JP2019002479A - Power transmission device for vehicle - Google Patents

Abstract

To adjust a position of center of gravity of an eccentric disc of a crank-type power transmission device without needing a balance weight.SOLUTION: An eccentric disc 19 is composed of a first part 51 positioned at an eccentric side and a second side part 52 positioned at an anti-eccentric side, and as the second part 52 and a part 53 of a ring gear connected to the first part 51 are composed of a material of high specific gravity and high strength with respect to a material of the first part 51, a position of center of gravity G of the eccentric disc 19 is adjusted to a center O1 side of the ring gear 19b without disposing a special balance weight, and generation of vibration can be prevented while reducing a size and a weight of the eccentric disc 19. Further the strength can be secured by making the whole ring gear 19b stranding over both of the first part 51 and the second part 52, by using the material of high specific gravity and strength.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a crank-type power transmission device for a vehicle, and more particularly to a structure of an eccentric disk that reciprocates a connecting rod that transmits driving force.

  The eccentric member (eccentric disc) of the crank type power transmission device for a vehicle is divided into two semicircular eccentric member halves, and these two eccentric member halves are integrated with two bolts. The one that is fastened and assembled is known from the following Patent Document 1.

  Further, in a crank-type vehicle power transmission device including an eccentric disk that is fitted to an outer periphery of an eccentric cam fixed in an eccentric state on an input shaft so as to be relatively rotatable in an eccentric state, the crankshaft power transmission device is radially outward from the non-eccentric side of the eccentric disk Even if the gear ratio is changed by rotating the eccentric disk relative to the eccentric cam by changing the gear ratio by projecting the balance weight and making the center of gravity of the eccentric disk coincide with the center of the eccentric cam, the eccentric disk Japanese Patent Application Laid-Open Publication No. 2004-228688 discloses a technique that suppresses the vibration of the input shaft so that the amount of eccentricity up to the center of gravity does not change.

Special table 2011-518290 gazette WO2013 / 008624 Publication

  However, the device described in Patent Document 1 does not have the technical idea of adjusting the position of the center of gravity of the eccentric member (eccentric disc) to prevent the occurrence of vibration. Further, the device described in Patent Document 2 has a problem in that the weight of the eccentric disc and the outer diameter are increased because the balance weight is protruded radially outward from the eccentric disc to adjust the position of the center of gravity.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to make it possible to adjust the position of the center of gravity of an eccentric disk of a crank type power transmission device without requiring a balance weight.

  To achieve the above object, according to the invention described in claim 1, an eccentric cam fixed in an eccentric state on the outer periphery of an input shaft connected to a drive source, and an eccentric state in the outer periphery of the eccentric cam An eccentric disk supported so as to be relatively rotatable, a transmission shaft coaxially fitted inside the input shaft, a pinion fixed to the transmission shaft, and formed on the eccentric disk and meshed with the pinion. A ring gear, a one-way clutch provided on the outer periphery of the output shaft, and a connecting rod connected to both ends of the eccentric disk and the one-way clutch to reciprocate, the rotation of the input shaft being controlled by the connecting rod and the one-way The transmission is intermittently transmitted to the output shaft via a clutch, and the eccentric disk is rotated around the eccentric cam by the speed change shaft. A vehicular power transmission device that changes a gear ratio by changing an eccentric amount of the eccentric disk with respect to an axis of an input shaft, wherein the eccentric disk is a first portion located on an eccentric side and a first part located on an opposite eccentric side. The second portion and a part of the ring gear connected to the first portion are made of a material having a high specific gravity and a high strength with respect to the material of the first portion. A vehicle power transmission device is proposed.

  According to the invention described in claim 2, in addition to the configuration of claim 1, the material of the first part is an aluminum-based material, and the material of the second part and a part of the ring gear is an iron-based material. A vehicle power transmission device characterized by being made of a material is proposed.

  According to the invention described in claim 3, in addition to the structure of claim 1 or 2, the first part and the second part are integrally fastened by a bolt, and the head of the bolt is The vehicle power transmission device is disposed in a space formed between a recess formed by cutting out the outer peripheral surface of the first portion and an inner race of a bearing fitted to the outer peripheral surface of the first portion. Is proposed.

