a phase opposite to that of the torque fluctuation generated on the rotary shaft 1 that is the output shaft of the engine during the reduced-cylinder operation of the engine. By using the planetary gear mechanism 30 configured to be capable of interlocking with the engine 21, it is possible to reliably reduce torque fluctuations generated on the output shaft of the engine during the reduced-cylinder operation of the engine.

  On the other hand, in the torque fluctuation reducing device 10, the carrier 35 is released from the case 3 during the all cylinder operation of the engine, and none of the rotating elements of the planetary gear mechanism 30 is fixed, so that the rotating shaft 1 and the support shaft 21 of the weight member 20 The weight members 20 are rotatably supported by weight support members 11 that rotate integrally with the rotary shaft 1.

  The weight member 20 and the weight support member 11 that rotatably supports the weight member 20 function as a pendulum damper, and reduce torque fluctuations generated on the rotary shaft 1 due to the swinging motion of the weight member 20 when the engine is operating in all cylinders. It is supposed to be.

  In the present embodiment, the distance r1 between the shaft center C1 of the rotating shaft 1 and the shaft center C2 of the weight member 20 and the distance r2 between the shaft center C2 of the weight member 20 and the center of gravity C3 of the weight member 20 are all cylinder operation of the engine. It is set so as to effectively reduce the torque fluctuation sometimes generated on the rotating shaft 1.

  As a result, torque fluctuations generated on the output shaft of the engine during all-cylinder operation of the engine due to the swinging motion of the weight member 20 supported by the weight support member 11 that rotates integrally with the rotary shaft 1 during all-cylinder operation of the engine. Can be effectively reduced.

  In the present embodiment, the torque fluctuation reducing device 10 reliably reduces torque fluctuation in one mode that occurs during reduced-cylinder operation in an in-line four-cylinder four-cycle engine, and is different from the mode that occurs during all-cylinder operation. Although the torque fluctuation of the mode is effectively reduced, it can be applied to, for example, an in-line 6-cylinder 4-cycle engine configured to be able to switch between all-cylinder operation and reduced-cylinder operation.

  For example, when applied to an in-line 6-cylinder 4-cycle engine configured to be able to switch between all-cylinder operation and reduced-cylinder operation, fluctuations in the opposite phase with respect to torque fluctuations generated during reduced-cylinder operation in the in-line 6-cylinder 4-cycle engine The number of teeth of the rotating elements 31 and 32 constituting the planetary gear mechanism 30 of the torque fluctuation reducing device 10 and the number of teeth of the support shaft driven gear 25 and support shaft drive gear 26 are appropriately set and reduced so as to generate torque. The phase alignment between the torque fluctuation generated in the rotating shaft 1 during the cylinder operation and the fluctuation torque generated by the torque fluctuation reduction device 10 is appropriately adjusted.

  Further, the distance r1 between the axis C1 of the rotating shaft 1 and the axis C2 of the weight member 20 and the axis of the weight member 20 are effectively reduced so as to effectively reduce torque fluctuations generated during all cylinder operation in the in-line six-cylinder four-cycle engine. A distance r2 between the center C2 and the gravity center position C3 of the weight member 20 is set.

  As described above, in the torque fluctuation reducing device 10 according to the present embodiment, the weight support member 11 that rotates integrally with the rotating shaft 1 that transmits torque and the weight supporting member 11 that is disposed at equal intervals in the circumferential direction of the rotating shaft 1. The rotating shaft 1 and the supporting shaft so that the plurality of weight members 20 having the center of gravity C3 eccentric from the supporting shaft 21 rotatably supported by the member 11 and the rotating shaft 1 and the supporting shaft 21 have a predetermined rotation ratio. A planetary gear mechanism 30 configured to be capable of interlocking with the rotating shaft 21, and a first state in which the rotating shaft 1 and the supporting shaft 21 are interlocked using the planetary gear mechanism 30, and the rotating shaft 1 and the supporting shaft 21. A switching means 40 for switching between the second state and the non-interlocking state is provided.

