JP6080211B2 - Power transmission device for vehicle - Google Patents

Description

  The present invention relates to a power transmission device for a vehicle in which a plurality of transmission units that shift rotation of an input shaft connected to a drive source and transmit the rotation to an output shaft are juxtaposed in the axial direction, and a pair of restrictions are provided on the outer periphery of the output shaft. The present invention relates to one having two or three one-way clutches sandwiched between means.

  For a vehicle that converts rotation of an input shaft connected to an engine into reciprocating motions of a plurality of connecting rods having mutually different phases, and converts reciprocating motion of the plurality of connecting rods to rotational motion of an output shaft by a plurality of one-way clutches. A power transmission device is known from Patent Document 1 below.

JP 2012-1048 A

  FIG. 17 schematically shows the structure around the output shaft 12 of such a vehicle power transmission device. The three one-way clutches 21 juxtaposed in the axial direction are provided with three swing links 22 constituting an outer member on the outer periphery of the output shaft 12 constituting the inner member. A plurality of rollers 25 are arranged between the links 22. In order to align the swing links 22 with respect to the output shaft 12, each one-way clutch 21 includes a pair of angular ball bearings 34, 34 disposed on both sides in the axial direction of the rollers 25. Each angular ball bearing 34 includes an inner ring 36 that is slidably fitted on the outer periphery of the output shaft 12, an outer ring 35 that is integrally formed on the inner periphery of the swing link 22, and an inner ring 36 and an outer ring 35. It comprises a plurality of balls 37 arranged.

  Inner rings 36 of a pair of angular ball bearings 34, 34 disposed between two adjacent one-way clutches 21, 21 are integrally formed to support two rows of balls 37. Further, the inner rings 36 of the angular ball bearings 34, 34 outside the axial direction of the one-way clutches 21, 21 at both ends in the axial direction are in contact with the restricting means 41, 44 fixed to the output shaft 12 and are fixed in the axial direction. The restricting means 41 and 44 are, for example, inner rings of bearings 27 and 28 that support the output shaft 12 in the transmission case. An axial spring 38 is disposed between the right end surface of the rollers 25 of each one-way clutch 21 and the inner ring 36 of the angular ball bearing 34 facing the right side thereof, and the rollers 25 are moved to the left by the axial spring 38. By energizing and pressing the left end surface of the rollers 25 against the inner ring 36 of the angular ball bearing 34, the one-way clutch 21 can be stably engaged by preventing the rollers 25 from tilting.

  As described above, in the conventional one, the axial springs 38 of the plurality of one-way clutches 21 are all arranged at the same position (on the right side of the roller 25 in the example of FIG. 17), and the rollers 25 are arranged in the same direction (see FIG. In the example of 17, the left side is biased, and there is a problem as described below.

  The three one-way clutches 21 arranged between the pair of regulating means 41 and 44 are sequentially engaged with a predetermined phase difference. FIG. 17 shows a state in which the # 3 one-way clutch 213 at the left end is engaged. When the rollers 253... Are engaged between the output shaft 12 and the swing link 223, the reaction force from the rollers 253. Further, the diameter of the swinging link 223 is increased, and backlash is generated between the # 3 one-way clutch 213 and the inner ring 3623, 363 of the angular ball bearings 343, 343 on both sides in the axial direction.

  Consider a case where, for example, the # 2 one-way clutch 21 2 starts to be engaged while the # 3 one-way clutch 213 is engaged. Since the inertia force is applied to the swing link 22 2 of the # 2 one-way clutch 21 2 from the connecting rod, if the swing link 22 2 is urged to the left side by this inertia force, play occurs in the angular ball bearings 343 and 343. Therefore, the swing link 22 2 and the inner ring 3623 move to the left while compressing the axial spring 383. As a result, when the # 2 one-way clutch 21 2 is engaged, the swing link 22 2 is displaced from the proper position, and the smooth engagement of the # 2 one-way clutch 21 2 may be hindered.

  In the example of FIG. 17, the axial springs 381, 382, and 383 of the # 1, # 2, and # 3 one-way clutches 211, 212, and 213 are all arranged on the same side (the right side of the roller 25 ...). , 382 and 383 can be devised to solve the above-mentioned problems and enable smooth engagement of all the one-way clutches 21.

  The present invention has been made in view of the above circumstances, and enables a stable engagement of a one-way clutch provided on the outer periphery of an output shaft in a vehicle power transmission device in which a plurality of crank-type transmission units are juxtaposed. With the goal.

  In order to achieve the above object, according to the first aspect of the present invention, a plurality of speed change units that shift the rotation of the input shaft connected to the drive source and transmit it to the output shaft are juxtaposed in the axial direction. Each of the transmission units includes an eccentric member that is variable in eccentricity from the axis of the input shaft and rotates together with the input shaft, a swing link that is rotatably supported by the output shaft, and the output shaft And the one-way clutch disposed between the swing links, the connecting rod connecting the eccentric member and the swing link, and the swing links disposed on both axial sides of the one-way clutch with respect to the output shaft. The three one-way clutches included in the three transmission units arranged in parallel in the axial direction are provided with a pair of angular bearings coaxially aligned with each other. Each of the one-way clutches included in the one-way clutch group includes a plurality of rollers disposed between an inner peripheral surface of the swing link and an outer peripheral surface of the output shaft, and the rollers are arranged in any of the axial directions. The angular bearing is provided on the outer periphery of the output shaft so as to be slidable in the axial direction, and includes an inner ring that supports the axial spring, and is adjacent to the one-way clutch group. The two inner rings sandwiched between the pair of one-way clutches are integrally formed, and the inner rings on the axially outer sides of the two one-way clutches located at both axial ends of the one-way clutch group are the output shafts. A vehicle power transmission device that is restricted from moving outward in the axial direction by abutting against a regulating means provided on the vehicle, The rollers of the two one-way clutches located at both ends in the axial direction of the latch group are urged inward in the axial direction by the axial springs arranged between the inner ring and the inner ring abutting against the restricting means. The roller of one of the one-way clutches located in the axially central portion of the one-way clutch group is the side of the two one-way clutches that starts engaging when the one one-way clutch is engaged. A vehicle power transmission device is proposed, which is biased by the axial spring toward the one-way clutch.

