JP6817900B2 - Vehicle power transmission device - Google Patents

Description

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

The eccentric body component (eccentric disk) of the crank-type vehicle power transmission device is divided into two semicircular eccentric body component halves, and the two eccentric body component halves are integrated with two bolts. It is known from Patent Document 1 below that it is assembled by fastening to.

Japanese Patent Publication No. 2011-518290

By the way, in the above-mentioned Patent Document 1, the large end portion of the connecting rod is supported on the outer peripheral surface of the eccentric body constituent member divided into two via a ball bearing, but on the outer peripheral surface of the eccentric body constituent member. Since the recess for inserting the head of the bolt is cut out, the inner race of the ball bearing press-fitted into the outer peripheral surface of the eccentric body component falls into the recess and the roundness decreases, and the ball The performance and durability of the bearing may be adversely affected.

The present invention has been made in view of the above circumstances, and an object of the present invention is to secure the roundness of a bearing supported on the outer peripheral surface of an eccentric disc of a crank type power transmission device.

In order to achieve the above object, according to the invention of 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 on the outer periphery of the eccentric cam. An eccentric disc supported so as to be relatively rotatable, a speed change shaft coaxially fitted inside the input shaft, a pinion fixed to the speed change shaft, and an eccentric disc formed on the eccentric disc 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 whose both ends are connected to the eccentric disk and the one-way clutch to reciprocate are provided, and the rotation of the input shaft is rotated by the connecting rod and the one-way. While intermittently transmitting to the output shaft via a clutch, the shift shaft rotates the eccentric disc around the eccentric cam to change the amount of eccentricity of the eccentric disc with respect to the axis of the input shaft to change the gear ratio. A vehicle power transmission device to be modified, the eccentric disk has a notch and a shaft formed in the first portion of a first portion located on the eccentric side and a second side portion located on the anti-eccentric side. It is configured by integrally fastening with a bolt inserted into a bolt hole composed of a hole and a female screw hole formed in the second side portion, and the axis of the bolt is a bearing that supports a large end of the connecting rod. The inner race is offset from the center of the bearing support surface on the outer periphery of the eccentric disk to one side in the axial direction of the input shaft, and the notch opens so as not to divide the bearing support surface in the circumferential direction. A vehicle power transmission device characterized by the above is proposed.

According to the second aspect of the invention, in addition to the configuration of the first aspect, the first portion and the second side portion are formed from the center of the bearing support surface to one of the axial directions of the input shaft. A vehicle power transmission device is proposed, which is integrally fastened with the bolt offset to the other side.

According to the third aspect of the present invention, in addition to the configuration of the second aspect, the two eccentric disks adjacent to each other in the axial direction of the input shaft are provided, and one of the eccentric disks facing each other is provided. A vehicle power transmission device is proposed in which the bolt and the bolt of the other eccentric disc are arranged so as to intersect with each other when viewed in the axial direction of the input shaft.

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 configuration of claim 1, when the eccentric disk rotates eccentrically with the input shaft, the connecting rod connected to one end of the eccentric disk reciprocates, and when the connecting rod moves in one direction, the one-way clutch engages. When the connecting rod moves in the other direction, the one-way clutch is disengaged, so that the rotation of the input shaft is changed and transmitted to the output shaft. When the amount of eccentricity of the eccentric disc is changed by the speed change shaft via the pinion and the ring gear, the reciprocating stroke of the connecting rod is changed and the gear ratio of the power transmission device is changed.

The eccentric disk has a first portion located on the eccentric side and a second side portion located on the anti-eccentric side, a notch and a shaft hole formed in the first portion, and a female screw hole formed in the second side portion. It is configured by integrally fastening with bolts inserted into the bolt holes consisting of, and the axis of the bolt is the bearing support surface on the outer circumference of the eccentric disc to which the inner race of the bearing supporting the large end of the connecting rod fits. It is offset in one direction from the center in the axial direction of the input shaft, and the notch opens so as not to divide the bearing support surface in the circumferential direction, so a part of the inner race of the bearing falls into the notch of the bolt hole and the diameter. It can prevent inward deformation and minimize the deterioration of bearing performance and durability.