  According to the invention described in claim 4, in addition to the configuration of claim 1 or claim 2, the second part and a part of the ring gear are cast into the first part. A vehicle power transmission device is proposed.

  According to a fifth aspect of the present invention, in addition to the configuration of any one of the first to fourth aspects, the first portion includes a lightening hole, and the vehicle power transmission is characterized in that A device is proposed.

  The ball bearing 22 of the embodiment corresponds to the bearing of the present invention, and the engine E of the embodiment corresponds to the drive source of the present invention.

  According to the first aspect of the present invention, when the eccentric disk rotates eccentrically with the input shaft, the connecting rod having one end connected to the eccentric disk reciprocates, and when the connecting rod moves in one direction, the one-way clutch is engaged. When the connecting rod moves in the other direction, the one-way clutch is disengaged, so that the rotation of the input shaft is shifted and transmitted to the output shaft. When the eccentric amount of the eccentric disk is changed via the pinion and the ring gear by the transmission shaft, the reciprocating stroke of the connecting rod is changed to change the gear ratio of the power transmission device.

  The eccentric disk is composed of a first part located on the eccentric side and a second side part located on the anti-eccentric side, and the second part and a part of the ring gear connected to the first part are used as the material of the first part. On the other hand, because it is made of a material with high specific gravity and high strength, the center of gravity of the eccentric disk is adjusted to the center side of the ring gear without providing a special balance weight, and vibration is generated while reducing the weight and size of the eccentric disk. In addition, the entire ring gear straddling both the first part and the second part can be made of a material having a high specific gravity and a high strength to ensure the strength.

  According to the invention described in claim 2, in addition to the structure of claim 1, the material of the first portion is an aluminum-based material, and the material of the second portion and part of the ring gear is an iron-based material. Therefore, the strength of the ring gear can be ensured while easily adjusting the position of the center of gravity of the eccentric disk.

  Further, according to the configuration of claim 3, since the first part and the second part are integrally fastened by the bolt, the first part and the second part can be disassembled to facilitate the assembly to the eccentric cam, Moreover, since the head of the bolt is disposed in a space formed between the recess formed by cutting out the outer peripheral surface of the first portion and the inner race of the bearing that fits into the outer peripheral surface of the first portion, Not only can the first part and the second part be fastened while avoiding the head from interfering with the inner race of the bearing, but also the weight of the first part can be reduced by the recess to easily adjust the position of the center of gravity of the eccentric disk.

  According to the fourth aspect of the present invention, since the second portion and a part of the ring gear are cast into the first portion, the first portion and the second portion are strengthened without requiring a fastening member such as a bolt. Can be integrated.

  According to the configuration of the fifth aspect, since the first portion has the lightening hole, not only can the first portion be reduced in weight to easily adjust the position of the center of gravity of the eccentric disc, but also the total weight of the eccentric disc can be reduced. Can do.

It is a longitudinal cross-sectional view of a continuously variable transmission. (First embodiment) FIG. 2 is a sectional view taken along line 2-2 of FIG. (First embodiment) It is a single figure of an eccentric disk. (First embodiment) It is a figure which shows the relationship between the eccentric amount of an eccentric disk, and a gear ratio. (First embodiment) It is a single figure of an eccentric disk. (Second Embodiment)

First embodiment

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS.

  As shown in FIGS. 1 and 2, an input shaft 12 and an output shaft 13 are supported in parallel with each other on a support frame 11 of a crank type continuously variable transmission T for an automobile, and are connected to an engine E. The rotation of the shaft 12 is transmitted to drive wheels (not shown) via the eight transmission units 14..., The output shaft 13 and a differential gear (not shown).

  Since the structure of the eight transmission units 14 is substantially the same, the structure will be described below with one transmission unit 14 as a representative.

  A transmission shaft 15 sharing the axis L is disposed inside the hollow input shaft 12, and the transmission shaft 15 is divided into nine in the direction of the axis L via ten needle bearings 16 on the outer periphery of the transmission shaft 15. The eccentric cams 17 are rotatably supported. A total of nine eccentric cams 17 of the eight transmission units 14 are integrally coupled by a plurality of bolts (not shown), and the inner peripheral portion of the nine eccentric cams 17 is substantially the input shaft. 12 is configured.