  As a result, the planetary gear mechanism is configured such that the rotation shaft 1 and the support shaft 21 can be interlocked so as to have a predetermined rotation ratio that generates a fluctuation torque having a phase opposite to that of one mode of torque fluctuation generated on the rotation shaft 1. By using 30, in the first state in which the rotating shaft 1 and the support shaft 21 are interlocked using the planetary gear mechanism 30, torque fluctuations in one mode generated on the rotating shaft 1 can be reliably reduced.

  Further, in the second state in which the rotary shaft 1 and the support shaft 21 are not interlocked, the rotation is performed by the swing motion of the weight member 20 rotatably supported by the weight support member 11 that rotates integrally with the rotary shaft 1. It is possible to effectively reduce torque fluctuation in a mode different from the mode generated in the shaft 1.

  Therefore, even when the torque fluctuation generated on the rotating shaft 1 has two modes, the torque fluctuation generated on the rotating shaft 1 can be effectively reduced.

  Further, the switching means 40 is constituted by a brake 40 that fixes or releases a predetermined rotating element 35 of the planetary gear mechanism 30 to or from the case 3, so that a plurality of switching means 40 are provided when supplying hydraulic pressure to the hydraulic chamber 45 as the brake 40. When the hydraulic brake for fastening the friction plates 41 and 42 is used, the hydraulic chamber 45 can be fixed to the case 3, so that the first state and the first state can be compared with the case where the hydraulic clutch that rotates the hydraulic chamber is used. Switching control between the two states can be performed with good responsiveness, and torque fluctuations generated on the rotating shaft 1 can be effectively reduced. Further, unlike the case of using a hydraulic clutch in which the hydraulic chamber rotates, there is no need to provide a centrifugal balance chamber for canceling the centrifugal force acting on the hydraulic oil in the hydraulic chamber, and the rotary shaft 1 has a relatively simple configuration. The torque fluctuations generated in can be effectively reduced.

  In the torque fluctuation reduction device 10 according to the first embodiment, the rotation shaft 1 and the support shaft 21 of the weight member 20 have a predetermined rotation ratio that generates a fluctuation torque having an opposite phase to the torque fluctuation generated in the rotation shaft 1. The planetary gear mechanism 30 for interlocking the rotary shaft 1 and the support shaft 21 uses a double pinion type planetary gear mechanism. However, a single pinion type planetary gear mechanism can also be used.

  FIG. 8 is a cross-sectional view of the torque fluctuation reducing device according to the second embodiment of the present invention. The torque fluctuation reducing device 50 according to the second embodiment is the same as the torque fluctuation reducing device 10 according to the first embodiment except that a single pinion type planetary gear mechanism is used as the planetary gear mechanism. Are denoted by the same reference numerals and description thereof is omitted.

  As shown in FIG. 8, the torque fluctuation reducing device 50 according to the second embodiment also rotates and is supported by the weight support member 11 that rotates integrally with the rotary shaft 1 and the weight support member 11, respectively. The rotating shaft 1 is arranged such that the plurality of weight members 20 that are arranged at equal intervals in the circumferential direction of the shaft 1 and have a center of gravity C3 eccentric from the supporting shaft 21 and the rotating shaft 1 and the supporting shaft 21 have a predetermined rotation ratio. And a planetary gear mechanism 60 configured to be capable of interlocking with the support shaft 21.

  The planetary gear mechanism 60 is a single pinion type planetary gear mechanism, and includes a sun gear 61, three pinions 63 that mesh with the sun gear 61, a carrier 65 that rotatably supports the pinion 63, and a ring gear 62 that meshes with the pinion 63. It is configured.

  The ring gear 62 is connected to the rotary shaft 1 via a power transmission member 32 a formed integrally with the ring gear 62. The carrier 65 includes a pinion shaft 65 a that rotatably supports the pinion 63, and a carrier body 65 b that fixes and supports both ends of the pinion shaft 65 a, and is fixed to the case 3 disposed on the outer peripheral side of the rotating shaft 1. Or released from the case 3. A support shaft driving gear 26 is integrally formed with the sun gear 61.

  The torque fluctuation reducing device 50 also uses the planetary gear mechanism 60 to link the rotary shaft 1 and the support shaft 21 of the weight member 20 with each other and the rotary shaft 1 and the support shaft 21 of the weight member 20 are not interlocked. A brake 40 is provided as switching means for switching between the second state and the second state.