Further, according to the configuration of claim 2, the first portion and the second side portion are integrally fastened with bolts offset from the center of the bearing support surface to one and the other in the axial direction of the input shaft. The fastening force of the bolt can be distributed to both side surfaces of the eccentric disc in a well-balanced manner, and the first portion and the second portion can be firmly fastened.

Further, according to the configuration of claim 3, two eccentric discs adjacent to each other in the axial direction of the input shaft are provided, and one eccentric disc bolt and the other eccentric disc bolt facing each other are the axis of the input shaft. Since they are arranged so as to intersect in the direction, it is possible to avoid interference between the part where the bolt of one eccentric disc is arranged and the part where the bolt of the other eccentric disc is arranged, and the axis of the input axis. It is possible to prevent the expansion of the dimension in the direction.

It is a vertical sectional view of a continuously variable transmission. It is a cross-sectional view taken along the line 2-2 of FIG. It is a single item drawing of an eccentric disc. It is sectional drawing corresponding to FIG. It is a side view of the input shaft provided with an eccentric disc. It is a figure which shows the relationship between the eccentricity amount of an eccentric disc and a gear ratio.

Hereinafter, embodiments of the present invention will be described with reference to FIGS. 1 to 6.

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

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

A speed change shaft 15 sharing the axis L is arranged inside the hollow input shaft 12, and is divided into 9 parts in the axis L direction via 10 needle bearings 16 ... On the outer circumference of the speed change shaft 15. The eccentric cam 17 ... Is rotatably supported. A total of nine eccentric cams 17 ... Of the eight transmission units 14 ... Are integrally connected by a plurality of bolts (not shown), and the inner peripheral portions of the nine eccentric cams 17 ... are substantially input shafts. 12 is configured.

The pair of adjacent eccentric cams 17 and 17 are inside the pair of circular cam portions 17a and 17a having a center O1 eccentric with respect to the axis L of the input shaft 12 by a distance d and the cam portions 17a and 17a in the radial direction. A guide portion 17b having a crescent-shaped cross section is provided. Eight pinions 18 ... Are integrally formed on the outer circumference of the speed change shaft 15 that shares the axis L with the input shaft 12, and each pinion 18 is a notch of a guide portion 17b having a crescent-shaped cross section of the eccentric cams 17 and 17. It is stored in the portion 17c. The phases of the cam portions 17a and 17a of the eccentric cams 17 and 17 of each transmission unit 14 are shifted by 45 ° from each other.

As shown in FIGS. 2 to 4, on the outer peripheral surfaces of the cam portions 17a and 17a of the eccentric cams 17 and 17, a pair of eccentric recesses 19a formed on both end faces of the disc-shaped eccentric disk 19 in the axial direction L direction, The 19a is rotatably supported via a pair of needle bearings 20, 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 deviated 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 centers 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 and 19a of the eccentric disc 19 slidably contact the outer peripheral surface of the guide portions 17b of the eccentric cams 17 and 17. Then, the pinion 18 of the speed change shaft 15 exposed from the opening 12a (see FIG. 2) of the input shaft 12 meshes with the ring gear 19b of the eccentric disc 19. A large end portion 21a of the connecting rod 21 is supported on the outer periphery of the eccentric disc 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 21b of the connecting rod 21 via a pin 24. A ring-shaped outer member 26 fixed to the inner circumference of the swing link 25, a ring-shaped inner member 27 arranged inside the outer member 26 and fixed to the output shaft 13, and an inner peripheral surface of the outer member 26. A plurality of rollers 29 ... Arranged in a wedge-shaped 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 ... Are provided.

Then, at the shaft end of the input shaft 12 opposite to the engine E, the speed change shaft 15 is rotated relative to the input shaft 12 to increase or decrease the eccentricity amount ε of the eccentric disc 19 to shift 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 ... includes a central frame 31 located at the center of the axis L direction and a pair of side frames 32 and 33 located on both sides of the axis L direction. Four transmission units 14 ... Are arranged between the central frame 31 and one side frame 32 located on the engine E side, and the center frame 31 and the other side frame located on the anti-engine E side. Four transmission units 14 ... Are arranged between them and 33.