  A pair of adjacent eccentric cams 17 and 17 are arranged on the radially inner side of the pair of circular cam portions 17a and 17a having a center O1 that is eccentric by a distance d with respect to the axis L of the input shaft 12, and the cam portions 17a and 17a. And a formed crescent-shaped guide portion 17b. Eight pinions 18 are integrally formed on the outer periphery of the transmission shaft 15 sharing the axis L with the input shaft 12, and each pinion 18 is a notch in the crescent-shaped guide portion 17 b of the eccentric cams 17, 17. It is stored in the part 17c. The phases of the cam portions 17a, 17a of the eccentric cams 17, 17 of each transmission unit 14 are shifted from each other by 45 °.

  As shown in FIGS. 2 and 3, a pair of eccentric recesses 19 a formed on both end surfaces in the axis L direction of the disc-shaped eccentric disk 19 are formed on the outer peripheral surfaces of the cam portions 17 a and 17 a of the eccentric cams 17 and 17. 19a is rotatably supported via a pair of needle bearings 20 and 20. The center O1 of the eccentric recesses 19a and 19a (that is, the center O1 of the cam portions 17a and 17a of the eccentric cams 17 and 17) is shifted from the center O2 of the eccentric disk 19 by a distance d. That is, the distance d between the axis L of the input shaft 12 and the center O1 of the cam portions 17a and 17a of the eccentric cams 17 and 17, the center O1 of the cam portions 17a and 17a of the eccentric cams 17 and 17, and the center O2 of the eccentric disc 19 The distance d between them is the same.

  The tooth tips of the ring gear 19b formed so as to communicate between the bottoms of the pair of eccentric recesses 19a, 19a of the eccentric disk 19 slidably contact the outer peripheral surfaces of the guide portions 17b of the eccentric cams 17, 17. Then, the pinion 18 of the transmission shaft 15 exposed from the opening 12a (see FIG. 2) of the input shaft 12 meshes with the ring gear 19b of the eccentric disk 19. A large end 21 a of a connecting rod 21 is supported on the outer periphery of the eccentric disk 19 via a ball bearing 22.

  As shown in FIGS. 1 and 2, the one-way clutch 23 provided on the outer periphery of the output shaft 13 includes a ring-shaped swing link 25 connected to the small end portion 21 b of the connecting rod 21 via a pin 24, A ring-shaped outer member 26 fixed to the inner periphery of the swing link 25, a ring-shaped inner member 27 disposed inside the outer member 26 and fixed to the output shaft 13, and an inner peripheral surface of the outer member 26 And a plurality of rollers 29 arranged in a wedge-like space formed between the inner member 27 and the outer peripheral surface of the inner member 27 and urged by a plurality of springs 28.

  At the shaft end of the input shaft 12 opposite to the engine E, the shift shaft 15 is rotated relative to the input shaft 12 to increase or decrease the amount of eccentricity ε of the eccentric disk 19, thereby shifting the speed of the continuously variable transmission T. A speed change actuator 30 for changing the ratio is provided.

  As shown in FIG. 1, the support frame 11 that supports the eight transmission units 14... Has a central frame 31 that is located in the center in the axis L direction, and a pair of side frames 32 and 33 that are located on both sides in the axis L direction. The four transmission units 14 are arranged between the central frame 31 and one side frame 32 located on the engine E side, and the other side frame located on the central frame 31 and the anti-engine E side. The four transmission units 14...

  The central frame 31 is an iron plate-like member and includes two bearing support holes 31a and 31b formed on the input shaft 12 side and the output shaft 13 side on both sides in the longitudinal direction.

  The side frame 32 located on the engine E side is basically a cast member made of aluminum alloy in a bowl shape, and a bearing holder 38, which is a plate member made of iron, is embedded in the center by casting. Bearing support holes 38a and 38b are formed on the input shaft 12 side and the output shaft 13 side of the bearing holder 38, respectively.