  According to the invention described in claim 2, in addition to the configuration of claim 1, a # 1 one-way clutch, a # 2 one-way clutch arranged in order from one axial end side to the other axial end side, A # 3 one-way clutch, a # 4 one-way clutch, a # 5 one-way clutch, and a # 6 one-way clutch are provided. The # 1- # 3 one-way clutch constitutes a first one-way clutch group, and the # 4- # 6 one-way clutch is a second one. The # 1 to # 6 one-way clutches are alternately engaged in the order of # 1 → # 6 → # 2 → # 4 → # 3 → # 5, and the rollers of the # 1 one-way clutch are The axial spring is biased toward the # 2 one-way clutch, and the roller of the # 2 one-way clutch is # 3 one-wake with the axial spring. The roller of the # 3 one-way clutch is biased toward the # 2 one-way clutch by the axial spring, and the roller of the # 4 one-way clutch is directed toward the # 5 one-way clutch by the axial spring. The roller of the # 5 one-way clutch is biased toward the # 6 one-way clutch by the axial spring, and the roller of the # 6 one-way clutch is biased toward the # 5 one-way clutch by the axial spring. A vehicular power transmission device is proposed.

According to a third aspect of the present invention, in addition to the structure of the first or second aspect , the restricting means is an inner ring of a shaft support bearing that supports the output shaft on a casing. A vehicle power transmission device is proposed.

According to the invention described in claim 4 , a plurality of transmission units that shift the rotation of the input shaft connected to the drive source and transmit it to the output shaft are juxtaposed in the axial direction, and each of the transmission units is An eccentric member that has a variable amount of eccentricity from the axis of the input shaft and rotates together with the input shaft, a swing link that is rotatably supported by the output shaft, and between the output shaft and the swing link A pair of disposed one-way clutches, connecting rods connecting the eccentric member and the swing link, and a pair of shafts disposed on both sides in the axial direction of the one-way clutch to coaxially align the swing link with respect to the output shaft. The two one-way clutches included in the two transmission units arranged side by side in the axial direction constitute a one-way clutch group, and Each of the two one-way clutches included in the clutch group includes a plurality of rollers disposed between an inner peripheral surface of the swing link and an outer peripheral surface of the output shaft, and the roller is disposed on either side in the axial direction. The angular bearings are provided on the outer periphery of the output shaft so as to be axially slidable to support the axial springs, and the two one-way clutch groups include the two one-way clutches. The two inner rings sandwiched between the clutches are integrally formed, and the inner ring on the outer side in the axial direction of the two one-way clutches of the one-way clutch group is in contact with the regulating means provided on the output shaft in the axial direction. A vehicle power transmission device that is restricted from moving outward, wherein the rollers of the two one-way clutches of the one-way clutch group include: Vehicle power transmission apparatus characterized by being urged axially inwardly is proposed by arranged the axial spring between the inner ring abuts against the restriction means.

  According to the invention described in claim 5, a plurality of transmission units that shift the rotation of the input shaft connected to the drive source and transmit it to the output shaft are juxtaposed in the axial direction, and each of the transmission units includes: An eccentric member that has a variable amount of eccentricity from the axis of the input shaft and rotates together with the input shaft, a swing link that is rotatably supported by the output shaft, and between the output shaft and the swing link A pair of disposed one-way clutches, connecting rods connecting the eccentric member and the swing link, and a pair of shafts disposed on both sides in the axial direction of the one-way clutch to coaxially align the swing link with respect to the output shaft. The two or three one-way clutches included in the two or three speed change units juxtaposed in the axial direction are one-way clutches. Each of the one-way clutches included in the one-way clutch group includes a plurality of rollers disposed between an inner peripheral surface of the swing link and an outer peripheral surface of the output shaft, An axial spring urging to the other side, and the angular bearing includes an inner ring that is slidably disposed on an outer periphery of the output shaft and supports the axial spring. The two inner rings sandwiched between a pair of adjacent one-way clutches are integrally formed, and the inner rings on the axially outer sides of the two one-way clutches located at both axial ends of the one-way clutch group are the output A power transmission device for a vehicle, whose movement outward in the axial direction is regulated by a regulating means provided on a shaft, wherein the one-way clutch Among the two or three one-way clutches included in the group, the direction in which the axial spring of the currently engaged one-way clutch urges the roller starts engagement while the one-way clutch is engaged. A vehicle power transmission device is proposed that is directed toward another one-way clutch.

  The eccentric disk 18 of the embodiment corresponds to the eccentric member of the present invention, and the first to third one-way clutch groups 21A to 21C of the embodiment correspond to the one-way clutch group of the present invention. The mission case 26 corresponds to the casing of the present invention, the ball bearing 27 and roller bearing 28 of the embodiment correspond to the shaft support bearing of the present invention, and the angular ball bearing 34 of the embodiment corresponds to the angular bearing of the present invention. The inner rings 41 and 44 and the clip 46 of the embodiment correspond to the regulating means 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 the first aspect, when the input shaft connected to the drive source rotates, the eccentric member of each transmission unit rotates eccentrically, and the connecting rod having one end connected to the eccentric member reciprocates, thereby connecting The output shaft rotates intermittently through a one-way clutch to which the other end of the rod is connected. The output shaft can be continuously rotated by transmitting the driving force by shifting the phases with each other.

  When one of the three one-way clutches of the one-way clutch group disposed between the pair of regulating means is engaged, the swing link of the engaged one-way clutch is expanded in diameter by the reaction force received from the roller, and the swing link An axial backlash occurs in the angular bearings on both sides in the axial direction, and the inner ring of the angular bearing can move in the axial direction along the output shaft. There is a risk that smooth engagement will be hindered by moving in the axial direction by the backlash.

  However, the two one-way clutch rollers positioned at both axial ends of the one-way clutch group are urged in the axial direction by an axial spring disposed between the inner ring and the inner ring contacting the restricting means, and the one-way clutch group Axial of one one-way clutch roller located in the axial center of the two-way clutch toward the one-way clutch of the two one-way clutches that starts engagement while the one one-way clutch is engaged By energizing with a spring, the movement of the swing link of the one-way clutch that starts the engagement in the axial direction is prevented by a roller that is engaged with and fixed to the output shaft of the engaged one-way clutch, The one-way clutch can be smoothly engaged by preventing the swing link from moving in the axial direction.

  According to the second aspect of the present invention, the first one-way clutch group consisting of # 1- # 3 one-way clutches and the second one-way clutch group consisting of # 4- # 6 one-way clutches are provided, and # 1- # When the six-way clutch is alternately engaged in the order of # 1, # 6, # 2, # 4, # 3, and # 5, all the swing links of # 1 to # 6 one-way clutch move in the axial direction. And can be engaged smoothly.

According to the third aspect of the present invention, since the restricting means is an inner ring of a shaft support bearing that supports the output shaft on the casing, the number of parts can be reduced by using the inner ring of the existing shaft support bearing as the restricting means. In addition, the axial dimension of the output shaft can be shortened.

