JP2007024297A - Power output device in two-wheeler - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a power output device capable of reducing unsprung weight in a two-wheeler. <P>SOLUTION: An output shaft 19 of an engine 9 and an input shaft 33 of a transmission 31 are arranged in series or parallel. The transmission 31 comprises a rotatable output shaft 41 arranged coaxially with the input shaft 33 and provided with a sun gear 43; a plurality of planetary gears 45 arranged around the sun gear 43; a plurality of support shafts 51 rotatably supporting the respective planetary gears 45 and integrally provided at the input shaft 33; a rotatable internal tooth gear 47 engaged with each planetary gear 45; a disc-like movable plate 53 supported to the input shaft 33 movably only in an axial direction; a plurality of tapered rollers 55 contacting the outer peripheral surface of the movable plate 53 and the outer peripheral surface of the internal tooth gear 47 to transmit the rotation of the movable plate 53 to the internal tooth gear 47; and a power transmission wheel 35 provided at the output shaft 41. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a power output device in a two-wheeled vehicle such as a scooter or a motorcycle (in this case, including a three-wheeled vehicle), and more specifically, when the rotation of an engine is transmitted to a rear wheel, the transmission is greatly decelerated. The present invention relates to a power output apparatus for a two-wheeled vehicle that can reduce the unsprung weight by omitting the final reduction gear mechanism near the axle of the rear wheel.

  For example, a schematic overall configuration of a motorcycle such as a scooter or a motorcycle is the configuration shown in FIG. 7 as disclosed in, for example, Japanese Patent Laid-Open No. 5-208694. That is, in brief description, a front wheel 5 operated by a handle 3 is provided on the front side of the body frame 1, and a rear wheel 7 is provided on the lower rear side of the body frame 1.

  In order to drive the rear wheel 7 by the engine 9, a drive unit 11 having the engine 9 is provided. The drive unit 11 is supported at the front end side by a support frame 13 that is swingably connected to the body frame 1, and the rear end side of the drive unit 11 is between the body frame 1 and the drive unit 11. Is supported by a cushion unit 15 interposed therebetween.

The configuration of the drive unit 11 is a configuration provided with a transmission 17 that is linked to the engine 9 as schematically shown in FIG. That is, in brief description, a drive V pulley 21 is attached to one end side of a crankshaft 19 that is an output shaft of the engine 9, and an intermediate shaft 25 provided close to an axle 23 that supports the rear wheel 7. Is attached with a driven V pulley 27. A V belt 29 is wound around the driving V pulley 21 and the driven V pulley 27. That is, a continuously variable transmission mechanism is constituted by the V pulley and the V belt. Further, a gear reduction mechanism that engages a plurality of gears 30 is provided between the intermediate shaft 25 and the axle 23.
JP-A-5-208694

  In the conventional configuration as described above, a continuously variable transmission mechanism is configured by using a V pulley and a V belt. Therefore, since the reduction ratio cannot be increased, the intermediate shaft 25 and the axle 23 are A gear reduction mechanism having a plurality of gears 30 in between is required. Therefore, not only the configuration around the axle is complicated, but also the weight in the vicinity of the axle is increased. There is a problem that the unsprung weight increases.

  The present invention has been made in view of the conventional problems as described above, and is a power output device for a two-wheeled vehicle including an engine and a transmission geared together with the engine, the output shaft of the engine and the speed change gear. The input shaft of the device is arranged in series or in parallel, and the transmission is arranged around the sun gear or the sun roller and a rotatable output shaft that is arranged coaxially with the input shaft and includes a sun gear or a sun roller. A plurality of planetary gears or planetary rollers, a plurality of support shafts rotatably supporting the planetary gears or planetary rollers and integrally provided on the input shaft, and meshing with the planetary gears or planetary rollers. A rotatable internal gear or roller, a disc-shaped movable plate supported only in the axial direction with respect to the input shaft, an outer peripheral surface of the movable plate, and the internal gear Comprises a plurality of tapered rollers that contact the outer peripheral surface of the roller and transmit the rotation of the movable plate to the internal gear or the roller, and a power transmission wheel provided on the output shaft of the transmission. It is characterized by that.