  The side frame 33 located on the side opposite to the engine E is also a cast member that is basically formed of an aluminum alloy in a bowl shape, and a bearing holder 39 that is an iron plate-like member is embedded in the center thereof by casting. The structures of the side frame 33 and the bearing holder 39 located on the side opposite to the engine E are symmetrical with respect to the side frame 32 side and the bearing holder 38 located on the engine E side described above, and therefore overlap. Description is omitted.

  The eccentric cam 17 fixed to the center portion of the input shaft 12 in the axis L direction is supported by the bearing support hole 31a of the center frame 31 via the center support bearing 34, and both ends of the input shaft 12 in the axis L direction are The bearing holders 38 and 39 of the pair of side frames 32 and 33 are supported by bearing support holes 38a and 39a via shaft end support bearings 36 and 36, respectively. Similarly, the center portion of the output shaft 13 in the axis L direction is supported by the bearing support hole 31b of the center frame 31 via the center support bearing 35, and both ends of the output shaft 13 in the axis L direction are a pair of sides. The bearings 38 and 39 of the side frames 32 and 33 are supported by bearing support holes 38b and 39b via shaft end support bearings 37 and 37, respectively.

  Then, the subframe is assembled by fastening the central frame 31 and the pair of side frames 32, 33 together with bolts 40, and the subassembly is fastened inside the transmission case 42 with bolts 41 passing through the central frame 31. Is done.

  Next, the operation of one transmission unit 14 of the continuously variable transmission T will be described.

  As is clear from FIGS. 2 and 4A to 4D, when the center O2 of the eccentric disk 19 is eccentric with respect to the axis L of the input shaft 12, the input shaft 12 is rotated by the engine E. As the large end portion 21a of the connecting rod 21 rotates eccentrically around the axis L, the connecting rod 21 reciprocates.

  As a result, when the connecting rod 21 is reciprocated and pulled to the left in the figure, the outer member 26 together with the swing link 25 swings counterclockwise in FIG. 2, and the roller 29 urged by the springs 28. ... Bite into a wedge-shaped space between the outer member 26 and the inner member 27, and the outer member 26 and the inner member 27 are coupled via the rollers 29, so that the one-way clutch 23 is engaged and the connecting rod 21 The movement is transmitted to the output shaft 13. On the other hand, when the connecting rod 21 is reciprocated and pushed to the right side in the figure, the outer member 26 swings in the clockwise direction in FIG. 2 together with the swing link 25, and the roller 29. When the outer member 26 and the inner member 27 are pushed out from the wedge-shaped space between the member 26 and the inner member 27 and slip each other, the one-way clutch 23 is disengaged and the movement of the connecting rod 21 is transmitted to the output shaft 13. It will not be done.

  Thus, since the rotation of the input shaft 12 is transmitted to the output shaft 13 for a predetermined time while the input shaft 12 rotates once, the output shaft 13 rotates intermittently when the input shaft 12 rotates continuously. The eccentric amounts ε of the eccentric discs 19 of the eight transmission units 14 are all the same, but the phases in the eccentric direction are shifted from each other by 45 °, so that the eight transmission units 14. By alternately transmitting the rotation to the output shaft 13, the output shaft 13 rotates continuously.

  At this time, the larger the eccentric amount ε of the eccentric disk 19 is, the larger the reciprocating stroke of the connecting rod 21 is, and the one rotation angle of the output shaft 13 is increased, and the gear ratio of the continuously variable transmission T is decreased. Conversely, the smaller the eccentric amount ε of the eccentric disk 19, the smaller the reciprocating stroke of the connecting rod 21, the smaller the rotation angle of the output shaft 13, and the higher the gear ratio of the continuously variable transmission T. When the eccentric amount ε of the eccentric disk 19 becomes zero, the connecting rod 21 stops moving even when the input shaft 12 rotates, so the output shaft 13 does not rotate, and the gear ratio of the continuously variable transmission T is maximum ( Infinity).