  The brake 40 is provided integrally with the plurality of rotation side friction plates 41 engaged with the carrier 65 of the planetary gear mechanism 60, the plurality of fixed side friction plates 42 engaged with the case 3, and the case 3. A cylinder 43, a piston 44, a hydraulic chamber 45, and a retaining plate 46 are provided. The carrier 65 is fixed to the case 3 and the planetary gear mechanism 60 is used to interlock the rotary shaft 1 and the support shaft 21 of the weight member 20. The first state and the second state in which the carrier 65 is released from the case 3 and the rotary shaft 1 and the support shaft 21 of the weight member 20 are not interlocked are switched.

  Also in this embodiment, the brake 40 is switched to the first state in which the carrier 65 is fixed to the case 3 and the planetary gear mechanism 60 is used to interlock the rotary shaft 1 and the support shaft 21 of the weight member 20 during the reduced cylinder operation. Then, the carrier 65 is released from the case 3 during the all-cylinder operation, and is switched to the second state in which the rotary shaft 1 and the support shaft 21 of the weight member 20 are not interlocked.

  When the rotary shaft 1 is rotated in the R1 direction around the axis C1 during the reduced-cylinder operation of the engine, the weight member 20 is rotated around the axis C2 of the support shaft 21 in the same direction as the R1 direction. The rotating shaft 1 is rotated in the R1 direction around the axis C1 of the rotating shaft 1, and the rotating shaft 1 and the support shaft 21 of the weight member 20 are rotated in the same direction.

  Also in the torque fluctuation reducing device 50, the planetary gear mechanism 60 generates a fluctuation torque having a phase opposite to that of the torque fluctuation generated on the rotating shaft 1 when the rotating shaft 1 and the support shaft 21 of the weight member 20 are operated in a reduced cylinder. The rotating shaft 1 and the support shaft 21 of the weight member 20 are interlocked so as to obtain a predetermined rotation ratio.

  In the present embodiment, the rotating shaft 1 and the support shaft 21 of the weight member 20 are reduced using the planetary gear mechanism 60 so as to reduce the torque fluctuation generated in the rotating shaft 1 during the reduced-cylinder operation of the in-line four-cylinder four-cycle engine. Interlocked so that the rotation ratio is 1: 1.

  The number of teeth of the rotating elements 61 and 62 constituting the planetary gear mechanism 60 of the torque fluctuation reducing device 50 and the number of teeth of the support shaft drive gear 25 and the support shaft driven gear 26 are appropriately set, and the rotation shaft is operated during the reduced cylinder operation. The phase alignment between the torque fluctuation generated in 1 and the fluctuation torque generated by the torque fluctuation reduction device 50 is adjusted as appropriate.

  Also in the torque fluctuation reducing device 50 according to the present embodiment, the rotary shaft 1 and the support shaft 21 have a predetermined rotation ratio that generates a fluctuation torque having an opposite phase to one mode of torque fluctuation generated on the rotary shaft 1. In the first state in which the rotating shaft 1 and the support shaft 21 are interlocked using the planetary gear mechanism 60 by using the planetary gear mechanism 60 configured to be able to be interlocked with each other, the torque of one mode generated on the rotating shaft 1 Variation can be reliably reduced.

  Further, in the second state in which the rotary shaft 1 and the support shaft 21 are not interlocked, the rotation is performed by the swing motion of the weight member 20 rotatably supported by the weight support member 11 that rotates integrally with the rotary shaft 1. It is possible to effectively reduce torque fluctuation in a mode different from the mode generated in the shaft 1.

  Therefore, even when the torque fluctuation generated on the rotating shaft 1 has two modes, the torque fluctuation generated on the rotating shaft 1 can be effectively reduced.

  The torque fluctuation reducing device 50 according to the second embodiment uses a single-pinion type planetary gear mechanism as the planetary gear mechanism 60, the ring gear 62 is connected to the rotary shaft 1, and the carrier 65 is fixed to the case 3 or the case 3 However, it is also possible to connect the carrier to the rotating shaft 1 and fix the ring gear to the case 3 or release it from the case 3.