  Further, in the power output device in the two-wheeled vehicle, the contact region between the movable plate and the tapered portion of the roller is more than the region in which the rotation of the output shaft of the transmission is reversely rotated with respect to the rotation of the input shaft. The region in which the rotation of the output shaft is shifted in the normal rotation is longer.

  In addition, the present invention is a power output apparatus for a two-wheeled vehicle in which a fluctuation absorbing device for absorbing torque fluctuation is interposed between the output shaft of the transmission and the rear wheel drive shaft or between the engine output shaft and the transmission.

  According to the present invention having the above-described configuration, the output shaft can be reversely rotated, stopped, and rotated forward with respect to the rotation of the input shaft of the transmission, and the reduction ratio can be increased. Therefore, the conventional gear reduction mechanism is not required, and the unsprung weight can be reduced.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Since the overall configuration of a motorcycle such as a scooter or a motorcycle is well known, the description of the overall configuration of the motorcycle is omitted. In addition, the same reference numerals are given to components having the same functions as those of the conventional components described above, and redundant description is omitted.

  Referring to FIG. 1 schematically and conceptually, FIG. 1 illustrates a configuration in which an output shaft (crankshaft) 19 of an engine 9 and an input shaft 33 of a transmission 31 are arranged in series. . The output shaft 19 and the input shaft 33 are horizontally provided in a direction (left-right direction) orthogonal to the traveling direction of the two-wheeled vehicle (left direction in FIG. 1). In the above configuration, even if the output shaft 19 and the input shaft 33 are integrated, the output shaft 19 is connected, for example, via a torque fluctuation absorbing damper as a fluctuation absorbing device for absorbing torque fluctuation of the engine 9. And the input shaft 33 may be provided separately. A power transmission wheel 35 such as a chain sprocket is provided at the end of the output shaft of the transmission 31 (not shown by being integrally displayed with the input shaft 33 in FIG. 1). An annular endless belt 39 such as a chain or a timing belt is wound around the power transmission wheel and a power transmission wheel 37 such as a chain sprocket provided on the axle 23 of the rear wheel 7. The fluctuation absorber may be configured to be interposed between the output shaft of the transmission 31 and the drive shaft (axle) of the rear wheel 7.

  In the above configuration, the output shaft 19 of the engine 9, the input shaft 33 and the output shaft of the transmission 31 are arranged in series, and the dimensions in the front-rear direction are shortened. Can be made shorter.

  In FIG. 2, the output shaft 19 of the engine 9 and the input shaft 33 and output shaft of the transmission 31 are arranged in parallel in the front-rear direction, and the output shaft 19 and the input shaft 33 are appropriately arranged such as a chain and a gear mechanism. 1 schematically and schematically shows a configuration in which the power transmission mechanism is linked through a power transmission mechanism. In the configuration as described above, the output shaft 19 of the engine 9 and the input shaft 33 and output shaft of the transmission 31 are horizontal in the left-right direction, and the engine 9 and the transmission 31 are arranged in the front-rear direction. The width dimension in the left-right direction can be reduced.

  By the way, the structure of the transmission 31 is as shown conceptually and schematically in FIG. That is, the transmission 31 includes a casing (not shown), and the input shaft 33 that is appropriately linked to the output shaft 19 of the engine 9 is rotatably supported by the casing. Further, an output shaft 41 arranged coaxially with the input shaft 33 is rotatably supported on the casing, and a sun gear (or sun roller) 43 is integrally provided at an inner end portion of the output shaft 41. ing.

  A plurality of planetary gears (or planetary rollers) 45 are meshed around the sun gear 43, and an internal gear (or ring roller) meshed with each planetary gear 45 is disposed outside the plurality of planetary gears 45. 47 is rotatably provided. Each planetary gear 45 is rotatably supported by a plurality of support shafts 51 that are integrally attached to a support portion 49 provided on the input shaft 33. Each of the support shafts 51 extends in a direction parallel to the axis of the input shaft 33, and a disk-shaped movable plate 53 is supported on each support shaft 51 so as to be movable in the axial direction.