  When the transmission shaft 15 does not rotate relative to the input shaft 12, that is, when the input shaft 12 and the transmission shaft 15 rotate at the same speed, the transmission ratio of the continuously variable transmission T is maintained constant. When the transmission shaft 15 is rotated relative to the input shaft 12 by the transmission actuator 30, the eccentric recesses 19 a and 19 a of the eccentric disk 19 in which the ring gear 19 b is engaged with the pinion 18 of each transmission unit 14 are integrated with the input shaft 12. The eccentric cams 17 and 17 are guided and rotated by the cam portions 17a and 17a, and the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 changes.

  FIG. 4A shows a state where the speed ratio is minimum (speed ratio: TD). At this time, the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 is the axis L of the input shaft 12. To a center O1 of the eccentric cams 17, 17 and a maximum value equal to 2d, which is the sum of the distance d from the center O1 of the eccentric cams 17, 17 to the center O2 of the eccentric disk 19. When the transmission shaft 15 rotates relative to the input shaft 12, the eccentric disk 19 rotates relative to the eccentric cams 17, 17 integrated with the input shaft 12, so that FIG. 4B and FIG. As shown, the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 gradually decreases from the maximum value 2d, and the gear ratio increases. When the transmission shaft 15 further rotates relative to the input shaft 12, the eccentric disk 19 further rotates relative to the eccentric cams 17, 17 integrated with the input shaft 12, as shown in FIG. Finally, the center O2 of the eccentric disk 19 overlaps the axis L of the input shaft 12, the eccentricity ε becomes zero, and the speed ratio becomes maximum (infinite) (speed ratio: UD). Transmission is interrupted.

  Next, the structure of the eccentric disk 19 will be described in detail with reference to FIG.

  The eccentric disk 19 is divided into two at a straight line L3 that passes through the center O1 of the ring gear 19b (that is, the center O1 of the eccentric cam 17) and is orthogonal to the straight line L2 that connects the center O1 of the ring gear 19b and the center O2 of the eccentric disk 19. ing. The eccentric side of the eccentric disc 19 divided into two, that is, the portion on the center O2 side, constitutes a relatively large first portion 51, and the opposite eccentric side of the divided eccentric disc 19, ie, the side opposite to the center O2. This part constitutes a relatively small second part 52. The first portion 51 is made of an aluminum-based material having a relatively low specific gravity and low strength, and the second portion 52 is made of an iron-based material having a relatively high specific gravity and high strength. Further, the ring gear 19b of the eccentric disk 19 has a half-circumferential portion on the anti-eccentric side formed in the first portion 51, and the half-circular portion on the eccentric side is constituted by a part 53 of the ring gear which is a separate member. The part 53 is also made of the same high specific gravity and high strength iron-based material as the second part 52. In the first portion 51, two circular lightening holes 51a and 51a are formed.

  Two recesses 51b, 51b cut out in a substantially triangular shape are formed on the outer peripheral surface of the first portion 51, and two shaft holes 51c, 51b, 51b are formed in parallel with the straight line L2 from the two recesses 51b, 51b. 51 c is formed toward the second portion 52. The second portion 52 is formed with two female screw holes 52a and 52a extending coaxially with the shaft holes 51c and 51c of the first portion. Then, the shaft portions 54a, 54a of the two bolts 54, 54 pass through the shaft holes 51c, 51c of the first portion 51 and are screwed into the female screw holes 52a, 52a of the second portion 52. And the 2nd part 52 is couple | bonded together.

  The ball bearing 22 that supports the large end portion 21 a of the connecting rod 21 on the outer periphery of the eccentric disk 19 includes an inner race 22 a that is press-fitted into the outer periphery of the eccentric disk 19, and two recesses of the first portion 51 of the eccentric disk 19. Spaces α are formed between 51b and 51b and the inner race 22a of the ball bearing 22b, and the heads 54b and 54b of the two bolts 54 and 54 are accommodated in these spaces α.

  The eccentric disk 19 of the present embodiment is configured by combining an eccentric first portion 51 made of a low specific gravity aluminum-based material and an anti-eccentric second portion 52 made of a high specific gravity iron-based material. Therefore, even when a plurality of eccentric cams 17 are integrated with the input shaft 12, the eccentric discs 19 can be assembled to the outer periphery of the eccentric cams 17 without any trouble, and the eccentric disc 19 is eccentric. The center of gravity position G of the eccentric disc 19 is increased from the center O2 side of the eccentric disc 19 without increasing the size by projecting a special balance weight from the side and without increasing the weight of the eccentric disc 19 by the balance weight. It can be moved to the second portion 52 side to coincide with the center (center of the eccentric cam 17) O1 of the ring gear 19b.