According to the configuration of claim 4 , when the input shaft connected to the drive source rotates, the eccentric member of each transmission unit rotates eccentrically, and the connecting rod having one end connected to the eccentric member reciprocates, The output shaft rotates intermittently through a one-way clutch to which the other end of the connecting rod is connected. The output shaft can be continuously rotated by transmitting the driving force by shifting the phases with each other.

  When one of the two one-way clutches of the one-way clutch group disposed between the pair of regulating means is engaged, the diameter of the swing link of the one-way clutch is increased by the reaction force received from the roller, and the axial direction of the swing link An axial backlash is generated in the angular bearings on both sides, and the inner ring of the angular bearing can move in the axial direction along the output shaft, so that the swing link of the other one-way clutch that starts the next engagement is There is a risk that smooth engagement will be hindered by moving in the axial direction by the amount of play.

  However, the two one-way clutch rollers are biased inward in the axial direction by an axial spring disposed between the inner ring and the inner ring abutting against the restricting means, so that the swing link of the one-way clutch that starts the engagement is moved. By blocking the movement in the axial direction with a roller that is engaged with and fixed to the output shaft of the engaged one-way clutch, the movement of the swing link in the axial direction is prevented, enabling smooth engagement of the one-way clutch. Can be.

  According to the configuration of claim 5, when the input shaft connected to the drive source rotates, the eccentric member of each transmission unit rotates eccentrically, and the connecting rod having one end connected to the eccentric member reciprocates, The output shaft rotates intermittently through a one-way clutch to which the other end of the connecting rod is connected. The output shaft can be continuously rotated by transmitting the driving force by shifting the phases with each other.

  When one of two or three one-way clutches of the one-way clutch group disposed between the pair of restricting means is engaged, the diameter of the swing link of the engaged one-way clutch is increased by the reaction force received from the roller, and the An axial backlash is generated in the angular bearings on both axial sides of the swing link, and the inner ring of the angular bearing can move in the axial direction along the output shaft. There is a possibility that the moving link moves in the axial direction by the amount of the backlash and hinders smooth engagement.

  However, of the two or three one-way clutches included in the one-way clutch group, the direction in which the axial spring of the currently engaged one-way clutch urges the roller starts to engage while the one-way clutch is engaged. Since the direction is toward the other one-way clutch, the axial movement of the swing link of the one-way clutch that starts the engagement is prevented by a roller that is engaged with and fixed to the output shaft of the engaged one-way clutch. This prevents the swing link from moving in the axial direction and allows the one-way clutch to be smoothly engaged.

The skeleton figure of the power transmission device for vehicles. (First embodiment) FIG. 2 is a detailed view of part 2 of FIG. 1. (First embodiment) FIG. 3 is a sectional view taken along line 3-3 in FIG. 2 (OD state). (First embodiment) FIG. 3 is a cross-sectional view taken along line 3-3 in FIG. 2 (GN state). (First embodiment) The action explanatory view in OD state. (First embodiment) The operation explanatory view in the GN state. (First embodiment) FIG. 7 is an enlarged view of part 7 of FIG. 2. (First embodiment) FIG. 8 is a cross-sectional view taken along line 8-8 in FIG. (First embodiment) The disassembled perspective view of a one-way clutch. (First embodiment) Explanatory drawing of the action at the start of # 1 one-way clutch engagement. (First embodiment) Explanatory drawing of the action at the start of # 6 one-way clutch engagement. (First embodiment) # 2 Explanatory drawing of the action at the start of engagement of the one-way clutch. (First embodiment) Explanatory drawing of the action at the start of # 4 one-way clutch engagement. (First embodiment) # 3 Explanatory drawing of the action at the start of engagement of the one-way clutch. (First embodiment) Explanatory drawing of the action at the start of # 5 one-way clutch engagement. (First embodiment) The figure corresponding to FIGS. (Second Embodiment) The figure corresponding to the right half part of FIGS. (Conventional example)

First embodiment

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

  As shown in FIGS. 1 to 3, the vehicle power transmission device for transmitting the driving force of the engine E to the drive wheels W, W via the left and right axles 10, 10 is a crank type continuously variable transmission T and a differential. Gear D is provided. The continuously variable transmission T according to the present embodiment is obtained by superimposing a plurality (six in the embodiment) of transmission units U in the axial direction, and these transmission units U are arranged in parallel. The common input shaft 11 and the common output shaft 12 are provided, and the rotation of the input shaft 11 is decelerated or increased and transmitted to the output shaft 12. In FIG. 2, for convenience, only four of the six transmission units U are shown.

  Next, the structure of the continuously variable transmission T will be described with reference to FIGS.

  First, the structure of one transmission unit U will be described as a representative. The input shaft 11 connected to the engine E and rotates passes through the hollow rotating shaft 14a of the speed change actuator 14 such as an electric motor so as to be relatively rotatable. The rotor 14b of the speed change actuator 14 is fixed to the rotating shaft 14a, and the stator 14c is fixed to the casing. The rotation shaft 14 a of the speed change actuator 14 can rotate at the same speed as the input shaft 11 and can rotate relative to the input shaft 11 at a different speed.

  A first pinion 15 is fixed to the input shaft 11 passing through the rotation shaft 14 a of the speed change actuator 14, and a crank-shaped carrier 16 is connected to the rotation shaft 14 a of the speed change actuator 14 so as to straddle the first pinion 15. The Two second pinions 17, 17 having the same diameter as the first pinion 15 are supported via pinion pins 16 a, 16 a at positions forming an equilateral triangle in cooperation with the first pinion 15, respectively. The first pinion 15 and the second pinions 17, 17 mesh with a ring gear 18 a formed eccentrically inside a disc-shaped eccentric disk 18. A ring portion 19 b provided at one end of the rod portion 19 a of the connecting rod 19 is fitted to the outer peripheral surface of the eccentric disk 18 via a ball bearing 20 so as to be relatively rotatable.

  The six transmission units U share a crank-shaped carrier 16, but the phase of the eccentric disk 18 supported on the carrier 16 via the second pinions 17, 17 is 60 ° at each transmission unit U. Is different.

  A one-way clutch 21 provided on the outer periphery of the output shaft 12 includes a ring-shaped swing link 22 pivotally supported on a rod portion 19a of a connecting rod 19 via a pin 19c, an inner peripheral surface 22a of the swing link 22, and The rollers 25 are arranged in a wedge-shaped space formed between the outer peripheral surfaces 12a of the output shaft 12 and are urged by the engagement springs 24. The specific structure of the one-way clutch 21 will be described in detail later.

  Next, the structure around the output shaft 12 will be described with reference to FIGS. 3 to 6, the one-way clutch 21 is schematically shown, and the actual structure is shown in FIGS.