  FIG. 9 is a sectional view of the torque fluctuation reducing device according to the third embodiment of the present invention. The torque fluctuation reducing device 70 according to the third embodiment is the same as the torque fluctuation reducing device 50 according to the second embodiment, and the carrier constituting the planetary gear mechanism is connected to the rotary shaft 1 and the ring gear is fixed to the case 3. Or, since it is the same except that it is released from the case 3, the same components are denoted by the same reference numerals, and description thereof is omitted.

  Also in the torque fluctuation reducing device 70 according to the third embodiment, as shown in FIG. 9, the weight support member 11 that rotates integrally with the rotating shaft 1 and the weight support member 11 are rotatably supported and rotated respectively. The rotating shaft 1 is arranged such that the plurality of weight members 20 that are arranged at equal intervals in the circumferential direction of the shaft 1 and have a center of gravity C3 eccentric from the supporting shaft 21 and the rotating shaft 1 and the supporting shaft 21 have a predetermined rotation ratio. And a planetary gear mechanism 80 configured to be capable of interlocking with the support shaft 21.

  The planetary gear mechanism 80 is a single pinion type planetary gear mechanism, and includes a sun gear 81, three pinions 83 that mesh with the sun gear 81, a carrier 85 that rotatably supports the pinion 83, and a ring gear 82 that meshes with the pinion 83. It is configured.

  The ring gear 82 is fixed to or released from the case 3 disposed on the outer peripheral side of the rotating shaft 1. The carrier 85 includes a pinion shaft 85a that rotatably supports the pinion 83, and a carrier body 85b that fixes and supports both ends of the pinion shaft 85a, and a power transmission member 85c formed integrally with the carrier body 85b. It is connected to the rotating shaft 1 via A support shaft drive gear 26 is integrally formed with the sun gear 81.

  The torque fluctuation reducing device 70 also uses the planetary gear mechanism 80 to link the rotating shaft 1 and the support shaft 21 of the weight member 20 with each other and the rotating shaft 1 and the support shaft 21 of the weight member 20 are not interlocked. A brake 40 is provided as switching means for switching between the second state and the second state.

  The brake 40 is provided integrally with the plurality of rotation-side friction plates 41 engaged with the ring gear 82 of the planetary gear mechanism 80, the plurality of fixed-side friction plates 42 engaged with the case 3, and the case 3. A cylinder 43, a piston 44, a hydraulic chamber 45, and a retaining plate 46 are provided, a ring gear 82 is fixed to the case 3, and the rotating shaft 1 and the support shaft 21 of the weight member 20 are interlocked using the planetary gear mechanism 80. The first state and the second state in which the ring gear 82 is released from the case 3 and the rotary shaft 1 and the support shaft 21 of the weight member 20 are not interlocked are switched.

  Also in this embodiment, the brake 40 is switched to the first state in which the ring gear 82 is fixed to the case 3 and the planetary gear mechanism 80 is used to interlock the rotary shaft 1 and the support shaft 21 of the weight member 20 during the reduced cylinder operation. Then, the ring gear 82 is released from the case 3 during the all-cylinder operation, and is switched to the second state in which the rotary shaft 1 and the support shaft 21 of the weight member 20 are not interlocked.

  When the rotary shaft 1 is rotated around the axis C1 in the R1 direction during the reduced-cylinder operation of the engine, the weight member 20 rotates around the axis C2 of the support shaft 21 in the R2 direction opposite to the R1 direction. At the same time, it is rotated in the R1 direction around the axis C1 of the rotating shaft 1, and the rotating shaft 1 and the support shaft 21 of the weight member 20 are rotated in opposite directions.

  Also in the torque fluctuation reducing device 70, the planetary gear mechanism 80 generates a fluctuation torque having a phase opposite to that of the torque fluctuation generated on the rotating shaft 1 when the rotating shaft 1 and the support shaft 21 of the weight member 20 are reduced in cylinder operation of the engine. The rotating shaft 1 and the support shaft 21 of the weight member 20 are interlocked so as to obtain a predetermined rotation ratio.