The central frame 31 is an iron plate-shaped 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 thereof.

The side frame 32 located on the engine E side is basically a cast member formed of an aluminum alloy in a cage shape, and a bearing holder 38, which is an iron plate-shaped member, is embedded in the central portion 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 anti-engine E side is also a cast member basically formed in a cage shape with an aluminum alloy, and a bearing holder 39, which 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 anti-engine E side overlap with each other because they are plane-symmetrical with respect to the side frame 32 side and the bearing holder 38 located on the engine E side described above. The description is omitted.

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

Then, the central frame 31 and the pair of side frames 32, 33 are integrally fastened with bolts 40 ... to assemble the subassembly, and this subassembly is fastened to the inside of the mission case 42 with bolts 41 ... Penetrating the central frame 31. Will be 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 6 (A) to 6 (D), when the center O2 of the eccentric disc 19 is eccentric with respect to the axis L of the input shaft 12, the engine E rotates the input shaft 12. The large end portion 21a of the connecting rod 21 rotates eccentrically around the axis L, so that the connecting rod 21 reciprocates.

As a result, when the connecting rod 21 is pulled to the left side in the drawing in the process of reciprocating, the outer member 26 swings counterclockwise in FIG. 2 together with the swing link 25, and the roller 29 urged by the spring 28 ... ... Is engaged in the 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 is engaged. The movement is transmitted to the output shaft 13. On the contrary, when the connecting rod 21 is pushed to the right side in the drawing in the process of reciprocating, the outer member 26 swings clockwise in FIG. 2 together with the swing link 25, and the rollers 29 ... compress the spring 28 ... The one-way clutch 23 is disengaged and the movement of the connecting rod 21 is transmitted to the output shaft 13 by being pushed out from the wedge-shaped space between the member 26 and the inner member 27 and slipping between the outer member 26 and the inner member 27. Will not be.

In this way, while the input shaft 12 makes one rotation, the rotation of the input shaft 12 is transmitted to the output shaft 13 for a predetermined time. Therefore, when the input shaft 12 continuously rotates, the output shaft 13 rotates intermittently. The eccentricity 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 by 45 ° from each other, so that the eight transmission units 14 ... Are on the input shaft 12. By alternately transmitting the rotation to the output shaft 13, the output shaft 13 rotates continuously.

At this time, as the eccentricity amount ε of the eccentric disc 19 increases, the reciprocating stroke of the connecting rod 21 increases, the rotation angle of the output shaft 13 increases once, and the gear ratio of the continuously variable transmission T decreases. On the contrary, as the eccentricity amount ε of the eccentric disc 19 becomes smaller, the reciprocating stroke of the connecting rod 21 becomes smaller, the rotation angle of the output shaft 13 at one time decreases, and the gear ratio of the continuously variable transmission T becomes larger. When the eccentricity ε of the eccentric disc 19 becomes zero, the output shaft 13 does not rotate because the connecting rod 21 stops moving even if the input shaft 12 rotates, and the gear ratio of the continuously variable transmission T becomes maximum ( Infinity).