  Both ends of the output shaft 12 in the axial direction are supported on the mission case 26 via a pair of ball bearings 27, 27, and the center in the axial direction is supported on the mission case 26 via a roller bearing 28. Therefore, three transmission units U are arranged on the right side of the roller bearing 28, and three transmission units U are arranged on the left side of the roller bearing 28. As described above, the output shaft 12 is supported at the three positions of the axial end portions and the axial center portion, thereby reducing the bending thereof.

  The one-way clutch 21 supported on the outer periphery of the output shaft 12 has twelve rollers 25 disposed between the circular inner peripheral surface 22a of the swing link 22 and the outer peripheral surface 12a of the output shaft 12 bent in a wave shape. The connecting rod 19 is connected to the projecting portions 22 b and 22 b provided on the outer periphery of the swing link 22 via pins 19 c and clips 29 and 29.

  The one-way clutch 21 includes a cage 31 for supporting the engagement springs 24 that urge the rollers 25 in the circumferential direction. The cage 31 includes a pair of inner rings 36 and 36 of angular ball bearings 34 and 34, which will be described later, and twelve spring support rods 33 that are arranged at equal intervals in the circumferential direction and connect the pair of inner rings 36 and 36 to each other. The pair of inner rings 36 are arranged on both sides in the axial direction of the twelve rollers 25. The twelve spring support rods 33 are arranged between the twelve rollers 25. The cage 31 is coupled to the output shaft 12 in a relatively non-rotatable manner by fitting the inner circumferential portions of the inner rings 36, 36 to the outer circumferential surface 12a of the output shaft 12 bent in a wave shape so as to be slidable in the axial direction.

  The engagement spring 24 is formed by bending a single elastic plate with an S-shaped cross section, one end of which is fixed to the spring support rod 33 of the cage 31 by welding or the like, and the other end is in contact with the roller 25 to be elastic. A deformable biasing portion 24a is formed.

  Further, between the swing link 22 and the output shaft 12, double-row angular ball bearings 34 are disposed on both sides in the axial direction of the rollers 25, and the swing link 22 is formed by these angular ball bearings 34. And the output shaft 12 is connected so that relative rotation is possible, maintaining a concentric state. Each angular ball bearing 34 is formed by arranging a plurality of balls 37... In two rows between outer rings 35 and 35 and an inner ring 36, and the outer rings 35 and 35 are integrally formed at the axial ends of the swing links 22 and 22. The common inner ring 36 is formed of a separate member and is supported on the outer periphery of the output shaft 12 so as to be slidable in the axial direction.

  In addition to the double row angular ball bearings 34 described above, the angular ball bearings that support the swing links 22... Are arranged adjacent to the ball bearings 27, 27 that support the output shaft 12 or the roller bearings 28. There is a row of angular ball bearings 34.

  An axial spring 38 is supported on one of a pair of angular ball bearings 34, 34 of each one-way clutch 21, and a plurality of projections 38 a projecting from the inner periphery of the axial spring 38 is one of the axial directions of the rollers 25. By elastically abutting and urging the end surface, the other end surface in the axial direction of the rollers 25 is pressed against the inner ring 36 of the angular ball bearing 34, and the posture is stabilized.

  A ball bearing 27 that supports both ends of the output shaft 12 includes an outer ring 40 fixed to the transmission case 26, an inner ring 41 fixed to the output shaft 12, and a plurality of balls 42 disposed between the outer ring 40 and the inner ring 41. … And. The roller bearing 28 that supports the central portion of the output shaft 12 includes an outer ring 43 fixed to the transmission case 26, an inner ring 44 fixed to the output shaft 12, and a plurality of rollers disposed between the outer ring 43 and the inner ring 44. 45.

  As schematically shown in FIG. 10, the six one-way clutches 21 are composed of # 1 one-way clutch 211, # 2 one-way clutch 212, # 3 one-way clutch 213, # 4 one-way in order from the right side to the left side in the axial direction. The clutches 21 4, # 5 one-way clutch 215, and # 6 one-way clutch 216 are named. The # 1 one-way clutch 21 1, # 2 one-way clutch 21 2 and # 3 one-way clutch 213 arranged between the right ball bearing 27 and the central roller bearing 28 constitute a first one-way clutch group 21A. The # 4 one-way clutch 21 4, the # 5 one-way clutch 215 and the # 6 one-way clutch 216 arranged between the left ball bearing 27 constitute a second one-way clutch group 21B.

  Angular ball bearings 34 of # 1 to # 3 one-way clutches 21 1, 21 2, and 21 3 of the first one-way clutch group 21A are sandwiched between the right ball bearing 27 and the central roller bearing 28 to be pressurized in the axial direction. The Also, the angular ball bearings 34 of # 4 to # 6 one-way clutches 21 4, 215, 216 of the second one-way clutch group 21B are sandwiched between the central roller bearing 28 and the left ball bearing 27 so as to be pressurized in the axial direction. Is done.

  The six one-way clutches 21 are engaged in the order of # 1 one-way clutch 211, # 6 one-way clutch 216, # 2 one-way clutch 212, # 4 one-way clutch 213, # 3 one-way clutch 213, and # 5 one-way clutch 215. The # 1 one-way clutch 211 starts engaging while the # 3 one-way clutch 213 is engaged, and the # 6 one-way clutch 216 starts engaging while the # 5 one-way clutch 215 is engaged. The # 2 one-way clutch 21 2 starts to be engaged while the # 1 one-way clutch 21 1 is engaged, while the # 4 one-way clutch 21 4 starts to be engaged while the # 6 one-way clutch 21 6 is engaged, and the # 2 one-way clutch 21 2 is engaged. # 3 one-way clutch 213 starts engaging while # 4 one-wake is engaged. ♯5 the one-way clutch 215 during engagement of the pitch 214 to start the engagement.

  Of the # 1 to # 3 one-way clutches 211 to 213 in the first one-way clutch group 21A, the axial spring 381 of the # 1 one-way clutch 211 is arranged on the right side of the roller 251... And the axial spring 382 of the # 2 one-way clutch 212 is The axial spring 383 of the # 3 one-way clutch 213 is arranged on the left side of the rollers 253. Of the # 4 to # 6 one-way clutches 21 4 to 216 of the second one-way clutch group 21B, the axial spring 384 of the # 4 one-way clutch 214 is disposed on the right side of the roller 254... And the axial spring 385 of the # 5 one-way clutch 215. Is disposed on the right side of the rollers 255, and the axial spring 386 of the # 6 one-way clutch 216 is disposed on the left side of the rollers 256. That is, the second one-way clutch group 21B corresponds to the first one-way clutch group 21A that is translated in the axial direction as it is.

  Next, the operation of the embodiment of the present invention having the above configuration will be described.