  FIG. 4A shows the state of the minimum speed ratio (speed ratio: TD) in which the eccentric amount ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 becomes the maximum value 2d. The eccentric direction of the center O1 of the eccentric cam 17 with respect to the axis L (upward in the figure) and the eccentric direction of the center O2 of the eccentric disk 19 with respect to the center O1 of the eccentric cam 17 (upward in the figure) are the same direction. At this time, the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 17.

  FIG. 4D shows a maximum gear ratio state (gear ratio: UD) in which the amount of eccentricity ε of the center O2 of the eccentric disk 19 with respect to the axis L of the input shaft 12 becomes the minimum value zero. The eccentric direction of the center O1 of the eccentric cam 17 with respect to the axis L (rightward in the figure) is opposite to the eccentric direction of the center O2 of the eccentric disk 19 with respect to the center O1 of the eccentric cam 17 (leftward in the figure). At this time, the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 17.

  That is, according to the present embodiment, since the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 17, the eccentric disk 19 is moved around the center O1 of the eccentric cam 17 in accordance with the change of the gear ratio. Even if it rotates eccentrically, the gravity center position G of the eccentric disk 19 always exists on the center O1 of the eccentric cam 17, and the distance between the axis L of the input shaft 12 and the gravity center position G of the eccentric disk 19 changes from a constant value d. Never do.

  If it is assumed that the distance from the axis L of the input shaft 12 to the center of gravity G of the eccentric disk 19 changes as the speed ratio changes, the inertia moment of inertia of the eccentric disk 19 around the input shaft 12 increases the distance. Therefore, the rotation load of the input shaft 12 may fluctuate with the change of the gear ratio, and vibration may occur. However, according to the present embodiment, even if the gear ratio is changed, the inertia moment of the eccentric disk 19 around the input shaft 12 does not change, so that the vibration of the input shaft 12 can be minimized.

  Since the eccentric disk 19 is supported by the eccentric cam 17 so as to be relatively rotatable, if the center of gravity G of the eccentric disk 19 does not coincide with the center O1 of the eccentric cam 17, the rotational speed of the input shaft 12 increases. Alternatively, when it decreases, the eccentric disk 19 tries to rotate relative to the eccentric cam 17 with inertial force, and the moment is transmitted from the ring gear 19b of the eccentric disk 19 to the transmission actuator 30 via the pinion 18, so that the transmission actuator 30 Unnecessary torque may act on the gears, and the accuracy of the shift control may be reduced.

  However, according to the present embodiment, since the center of gravity G of the eccentric disk 19 coincides with the center O1 of the eccentric cam 17, even if the rotational speed of the input shaft 12 increases or decreases, the eccentric disk 19 is inertial. A moment that causes relative rotation around the eccentric cam 17 by force is not generated, thereby preventing unnecessary torque from acting on the speed change actuator 30 and ensuring the accuracy of speed change control.

  Further, if the ring gear 19b is formed directly on the first portion 51 made of a relatively low strength aluminum-based material, there is a problem that the durability of the ring gear 19b is insufficient due to insufficient strength of the ring gear 19b. By comprising, durability can be ensured by making the whole ring gear 19b into a ferrous material. At this time, since the circular hollow holes 51a and 51a are formed in the first portion 51, the center of gravity position G can be easily adjusted only by changing the size and number of the hollow holes 51a and 51a.

  Also, bolts 54, 54 for fastening the first portion 51 and the second portion 52 together in the space α formed by the recesses 51b, 51b when the inner race 22a of the ball bearing 22 is press-fitted into the outer peripheral surface of the eccentric disk 19. Since the heads 54b and 54b are housed, the press-fit of the inner race 22a of the ball bearing 22 is not hindered by the interference of the bolts 54 and 54 with the heads 54b and 54b. In addition, since the concave portions 51b and 51b are formed in the first portion 51, the weight of the outer peripheral portion of the first portion 51 can be reduced, and the adjustment of the gravity center position G can be further facilitated.