When the speed change shaft 15 does not rotate relative to the input shaft 12, that is, when the input shaft 12 and the speed change shaft 15 rotate at the same speed, the gear ratio of the continuously variable transmission T is maintained constant. When the speed change shaft 15 is rotated relative to the input shaft 12 by the speed change actuator 30, the eccentric recesses 19a and 19a of the eccentric disk 19 in which the ring gear 19b is meshed with the pinion 18 of each transmission unit 14 are integrated with the input shaft 12. The eccentric cams 17 and 17 are guided by the cams 17a and 17a to rotate, 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. 6A shows a state in which the gear ratio is the minimum (gear 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. The maximum value is equal to 2d, which is the sum of the distance d from the center O1 of the eccentric cams 17 and 17 to the center O1 of the eccentric cams 17 and 17 and the distance d from the center O1 of the eccentric cams 17 and 17 to the center O2 of the eccentric disk 19. When the speed change shaft 15 rotates relative to the input shaft 12, the eccentric disc 19 rotates relative to the eccentric cams 17 and 17 integrated with the input shaft 12, so that FIGS. 6 (B) and 6 (C) show. As shown, the eccentric amount ε of the center O2 of the eccentric disc 19 with respect to the axis L of the input shaft 12 gradually decreases from the maximum value of 2d, and the gear ratio increases. When the speed change shaft 15 further rotates relative to the input shaft 12, the eccentric disc 19 further rotates relative to the eccentric cams 17 and 17 integrated with the input shaft 12, as shown in FIG. 6 (D). Finally, the center O2 of the eccentric disk 19 overlaps the axis L of the input shaft 12, the eccentric amount ε becomes zero, the gear ratio becomes the maximum (infinity) (gear ratio: UD), and the power with respect to the output shaft 13 is reached. Transmission is blocked.

Next, the structure of the eccentric disk 19 will be described in detail with reference to FIGS. 3 and 4.

The eccentric disc 19 is divided into two in 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 connecting the center O1 of the ring gear 19b and the center O2 of the eccentric disc 19. ing. The eccentric side of the eccentric disk 19 divided into two, that is, the portion on the center O2 side constitutes a relatively large first portion 51, and the anti-eccentric side of the eccentric disk 19 divided into two, that is, the side opposite to the center O2. 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, a part 53 of the ring gear constituting the ring gear 19b is also made of an iron-based material having the same high specific gravity and high strength as the second part 52. That is, the ring gear 19b of the eccentric disc 19 has a half-circumferential portion on the anti-eccentric side formed in the second portion 52, and a half-circumferential portion on the eccentric side is composed of a partial 53 of the ring gear. Two circular lightening holes 51d and 51d are formed in the first portion 51.

The first portion 51 and the second portion 52 are integrally fastened by two bolts 54 and 54 arranged parallel to each other in a state of being positioned by the two knock pins 43 and 43. The two bolts 54, 54 are offset to both sides with respect to the central surface of the eccentric disc 19 in the thickness direction (axis L direction of the input shaft 12).

A first bulging portion 51a and a second bulging portion 52a having a semicircular cross section aligned linearly are projected on one side surface of the first portion 51 and the second portion 52 of the eccentric disk 19, and the first A notch 51b having a semicircular cross section that is linearly aligned with the first bulging portion 51a and the second bulging portion 52a is recessed on one side surface of the portion 51, and the bottom portion of the notch 51b of the first portion 51 is recessed. A seat surface 51e is formed on the surface (see FIG. 3A). Similarly, the first bulging portion 51a, the second bulging portion 52a, the notch 51b, and the seating surface 51e are formed on the other side surfaces of the first portion 51 and the second portion 52 of the eccentric disc 19.

The bolt 54 includes a head portion 54a, a shaft portion 54b, and a male screw portion 54c, and the shaft portion 54b of the bolt 54 inserted through the notch 51b of the first portion 51 fits into the shaft hole 51c of the first portion 51. The male screw portion 54c is screwed into the female screw hole 52b of the second portion 52, and the head 54a is seated on the seat surface 51e of the first portion 51, whereby the first portion 51 and the second portion 52 are integrally fastened. To.

The ball bearing 22 that supports the connecting rod 21 on the eccentric disc 19 includes an inner race 22a, an outer race 22b, and a plurality of balls 22c ... (See FIG. 2). The outer race 22b is composed of an inner peripheral surface of a large end portion 21a of the connecting rod 21. The outer peripheral surface of the eccentric disc 19 constitutes an annular bearing support surface 19c into which the inner peripheral surface of the inner race 22a of the ball bearing 22 is press-fitted, and the opening of the notch 51b into which the bolt 54 is inserted is a bearing. It is opened so as to cut out only a part of the support surface 19c.