  First, the operation of one transmission unit U of the continuously variable transmission T will be described. When the rotation shaft 14 a of the speed change actuator 14 is rotated relative to the input shaft 11, the carrier 16 rotates about the axis L <b> 1 of the input shaft 11. At this time, the center O of the carrier 16, that is, the center of the equilateral triangle formed by the first pinion 15 and the two second pinions 17, 17 rotates around the axis L 1 of the input shaft 11.

  3 and 5 show a state in which the center O of the carrier 16 is on the opposite side of the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). The amount of eccentricity becomes maximum, and the transmission ratio of the continuously variable transmission T becomes the minimum OD (overdrive) state. 4 and 6 show a state in which the center O of the carrier 16 is on the same side as the output shaft 12 with respect to the first pinion 15 (that is, the input shaft 11). At this time, the eccentric disk 18 with respect to the input shaft 11 The amount of eccentricity becomes zero, and the transmission ratio of the continuously variable transmission T becomes an infinite GN (geared neutral) state.

  In the OD state shown in FIG. 5, when the input shaft 11 is rotated by the engine E and the rotation shaft 14 a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotation shaft 14 a, the carrier 16, With the one pinion 15, the two second pinions 17 and 17, and the eccentric disk 18 being integrated, the pinion 15 rotates eccentrically around the input shaft 11 (see arrow A). While rotating from FIG. 5A through FIG. 5B to the state of FIG. 5C, the ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the swing link 22 pivotally supported by the pin 19c at the tip of the rod portion 19a in the counterclockwise direction (see arrow B). 5A and 5C show both ends of the rotation of the swing link 22 in the arrow B direction.

  When the swing link 22 rotates in the direction of arrow B in this way, the rollers 25... Engage with the wedge-shaped space between the swing link 22 of the one-way clutch 21 and the output shaft 12, and the rotation of the swing link 22 rotates the output shaft. Therefore, the output shaft 12 rotates counterclockwise (see arrow C).

  When the input shaft 11 and the first pinion 15 further rotate, the eccentric disk 18 in which the ring gear 18a is engaged with the first pinion 15 and the second pinion 17, 17 rotates eccentrically in the counterclockwise direction (see arrow A). While rotating from the state shown in FIG. 5C to the state shown in FIG. 5A, the ring portion 19b is supported on the outer periphery of the eccentric disk 18 via the ball bearing 20 so as to be relatively rotatable. The connecting rod 19 rotates the swing link 22 pivotally supported by the pin 19c at the tip of the rod portion 19a in the clockwise direction (see arrow B '). 5C and 5A show both ends of the rotation of the swing link 22 in the direction of the arrow B ′.

  When the swing link 22 rotates in the direction of the arrow B ′ in this way, the rollers 25 are pushed out from the wedge-shaped space between the swing link 22 and the output shaft 12 while compressing the engagement springs 24. The swing link 22 slips with respect to the output shaft 12, and the output shaft 12 does not rotate.

  As described above, when the swing link 22 reciprocates, the output shaft 12 rotates counterclockwise (see arrow C) only when the swing link 22 rotates counterclockwise (see arrow B). The output shaft 12 rotates intermittently.

  FIG. 6 shows the operation when the continuously variable transmission T is operated in the GN state. At this time, since the position of the input shaft 11 coincides with the center of the eccentric disk 18, the eccentric amount of the eccentric disk 18 with respect to the input shaft 11 becomes zero. In this state, when the input shaft 11 is rotated by the engine E and the rotating shaft 14a of the speed change actuator 14 is rotated at the same speed as the input shaft 11, the input shaft 11, the rotating shaft 14a, the carrier 16, the first pinion 15, 2 In a state where the second pinions 17 and 17 and the eccentric disk 18 are integrated, the input pin 11 is rotated eccentrically in the counterclockwise direction (see arrow A). However, since the eccentric amount of the eccentric disk 18 is zero, the stroke of the reciprocating motion of the connecting rod 19 is also zero, and the output shaft 12 does not rotate.

  Accordingly, if the speed change actuator 14 is driven and the position of the carrier 16 is set between the OD state of FIG. 3 and the GN state of FIG. 4, operation at an arbitrary speed ratio between the infinite speed ratio and the minimum speed ratio is performed. Is possible.

  In the continuously variable transmission T, the phases of the eccentric disks 18 of the six transmission units U arranged in parallel are shifted by 60 ° from each other, so that the six transmission units U alternately transmit the driving force. In other words, any one of the six one-way clutches 21 is always in an engaged state, so that the output shaft 12 can be continuously rotated.

  Next, the operation of the one-way clutch 21 will be described.

  FIG. 10 shows a state in which the # 3 one-way clutch 213 is engaged. The diameter of the swing link 223 of the # 3 one-way clutch 213 is increased by the reaction force received from the rollers 253. Since backlash occurs in the inner rings 3623 and 363 of the bearings 343 and 343, the inner ring 3623 disposed between the # 2 one-way clutch 212 and the # 3 one-way clutch 213 may move to the left in the axial direction.

  While the # 3 one-way clutch 213 is engaged, the # 1 one-way clutch 211 in the same first one-way clutch group 21A starts engaging, but the rollers 253... 12 is fixed so as not to move in the axial direction, and since the axial spring 383 is not interposed between the right end surface of the rollers 253 and the left end surface of the inner ring 3623, the inner ring 3623 moves to the left in the axial direction. It becomes impossible. As a result, even if a leftward load is applied from the connecting rod 19 to the swing link 221 of the # 1 one-way clutch 211 to be engaged next, the load is applied to the swing link 221, inner ring 3612, swing link 222, and inner ring. 3623 is supported by the fixed rollers 253... So that the swing link 221 of the # 1 one-way clutch 211 is prevented from being displaced to the left, and the # 1 one-way clutch 211 can be smoothly engaged. It becomes.

  FIG. 11 shows a state in which the # 5 one-way clutch 215 is engaged. The diameter of the swing link 225 of the # 5 one-way clutch 215 is increased by the reaction force received from the rollers 255, so that the angular balls on both sides thereof are expanded. Since backlash occurs in the inner rings 3645 and 3656 of the bearings 345 and 345, the inner ring 3656 disposed between the # 5 one-way clutch 215 and the # 6 one-way clutch 216 may move to the right in the axial direction.

  While the # 5 one-way clutch 215 is engaged, the # 6 one-way clutch 216 in the same second one-way clutch group 21B starts to be engaged, but the roller 255 of the # 5 one-way clutch 215 being engaged is the output shaft. 12 is fixed so as not to move in the axial direction, and the axial spring 386 is not interposed between the left end surface of the rollers 255 and the right end surface of the inner ring 3656, so that the inner ring 3656 moves to the right in the axial direction. It becomes impossible. As a result, even if a rightward load is applied from the connecting rod 19 to the swing link 226 of the # 6 one-way clutch 216 which starts engagement, the load is supported by the fixed roller 255 through the inner ring 3656. Therefore, the swing link 226 of the # 6 one-way clutch 216 is prevented from being displaced to the right, and the # 6 one-way clutch 216 can be smoothly engaged.