  The movable plate 53 is supported on the input shaft 33 so that the support shaft 51 is shortened and cannot be rotated with respect to the input shaft 33 and movable in the axial direction. It can be set as the structure made. In short, even if the movable plate 53 is arranged between the support portion 49 and the planetary gear 45 or on the opposite side of the planetary gear 45 with the support portion 49 in between, the movable plate 53 is not connected to the input shaft. Any configuration that can move in the axial direction without rotating with respect to 33 is acceptable. As described above, when the movable plate 53 is supported by the support shaft 51, the movable plate 53 is indirectly supported by the input shaft 33, which is substantially the same as the case where the movable plate 53 is supported by the input shaft 33. Are equal.

  In order to transmit the rotation of the movable plate 53 to the internal gear 47, a plurality of tapered rollers 55 (see FIG. 3 shows only one). Each of the rollers 55 is rotatably supported on the casing so as not to freely revolve (roll) around the movable plate 53 and the internal gear 47.

  The diameters of the predetermined range in the axial direction near the contact portion where the roller 55 contacts the outer peripheral surface of the internal gear 47 are formed to be equal. A region where the roller 55 comes into contact with the outer peripheral surface of the movable plate 53 is formed in a tapered shape having a larger diameter as the roller 55 approaches the internal gear 47. Therefore, when the contact position between the movable plate 53 and the roller 55 changes in the axial direction of the roller 55, the rotational speed transmitted to the internal gear 47 is changed even if the rotational speed of the movable plate 53 is constant. It is what is done.

  In the configuration as described above, as shown in FIG. 3, when the movable plate 53 is in contact with a position close to the small diameter end of the tapered portion of the roller 55 (hereinafter referred to as a neutral position), the input shaft 33 Is rotated in the direction of arrow A, the movable plate 53 is integrally rotated in the same direction, and each planetary gear 45 revolves around the sun gear 43 in the same direction. Since the roller 55 in contact with the movable plate 53 is rotated in the arrow B direction, the internal gear 47 in contact with the roller 55 rotates in the same direction as the rotation direction of the input shaft 33.

  At this time, the contact position (neutral position) of the movable plate 53 with respect to the roller 55 is a tapered portion, and the diameter of the roller 55 is smaller than the diameter of the roller 55 at the contact position between the internal gear 47 and the roller 55. Position. Accordingly, the rotation of the movable plate 53 is accelerated and transmitted to the internal gear 47. When the movable plate 53 is in contact with the neutral position of the tapered portion of the roller 55, the rotational speed due to the revolution of the planetary gear 45 and the rotational speed of the internal gear 47 are equal. The internal gear 47 rotates in synchronization with the rolling (revolution) of the sun gear 43 and the sun gear 43 is stopped.

  Next, as shown in FIG. 4, when the contact position of the movable plate 53 with respect to the roller 55 is moved to a position where the diameter of the tip of the tapered portion of the roller 55 is smaller (hereinafter referred to as a reverse rotation position), Since the tapered portion in the neutral position has a smaller diameter, the internal gear 47 is rotated at a higher speed. That is, the rotation of the internal gear 47 is faster than the rotation speed due to the revolution of the planetary gear 45, so that the sun gear 43 is caused to differ by the difference between the rotation speed of the internal gear 47 and the rotation speed due to the revolution of the planetary gear 45. It will rotate in the direction of arrow C. That is, the rotation direction of the input shaft 33 (arrow A direction) and the rotation direction of the output shaft 41 (arrow C direction) are opposite to each other.

  Next, as shown in FIG. 5, when the contact position of the movable plate 53 is changed from the neutral position to the large diameter side of the taper portion of the roller 55 (position on the positive rotation side), the taper portion at the contact position is changed. Since the diameter is larger than the diameter of the tapered portion at the neutral position, the rotational speed of the internal gear 47 is lower than the rotational speed when the movable plate 53 is positioned at the neutral position. Therefore, the sun gear 43 is rotated in the revolution direction of the planetary gear 45 due to the difference between the rotation speed of the internal gear 47 and the rotation speed due to the revolution of the planetary gear 45, and the output shaft 41 is rotated in the direction of arrow D at a low speed. Will be rotated.