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

FIG. 6A shows a state of the minimum gear ratio (gear ratio: TD) in which the eccentricity ε of the center O2 of the eccentric disc 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 disc 19 with respect to the center O1 of the eccentric cam 17 (upward in the figure) are the same directions. At this time, the position G of the center of gravity of the eccentric disc 19 coincides with the center O1 of the eccentric cam 17.

FIG. 6D shows a state of the maximum gear ratio (gear ratio: UD) in which the eccentricity amount ε of the center O2 of the eccentric disc 19 with respect to the axis L of the input shaft 12 becomes zero, and the input shaft 12 The eccentric direction of the center O1 of the eccentric cam 17 with respect to the axis L (to the right in the figure) and the eccentric direction of the center O2 of the eccentric disc 19 to the center O1 of the eccentric cam 17 (to the left in the figure) are opposite. At this time, the position G of the center of gravity of the eccentric disc 19 coincides with the center O1 of the eccentric cam 17.

That is, according to the present embodiment, since the center of gravity position G of the eccentric disc 19 coincides with the center O1 of the eccentric cam 17, the eccentric disc 19 is moved around the center O1 of the eccentric cam 17 as the gear ratio is changed. Even if the eccentric rotation occurs, the center of gravity position G of the eccentric disc 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 center of gravity position G of the eccentric disc 19 changes from a constant value d. There is nothing to do.

Assuming that the distance from the axis L of the input shaft 12 to the center of gravity position G of the eccentric disc 19 changes with the change of the gear ratio, the inertial moment of inertia of the eccentric disc 19 around the input shaft 12 increases the distance. Since it increases accordingly and decreases as the distance decreases, the rotational load of the input shaft 12 may fluctuate and vibration may occur as the gear ratio changes. However, according to the present embodiment, since the inertial secondary moment of the eccentric disc 19 around the input shaft 12 does not change even if the gear ratio is changed, the vibration of the input shaft 12 can be minimized.

Further, since the eccentric disc 19 is supported by the eccentric cam 17 so as to be relatively rotatable, if the center of gravity position G of the eccentric disc 19 does not match the center O1 of the eccentric cam 17, the rotation speed of the input shaft 12 increases. Alternatively, when the value decreases, the eccentric disc 19 tries to rotate relative to the eccentric cam 17 due to inertial force, and the moment is transmitted from the ring gear 19b of the eccentric disc 19 to the speed change actuator 30 via the pinion 18, so that the speed change actuator 30 Unnecessary torque may act on the gear to reduce the accuracy of shift control.

However, according to the present embodiment, since the center of gravity position G of the eccentric disc 19 coincides with the center O1 of the eccentric cam 17, the eccentric disc 19 is inertial even if the rotation speed of the input shaft 12 increases or decreases. The force does not generate a moment that tends to rotate relative to the eccentric cam 17, which prevents unnecessary torque from acting on the speed change actuator 30 and ensures the accuracy of shift control.

Further, if the ring gear 19b is directly formed on the first portion 51 made of a relatively low-strength aluminum-based material, there is a problem that the ring gear 19b is insufficient in strength and durability, but a part 53 of the ring gear is made of an iron-based material. Due to the configuration, the entire ring gear 19b is made of an iron-based material to ensure durability. At this time, since the lightening holes 51d and 51d of the shape are formed in the first portion 51, the center of gravity position G can be easily adjusted only by changing the size and the number of the lightening holes 51d and 51d.

Further, since the two bolts 54 and 54 for fastening the first portion 51 and the second side portion 52 are offset from the center of the bearing support surface 19c of the eccentric disc 19 to one and the other in the axis L direction of the input shaft 12, the bearing The support surface 19c is not divided in the circumferential direction by the notches 51b and 51b, and the width of the input shaft 12 in the axis L direction is only partially cut out to make the inner race 22a all around. Can be supported throughout. Therefore, it is possible to prevent a part of the inner race 22a of the ball bearing 22 from falling into the openings of the notches 51b and 51b and deforming inward in the radial direction, and minimizing the deterioration of the performance and durability of the ball bearing 22. Can be suppressed to.