  FIG. 12 shows a state in which the # 1 one-way clutch 211 is engaged. The diameter of the swing link 221 of the # 1 one-way clutch 211 is increased by the reaction force received from the rollers 251,. Since backlash occurs in the inner rings 361 and 3612 of the bearings 341 and 341, there is a possibility that the inner ring 3612 arranged between the # 1 one-way clutch 211 and the # 2 one-way clutch 212 moves to the right in the axial direction.

  While the # 1 one-way clutch 211 is engaged, the # 2 one-way clutch 212 in the same first one-way clutch group 21A starts to be engaged, but the rollers 251. 12 is fixed so as not to move in the axial direction, and the axial spring 381 is not interposed between the left end surface of the rollers 251 and the right end surface of the inner ring 3612. Therefore, the inner ring 3612 moves to the right in the axial direction. It becomes impossible. As a result, even if a rightward load is applied from the connecting rod 19 to the swing link 22 2 of the # 2 one-way clutch 21 2 that starts the next engagement, the load is supported by the fixed rollers 251 through the inner ring 3612. Therefore, the swing link 22 2 of the # 2 one-way clutch 21 2 is prevented from being displaced to the right and the # 2 one-way clutch 21 2 can be smoothly engaged.

  FIG. 13 shows a case where the # 4 one-way clutch 214 starts to be engaged while the # 6 one-way clutch 216 is engaged. In the same manner as the operation described with reference to FIG. The swing link 22 4 is prevented from moving in the left direction, and the # 4 one-way clutch 21 4 can be smoothly engaged.

  FIG. 14 shows a case in which the # 3 one-way clutch 213 starts to be engaged while the # 2 one-way clutch 21 2 is engaged. In the same manner as the operation described in FIG. The swinging link 223 is prevented from moving in the right direction, and the # 3 one-way clutch 213 can be smoothly engaged.

  FIG. 15 shows a case in which the # 5 one-way clutch 215 starts to be engaged while the # 4 one-way clutch 214 is engaged. In the same manner as the operation described with reference to FIG. The swing link 225 is prevented from moving in the right direction, and the # 5 one-way clutch 215 can be smoothly engaged.

  As described above, when the # 3 one-way clutch 213 at the left end of the first one-way clutch group 21A is engaged and the rollers 253 are fixed to the output shaft 12 (see FIG. 10), the right end of the rollers 253. Since the axial spring 383 of the # 3 one-way clutch 213 does not exist on the surface, even if the swing link 221 of the # 1 one-way clutch 211 located next to the # 3 one-way clutch 213 tries to move to the left side. The movement of the # 1 one-way clutch 211 is prevented from moving to the left side of the swing link 221, and the # 1 one-way clutch 211 can be smoothly engaged by preventing the movement by the fixed rollers 253. Can do.

  At this time, if the axial spring 383 of the # 3 one-way clutch 213 is disposed on the right side of the roller 253..., The inner ring 3623 can move to the left side while compressing the axial spring 386 3. Accordingly, the movement of the swing link 221 of 21 1 or the swing link 22 2 of the # 2 one-way clutch 21 2 to the left cannot be prevented.

  When the right end # 1 one-way clutch 21 1 of the first one-way clutch group 21A is engaged and the rollers 251 are fixed to the output shaft 12 (see FIG. 12), the left end surface of the rollers 251. Since the axial spring 381 of the one-way clutch 211 does not exist, even if the swing link 222 of the # 2 one-way clutch 212, which is located on the left side of the # 1 one-way clutch 211 and then engages, moves to the right By blocking with the fixed rollers 251..., The movement of the # 2 one-way clutch 21 2 to the right side of the swing link 22 2 can be blocked, and the # 2 one-way clutch 212 can be smoothly engaged.

  At this time, if the axial spring 381 of the # 1 one-way clutch 211 is disposed on the left side of the rollers 251,..., The inner ring 3612 can move to the right side while compressing the axial spring 381, so that the # 2 one-way clutch 212. It is impossible to prevent the rocking link 22 2 from moving to the right side.

  When the # 2 one-way clutch 21 2 at the center of the first one-way clutch group 21A is engaged and the rollers 252,... Are fixed to the output shaft 12 (see FIG. 14), the left end surface of the rollers 252,. 2 Since the axial spring 382 of the one-way clutch 21 2 does not exist, even if the swing link 223 of the # 3 one-way clutch 21 3 which is located on the left side of the # 2 one-way clutch 21 2 and then engages moves to the right side, the movement is continued. By blocking with the fixed rollers 252,..., The movement of the # 3 one-way clutch 213 to the right side of the swing link 223 can be blocked, and the # 3 one-way clutch 213 can be smoothly engaged.

  At this time, if the axial spring 382 of the # 2 one-way clutch 212 is disposed on the left side of the roller 252,..., The inner ring 3623 can move to the right side while compressing the axial spring 382, so that the # 3 one-way clutch 213. It becomes impossible to prevent the movement of the rocking link 223 to the right.

  As described above, the rollers 251... 253... Of the first and third one-way clutches 21 1, 21 3 positioned at both axial ends of the first one-way clutch group 21 A are connected to the inner ring 41 of the ball bearing 27 or the roller bearing 28. The # 2 one-way clutch 21 2 is urged axially inward (in a direction approaching each other) by axial springs 38 1, 383 arranged between the inner rings 361, 363 abutting against the inner ring 44 and located in the axial center. Of the first one-way clutch group 21A by urging the rollers 252... To the left side by the axial spring 382 toward the # 3 one-way clutch 213 which starts engagement during the engagement. All of the clutches 211, 212, and 213 can be smoothly engaged.

  The # 1 one-way clutch 211, # 2 one-way clutch 212, and # 3 one-way clutch 213 of the first one-way clutch group 21A have been described above. However, the # 4 one-way clutch 214, # 5 one-way clutch of the second one-way clutch group 21B. The same applies to 215 and # 6 one-way clutch 216.

  The arrangement of the first to third one-way clutches 21 1 to 213 of the first one-way clutch group 21A, the fourth to fifth one-way clutches 21 4 to 216 and the axial springs 381 to 386 of the second one-way clutch group 21B from another viewpoint. When viewed, the direction in which the axial spring 38 of the currently engaged one-way clutch 21 urges the roller 25 is the direction toward the other one-way clutch 21 that starts engagement while the one-way clutch 21 is engaged. Thus, the other one-way clutch 21 that starts engagement can be prevented from moving in the axial direction of the swing link 22.