  In the present embodiment, the planetary gear mechanism 80 is used to reduce the torque fluctuation generated in the rotary shaft 1 during the reduced-cylinder operation of the in-line four-cylinder four-cycle engine. Interlocked so that the rotation ratio is 1: -1.

  The number of teeth of the rotating elements 81 and 82 constituting the planetary gear mechanism 80 of the torque fluctuation reducing device 70 and the number of teeth of the support shaft driving gear 25 and the support shaft driven gear 26 are appropriately set, and the rotating shaft is operated during the reduced cylinder operation. The phase alignment between the torque fluctuation generated in 1 and the fluctuation torque generated by the torque fluctuation reduction device 70 is adjusted as appropriate.

  Also in the torque fluctuation reducing device 70 according to the present embodiment, the rotary shaft 1 and the support shaft 21 have a predetermined rotation ratio that generates a fluctuation torque having an opposite phase to one mode of torque fluctuation generated on the rotary shaft 1. In the first state in which the planetary gear mechanism 80 is configured so that the rotary shaft 1 and the support shaft 21 are linked using the planetary gear mechanism 80, torque in one mode generated on the rotary shaft 1 is used. Variation can be reliably reduced.

  Further, in the second state in which the rotary shaft 1 and the support shaft 21 are not interlocked, the rotation is performed by the swing motion of the weight member 20 rotatably supported by the weight support member 11 that rotates integrally with the rotary shaft 1. It is possible to effectively reduce torque fluctuation in a mode different from the mode generated in the shaft 1.

  Therefore, even when the torque fluctuation generated on the rotating shaft 1 has two modes, the torque fluctuation generated on the rotating shaft 1 can be effectively reduced.

  The present invention is not limited to the illustrated embodiments, and various improvements and design changes can be made without departing from the scope of the present invention.

  As described above, according to the present invention, it is possible to effectively reduce the torque fluctuation even when the torque fluctuation generated on the rotating shaft has two modes. There is a possibility that the torque fluctuation generated in the output shaft of the engine is suitably used in the field of the vehicle manufacturing industry, for example, when there are two modes.

DESCRIPTION OF SYMBOLS 1 Rotating shaft 3 Case 10, 50, 70 Torque fluctuation reduction apparatus 11 Weight support member 20 Weight member 21 Support shaft 25 Support shaft driven gear 26 Support shaft drive gear 30, 60, 80 Planetary gear mechanism 31, 61, 81 Sun gear 32 , 62, 82 Ring gear 33, 34, 63, 83 Pinion 35, 65, 85 Carrier 40 Brake

Claims (4)

A rotating shaft that transmits torque, a weight support member that rotates integrally with the rotating shaft, and a plurality of shafts that are rotatably supported by the weight support member and that are arranged at equal intervals in the circumferential direction of the rotating shaft A plurality of weight members, each of which is provided in parallel to the rotation shaft and has a center of gravity position eccentric from a support shaft rotatably supported by the weight support member; and And a planetary gear mechanism that is coupled to the support shaft and configured to be able to interlock the rotation shaft and the support shaft so that the rotation shaft and the support shaft have a predetermined rotation ratio. A torque fluctuation reducing device,
Switching means for switching between a first state in which the rotating shaft and the support shaft are interlocked using the planetary gear mechanism and a second state in which the rotation shaft and the support shaft are not interlocked;
A torque fluctuation reducing device characterized by that. The switching means is constituted by a brake that fixes a predetermined rotating element of the planetary gear mechanism to the case or releases it from the case.
The torque fluctuation reducing device according to claim 1, wherein: It has an engine that can be switched between full-cylinder operation and reduced-cylinder operation,
The rotating shaft is an output shaft of the engine;
The switching means switches to the first state during reduced-cylinder operation of the engine;
The torque fluctuation reducing device according to claim 1 or 2, characterized in that It has an engine that can be switched between full-cylinder operation and reduced-cylinder operation,
The rotating shaft is an output shaft of the engine;
The switching means switches to the second state when all cylinders of the engine are operating.
The torque fluctuation reducing device according to claim 1 or 2, characterized in that

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