Second embodiment

  Next, a second embodiment of the present invention will be described with reference to FIG.

  In the second embodiment, a second portion 52 made of an iron-based material is cast into and integrated with a first portion 51 made of an aluminum-based material. At this time, a portion corresponding to a portion 53 of the ring gear made of iron-based material of the first embodiment is formed integrally with the second portion 52 in advance in the second embodiment. Further, by covering both side surfaces of the second portion 52 with thin portions 51d and 51d obtained by extending the first portion 51, the first portion 51 and the second portion are not required without using the bolts 54 and 54 of the first embodiment. 52 can be firmly integrated.

  Also according to the second embodiment, the center of gravity G of the eccentric disk 19 is moved from the center O2 side of the eccentric disk 19 to the second portion 52 side without requiring a balance weight, and the center of the ring gear 19b (eccentric cam). 17 center) can match O1.

  The embodiments of the present invention have been described above, but various design changes can be made without departing from the scope of the present invention.

  For example, in the embodiment, the center of gravity G of the eccentric disk 19 is made to coincide with the center O1 of the ring gear 19b, but it may be only brought close to the center O1 of the ring gear 19b.

  In the embodiment, the first portion 51 is made of an aluminum-based material and the second portion 52 is made of an iron-based material. However, the present invention is not limited to these materials.

  The drive source of the present invention is not limited to the engine E of the embodiment, and may be another drive source such as an electric motor.

12 Input shaft 13 Output shaft 15 Transmission shaft 17 Eccentric cam 18 Pinion 19 Eccentric disc 19b Ring gear 21 Connecting rod 22 Ball bearing (bearing)
22a Inner race 23 One-way clutch 51 First part 51a Lightening hole 51b Recess 52 Second part 53 Ring gear part 54 Bolt 54b Head E Engine (drive source)
L Input shaft axis α Space ε Eccentricity of eccentric member

Claims (5)

An eccentric cam (17) fixed in an eccentric state on the outer periphery of the input shaft (12) connected to the drive source (E);
An eccentric disk (19) supported on the outer periphery of the eccentric cam (17) so as to be relatively rotatable in an eccentric state;
A transmission shaft (15) coaxially fitted inside the input shaft (12);
A pinion (18) fixed to the transmission shaft (15);
A ring gear (19b) formed on the eccentric disk (19) and meshing with the pinion (18);
A one-way clutch (23) provided on the outer periphery of the output shaft (13);
A connecting rod (21) reciprocatingly connected to both ends of the eccentric disk (19) and the one-way clutch (23);
The rotation of the input shaft (12) is intermittently transmitted to the output shaft (13) via the connecting rod (21) and the one-way clutch (23), and the eccentric cam (15) is transmitted by the transmission shaft (15). 17) Vehicle power for changing the gear ratio by rotating the eccentric disk (19) around and changing the eccentric amount (ε) of the eccentric disk (19) with respect to the axis (L) of the input shaft (12). A transmission device,
The eccentric disk (19) includes a first part (51) located on the eccentric side and a second side part (52) located on the opposite eccentric side, and the second part (52) and the first part ( 51. The vehicle power transmission device, wherein a part (53) of the ring gear connected to 51) is made of a material having a high specific gravity and a high strength relative to a material of the first part (51).   The material of the first part (51) is an aluminum-based material, and the material of the second part (52) and a part of the ring gear (53) is an iron-based material. The vehicle power transmission device as described.   The first part (51) and the second part (52) are integrally fastened by a bolt (54), and the head (54b) of the bolt (54) is formed on the outer peripheral surface of the first part (51). It is arranged in a space (α) formed between the notched recess (51b) and the inner race (22a) of the bearing (22) fitted to the outer peripheral surface of the first portion (51). The vehicle power transmission device according to claim 1 or 2.   The power transmission for a vehicle according to claim 1 or 2, wherein the second part (52) and a part (53) of the ring gear are cast into the first part (51). apparatus. The vehicle power transmission device according to any one of claims 1 to 4, wherein the first portion (51) includes a lightening hole (51a).

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