  That is, in the first one-way clutch group 21A, the axial spring 383 of the # 3 one-way clutch 213 being engaged urges the rollers 253... To the right toward the # 1 one-way clutch 211 to be engaged next. 10 (see FIG. 10), the axial spring 382 of the engaged second clutch 19 latch 21 2 urges the rollers 25 2 to the left toward the # 3 one-way clutch 213 which starts the next engagement. The axial spring 381 of the engaged # 1 one-way clutch 211 biases the rollers 251... To the left toward the # 2 one-way clutch 212 to be engaged next (see FIG. 14). reference).

  Further, in the second one-way clutch group 21B, the axial spring 386 of the # 6 one-way clutch 216 being engaged urges the rollers 256 to the right toward the # 4 one-way clutch 213 to be engaged next. 13 (see FIG. 13), the axial spring 385 of the # 5 one-way clutch 215 being engaged urges the rollers 255 to the left toward the # 6 one-way clutch 216 to be engaged next (see FIG. 13). 11), the axial spring 384 of the # 4 one-way clutch 213 being engaged urges the rollers 254... To the left toward the # 5 one-way clutch 215 which starts the next engagement (see FIG. 15). .

  Further, as the restricting means for restricting both ends of the first and third one-way clutches 21 1 and 21 3 at both ends of the first one-way clutch group 21A, the inner rings 41 and 44 of the existing ball bearing 27 and roller bearing 28 supporting the output shaft 12 are used. As a restricting means for restricting both ends of the fourth and sixth one-way clutches 21 4 and 216 at both ends of the second one-way clutch group 21B, the existing roller bearing 28 and ball bearing 27 for supporting the output shaft 12 are used. Since the inner rings 44 and 41 are used, it is possible to reduce the number of parts and the axial dimension of the output shaft 12 as compared with the case where a special restricting member is provided.

Second embodiment

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

  In the second embodiment, six one-way clutches 21... Are replaced with a first one-way clutch group 21A composed of # 1 one-way clutch 211 and # 2 one-way clutch 212, and # 3 one-way clutch 213 and # 4 one-way clutch 214. And a third one-way clutch group 21C consisting of a # 5 one-way clutch 215 and a # 6 one-way clutch 216.

  The positions of the inner rings 36, 36 of the pair of angular ball bearings 34, 34 located at both axial ends of the first to third one-way clutch groups 21A, 21B, 21C are fixed to the output shafts 12 on both axial sides. The clips 46 and 46 are regulated. At this time, the position of the inner ring 36 at the left end of the first one-way clutch group 21A and the inner ring 36 at the right end of the second one-way clutch group 21B are restricted by the common clip 46, and the left end inner ring 36 of the second one-way clutch group 21B is Since the position of the inner ring 36 and the inner ring 36 at the right end of the third one-way clutch group 21C is restricted by a common clip 46, the total number of clips 46 is four.

  The order in which the # 1 one-way clutch 211 to the # 6 one-way clutch 216 are engaged can be arbitrarily set, but the other one starts engagement while one of the two one-way clutches 21 and 21 in the same group is engaged. In this case, the same effect as that of the first embodiment is achieved.

  For example, if the # 1 one-way clutch 211 starts engaging when the # 2 one-way clutch 212 of the first one-way clutch group 21A is engaged and the swing link 222 expands, the # 1 one-way clutch starts. Since the inner ring 3612 disposed between the clutch 211 and the # 2 one-way clutch 212 contacts the right end surface of the fixed roller 252,... Of the # 2 one-way clutch 212, the movement to the left side is restricted. Is prevented from moving to the left side and the # 1 one-way clutch 211 can be smoothly engaged.

  Conversely, when the # 2 one-way clutch 21 2 starts engaging when the # 1 one-way clutch 21 1 of the first one-way clutch group 21A is engaged and the swing link 221 expands, # 1 Since 3612 disposed between the one-way clutch 211 and the # 2 one-way clutch 212 contacts the left end face of the fixed roller 251... Of the # 1 one-way clutch 211, the movement to the right side is restricted. Is prevented from moving to the right side and the # 2 one-way clutch 21 2 can be smoothly engaged.

  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, six one-way clutches 21 are provided, but the number of one-way clutches is not limited to six, and two one-way clutches or three one-way clutches sandwiched between a pair of regulating members. As long as it includes a clutch, the present invention can be applied to these two or three one-way clutches.

  The regulating means of the present invention is not limited to the inner ring 41 of the ball bearing 27, the inner ring 44 of the roller bearing 28, or the clip 46 in the embodiment, and may be any means.

  The axial spring of the present invention is not limited to the leaf spring of the embodiment, and may be an arbitrary spring.

  The angular bearing of the present invention is not limited to the angular ball bearing 34 of the embodiment, and may be an arbitrary bearing such as an angular roller bearing.

11 Input shaft 12 Output shaft 12a Outer peripheral surface 18 Eccentric disc (eccentric member)
19 Connecting rod 21 One-way clutch 21A First one-way clutch group (one-way clutch group)
21B Second one-way clutch group (one-way clutch group)
21C Third one-way clutch group (one-way clutch group)
22 Oscillating link 22a Inner peripheral surface 25 Roller 26 Mission case (casing)
27 Ball bearing (shaft support bearing)
28 Roller bearing (shaft support bearing)
34 Angular Ball Bearing (Angular Bearing)
36 Inner ring 38 Axial spring 41 Inner ring (regulation means)
44 Inner ring (regulation means)
46 clips (regulation means)
E Engine (drive source)
U transmission unit

Claims (5)