  Thereafter, as shown in FIG. 6, when the movable plate 53 is further moved to the larger diameter side of the tapered portion of the roller 55, the rotational speed of the internal gear 47 becomes lower, and the revolution speed of the planetary gear 45 is reduced. Since the difference becomes larger, the rotation of the output shaft 41 in the direction of the arrow D becomes faster. As already understood, the taper portion in the roller 55 is a region on the forward rotation position side from the neutral position to the large rotation side rather than the region dimension on the reverse rotation position side from the neutral position to the small diameter front end side. The dimensions are long.

  As understood from the above description, the transmission 31 can shift the rotation of the output shaft 41 to the reverse rotation, stop, and forward rotation with respect to the rotation of the input shaft 33, and the output shaft 41. The forward rotation can be steplessly changed from a low speed rotation to a high speed rotation. The reduction ratio can be increased by increasing the taper (inclination angle) of the tapered portion of the roller 55.

  That is, when the rotation of the engine is reduced and transmitted to the rear wheel 7 in a two-wheeled vehicle, for example, a large speed change can be made from a stopped state to a high-speed rotation. Therefore, conventionally, the reduction gear 30 provided near the rear wheel 7 is provided. It becomes unnecessary. Accordingly, the unsprung weight can be reduced. Therefore, the followability of the rear wheels of the two-wheeled vehicle to the road surface unevenness is improved and the cushion unit absorbs the unevenness sharply, and the adverse effect of the uneven portions on the body frame of the two-wheeled vehicle is suppressed and the riding comfort is improved. To do.

FIG. 2 is an arrangement explanatory diagram conceptually and schematically showing an arrangement relationship between an engine and a transmission in a motorcycle. FIG. 2 is an arrangement explanatory diagram conceptually and schematically showing an arrangement relationship between an engine and a transmission in a motorcycle. It is action explanatory drawing which showed notionally and schematically the structure of the transmission. It is action explanatory drawing which showed notionally and schematically the structure of the transmission. It is action explanatory drawing which showed notionally and schematically the structure of the transmission. It is action explanatory drawing which showed notionally and schematically the structure of the transmission. It is explanatory drawing which showed the external appearance of the conventional two-wheeled vehicle roughly. It is a schematic explanatory drawing of the transmission device of the conventional two-wheeled vehicle.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Body frame 5 Front wheel 7 Rear wheel 9 Engine 11 Drive unit 15 Cushion unit 17, 31 Transmission 19 Crankshaft (output shaft)
21 Drive V Pulley 27 Driven Pulley 33 Input Shaft 35, 37 Power Transmission Wheel 41 Output Shaft 43 Sun Gear (Sun Roller)
45 Planetary Gear (Planetary Roller)
47 Internal gear (ring roller)
51 Support shaft 53 Movable plate 55 Roller

Claims (3)

  A power output device for a motorcycle including an engine and a transmission geared to the engine, wherein the output shaft of the engine and the input shaft of the transmission device are arranged in series or in parallel. A rotatable output shaft arranged coaxially with the input shaft and provided with a sun gear or sun roller, a plurality of planet gears or planet rollers arranged around the sun gear or sun roller, and the planet gears or planets. A plurality of support shafts that rotatably support the rollers and provided integrally with the input shaft; a rotatable internal gear or roller meshed with each planetary gear or each planetary roller; and the input shaft A disc-shaped movable plate that is supported so as to be movable only in the axial direction, and contact the outer peripheral surface of the movable plate and the outer peripheral surface of the internal gear or roller to rotate the movable plate. Or a plurality of rollers for tapered freely transmitted to the roller, the power output of the two-wheeled vehicle, characterized in that it comprises a power transmission wheel provided on the output shaft of the transmission device.   2. The power output apparatus for a motorcycle according to claim 1, wherein a contact region between the movable plate and the tapered portion of the roller shifts the rotation of the output shaft of the transmission to a reverse rotation with respect to the rotation of the input shaft. The power output apparatus for a two-wheeled vehicle is characterized in that a region in which the rotation of the output shaft is shifted in a positive direction is longer than a region.   A power output device for a two-wheeled vehicle in which a fluctuation absorbing device for absorbing torque fluctuation is interposed between an output shaft and a rear wheel drive shaft of the transmission or between an engine output shaft and the transmission.

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