Further, as is clear from FIGS. 3 to 5, since the two bolts 54 and 54 are offset from each other in opposite directions, the fastening force of the two bolts 54 and 54 is balanced on both side surfaces of the eccentric disk 19. It is well dispersed and the first portion 51 and the second portion 52 can be firmly fastened. Moreover, since the phases of the eight eccentric discs 19 are all different, when viewed in the L direction of the axis of the input shaft 12, the first and second bulging portions 51a and 52a of one of the eccentric discs 19 facing each other , The other eccentric disc 19 is arranged so as to intersect with the first and second bulging portions 51a and 52a. Therefore, it is possible to prevent the first and second bulging portions 51a and 52a of one eccentric disk 19 from interfering with the first and second bulging portions 51a and 52a of the other eccentric disk 19, and to prevent the input shaft 12 from interfering with each other. It is possible to prevent the dimension of the axis L direction from expanding.

Although the embodiments of the present invention have been described above, the present invention can make various design changes without departing from the gist thereof.

For example, in the embodiment, the materials of the first portion 51 and the second portion 52 of the eccentric disk 19 are different, but they may be matched.
Further, the bearing of the present invention is not limited to the ball bearing 22 of the embodiment, and may be another type of bearing such as a roller bearing or a needle bearing.

Further, 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 Speed change shaft 17 Eccentric cam 18 Pinion 19 Eccentric disc 19b Ring gear 19c Bearing support surface 21 Connecting rod 22 Ball bearing (bearing)
22a Inner race 23 One-way clutch 51 1st part 51b Notch 51c Shaft hole 52 2nd part 52b Female screw hole 54 Bolt E Engine (drive source)
L Input axis axis ε Eccentricity of eccentric member

Claims (3)

An eccentric cam (17) fixed in an eccentric state on the outer circumference of the input shaft (12) connected to the drive source (E),
An eccentric disc (19) supported on the outer circumference of the eccentric cam (17) so as to be relatively rotatable in an eccentric state.
A speed change shaft (15) coaxially fitted inside the input shaft (12),
A pinion (18) fixed to the transmission shaft (15) and
A ring gear (19b) formed on the eccentric disc (19) and meshing with the pinion (18),
A one-way clutch (23) provided on the outer circumference of the output shaft (13) and
The eccentric disc (19) and the one-way clutch (23) are provided with a connecting rod (21) having both ends connected to each other and reciprocating.
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 speed change shaft (15). 17) Vehicle power that changes the gear ratio by rotating the eccentric disc (19) around to change the eccentric amount (ε) of the eccentric disc (19) with respect to the axis (L) of the input shaft (12). It ’s a transmission device,
The eccentric disk (19) has a notch (51) formed in the first portion (51) of a first portion (51) located on the eccentric side and a second side portion (52) located on the anti-eccentric side. The bolt (54) inserted into the bolt hole composed of the 51b) and the shaft hole (51c) and the female screw hole (52b) formed in the second side portion (52) is integrally fastened. The axis of the bolt (54) is the bearing support surface on the outer periphery of the eccentric disk (19) to which the inner race (22a) of the bearing (22) supporting the large end portion (21a) of the connecting rod (21) is fitted. It is offset in one direction from the center of (19c) in the axis (L) direction of the input shaft (12), and the notch (51b) opens the bearing support surface (19c) so as not to divide it in the circumferential direction. A power transmission device for vehicles characterized by this. The first portion (51) and the second side portion (52) are offset from the center of the bearing support surface (19c) to one and the other in the axis (L) direction of the input shaft (12). 54) The vehicle power transmission device according to claim 1, wherein the power transmission device is integrally fastened. The bolt (54) of one of the eccentric discs (19) facing each other and the eccentricity of the other are provided with two eccentric discs (19) adjacent to each other in the axis (L) direction of the input shaft (12). The vehicle power according to claim 2, wherein the bolt (54) of the disk (19) is arranged so as to intersect with each other when viewed in the axial direction (L) direction of the input shaft (12). Transmission device.

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