A plurality of transmission units (U) that change the rotation of the input shaft (11) connected to the drive source (E) and transmit the rotation to the output shaft (12) are juxtaposed in the axial direction,
Each of the transmission units (U) includes an eccentric member (18) whose amount of eccentricity from the axis of the input shaft (11) is variable and rotating together with the input shaft (11), and an output shaft (12). A swing link (22) supported in a relatively rotatable manner, a one-way clutch (21) disposed between the output shaft (12) and the swing link (22), the eccentric member (18) and the swing link. A connecting rod (19) for connecting a dynamic link (22) and an axially opposite side of the one-way clutch (21) are arranged coaxially with respect to the output shaft (12). A pair of angular bearings (34) that
The three one-way clutches (21) included in the three transmission units (U) juxtaposed in the axial direction constitute a one-way clutch group (21A, 21B), and the one-way clutch group (21A, 21B) Each of the included one-way clutches (21) includes a plurality of rollers (25) disposed between an inner peripheral surface (22a) of the swing link (22) and an outer peripheral surface (12a) of the output shaft (12). And an axial spring (38) for urging the roller (25) to either side in the axial direction,
The angular bearing (34) includes an inner ring (36) that is slidably disposed on an outer periphery of the output shaft (12) and supports the axial spring (38), and the one-way clutch group (21A, 21B). The two inner rings (36) sandwiched between a pair of the one-way clutches (21) adjacent to each other are integrally formed and are located at both ends in the axial direction of the one-way clutch group (21A, 21B). The inner ring (36) on the outer side in the axial direction of each of the one-way clutches (21) is in contact with the restricting means (41, 44) provided on the output shaft (12) and is restricted from moving outward in the axial direction. A power transmission device for a vehicle,
The rollers (25) of the two one-way clutches (21) located at both axial ends of the one-way clutch group (21A, 21B) are in contact with the restricting means (41, 44). The one-way clutch (21) located in the axially central portion of the one-way clutch group (21A, 21B) while being urged axially inward by the axial spring (38) disposed between The roller (25) of the two one-way clutches (21) is directed toward the one-way clutch (21) on the side of starting engagement while the one one-way clutch (21) is engaged. A vehicle power transmission device that is biased by an axial spring (38). # 1 one-way clutch, # 2 one-way clutch, # 3 one-way clutch, # 4 one-way clutch, # 5 one-way clutch and # 6 one-way clutch arranged in order from one axial end to the other axial end; The # 1 to # 3 one-way clutches constitute the first one-way clutch group (21A), the # 4 to # 6 one-way clutches constitute the second one-way clutch group (21B), and the # 1 to # 6 one-way clutches # 1 → # 6 → # 2 → # 4 → # 3 → # 5
The roller (25) of the # 1 one-way clutch is biased toward the # 2 one-way clutch by the axial spring (38), and the roller (25) of the # 2 one-way clutch is # 3 one-way by the axial spring (38). Energized toward the clutch, the roller (25) of the # 3 one-way clutch is energized toward the # 2 one-way clutch with the axial spring (38),
The roller (25) of the # 4 one-way clutch is biased toward the # 5 one-way clutch by the axial spring (38), and the roller (25) of the # 5 one-way clutch is # 6 one-way by the axial spring (38). The vehicle according to claim 1, wherein the roller (25) of the # 6 one-way clutch is urged toward the clutch, and the roller (25) of the # 6 one-way clutch is urged toward the # 5 one-way clutch by the axial spring (38). Power transmission device. The said restricting means (41, 44) is an inner ring (41, 44) of a shaft support bearing (27, 28) for supporting the output shaft (12) on a casing (26). Alternatively, the vehicle power transmission device according to claim 2 . A plurality of transmission units (U) that change the rotation of the input shaft (11) connected to the drive source (E) and transmit the rotation to the output shaft (12) are juxtaposed in the axial direction,
Each of the transmission units (U) includes an eccentric member (18) whose amount of eccentricity from the axis of the input shaft (11) is variable and rotating together with the input shaft (11), and an output shaft (12). A swing link (22) supported in a relatively rotatable manner, a one-way clutch (21) disposed between the output shaft (12) and the swing link (22), the eccentric member (18) and the swing link. A connecting rod (19) for connecting a dynamic link (22) and an axially opposite side of the one-way clutch (21) are arranged coaxially with respect to the output shaft (12). A pair of angular bearings (34) that
The two one-way clutches (21) included in the two transmission units (U) juxtaposed in the axial direction constitute a one-way clutch group (21A, 21B, 21C), and the one-way clutch group (21A, 21B). , 21C) is disposed between the inner peripheral surface (22a) of the swing link (22) and the outer peripheral surface (12a) of the output shaft (12). A plurality of rollers (25), and an axial spring (38) for urging the rollers (25) to either side in the axial direction,
The angular bearing (34) includes an inner ring (36) that is slidably disposed on an outer periphery of the output shaft (12) and supports the axial spring (38), and the one-way clutch group (21A, 21B). , 21C), the two inner rings (36) sandwiched between the two one-way clutches (21) are integrally formed, and the two one-way clutches (21A, 21B, 21C) 21) The inner ring (36) on the outer side in the axial direction of 21) is a vehicle power transmission device that abuts against the restricting means (46) provided on the output shaft (12) and is restricted from moving outward in the axial direction. ,
The rollers (25) of the two one-way clutches (21) of the one-way clutch group (21A, 21B, 21C) are disposed between the inner ring (36) contacting the restricting means (46). The vehicular power transmission device is biased inward in the axial direction by the axial spring (38). A plurality of transmission units (U) that change the rotation of the input shaft (11) connected to the drive source (E) and transmit the rotation to the output shaft (12) are juxtaposed in the axial direction,
Each of the transmission units (U) includes an eccentric member (18) whose amount of eccentricity from the axis of the input shaft (11) is variable and rotating together with the input shaft (11), and an output shaft (12). A swing link (22) supported in a relatively rotatable manner, a one-way clutch (21) disposed between the output shaft (12) and the swing link (22), the eccentric member (18) and the swing link. A connecting rod (19) for connecting a dynamic link (22) and an axially opposite side of the one-way clutch (21) are arranged coaxially with respect to the output shaft (12). A pair of angular bearings (34) that
Two or three one-way clutches (21) included in two or three transmission units (U) juxtaposed in the axial direction constitute a one-way clutch group (21A, 21B, 21C), and the one-way clutch Each of the one-way clutches (21) included in the clutch group (21A, 21B, 21C) is between the inner peripheral surface (22a) of the swing link (22) and the outer peripheral surface (12a) of the output shaft (12). A plurality of rollers (25) disposed in the axial direction, and an axial spring (38) for urging the rollers (25) to any side in the axial direction,
The angular bearing (34) includes an inner ring (36) that is slidably disposed on an outer periphery of the output shaft (12) and supports the axial spring (38), and the one-way clutch group (21A, 21B). , 21C), the two inner rings (36) sandwiched between a pair of mutually adjacent one-way clutches (21) are integrally formed, and both end portions in the axial direction of the one-way clutch group (21A, 21B, 21C) The inner ring (36) on the outer side in the axial direction of the two one-way clutches (21) positioned in the position is moved outward in the axial direction by the restricting means (41, 44, 46) provided on the output shaft (12). A vehicle power transmission device to be regulated,
Of the two or three one-way clutches (21) included in the one-way clutch group (21A, 21B, 21C), the axial spring (38) of the currently engaged one-way clutch (21) is the roller ( 25) The power transmission device for a vehicle, characterized in that the direction of energizing 25) is a direction toward another one-way clutch (21) that starts engagement while the one-way clutch (21) is engaged.

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