Electric continuously variable transmission

Abstract

To improve assemblability of an electric continuously variable transmission.SOLUTION: In an electric continuously variable transmission comprising an actuator that changes a groove width of a pulley to be controlled, a pulley drive arm 71 and a nut member 75 of a feed screw mechanism 73 are connected via a ball joint 76, a ball bearing 79 can be fitted into a ball housing 78 of the ball joint 76 through an opening 78d on the nut member 75 side, and when a connection pin 77 is inclined from an upright state relative to the ball housing 78, the outer peripheral part of a flange part 77b of the connection pin 77 can be in contact with the inner peripheral part of a seat bore part 78b of the ball housing 78.SELECTED DRAWING: Figure 5

Description

Technical Field

[0001] The present invention relates to an electric continuously variable transmission.

Background Art

[0002] In recent years, in order to enable more people to access affordable, reliable, sustainable, and advanced energy, research and development related to improving fuel efficiency, which contributes to energy efficiency, has been carried out. In a belt-type continuously variable transmission employed in saddle-riding type vehicles such as motorcycles, the centrifugal weight is used to change the transmission ratio according to the rotational speed. However, in order to further improve fuel efficiency, it is preferable to perform shift control considering more conditions rather than shifting only according to the rotational speed. For example, Patent Document 1 describes an electric belt-type continuously variable transmission including a driving pulley supported by an input shaft, a driven pulley supported by an output shaft, a transmission belt wound around both pulleys, and an actuator driven by a control device to apply an axial force to one of the two pulleys to change the groove width.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the above conventional structure, the actuator includes a motor that generates rotational power and a feed screw mechanism that converts the rotational power of the motor into axial power of the controlled pulley. A pulley driving member is connected to the controlled pulley so as to be relatively rotatable, and this pulley driving member faces the operating member of the feed screw mechanism in the radial direction, and these pulley driving member and operating member are connected via a ball joint. A ball joint comprises, for example, a connecting pin fixed to a pulley drive member, a ball housing provided on, for example, an operating member, and a ball bearing supported by the connecting pin while housed within the ball housing. The ball housing is cylindrical with a closed bottom and is positioned with its bottom facing the pulley drive member. A through-hole smaller in diameter than the ball bearing is formed in the bottom of the ball housing, and the support shaft portion of the connecting pin is inserted through this through-hole. A stopper surface is formed on the inner circumference of the through-hole, which contacts the outer surface of the support shaft portion to restrict the rotation angle of the connecting pin. A ball bearing is fitted into the ball housing from the opening side, and the support shaft portion of the connecting pin is inserted through the through-hole into the connecting hole of the ball bearing. This connects the pulley drive member and the operating member via a ball joint. However, in the conventional configuration described above, the ball bearing is fitted into the ball housing independently, and the support shaft portion of the connecting pin, which has passed through the through hole, is inserted into the connecting hole of the ball bearing. This presented a challenge in that assembly around the ball joint was difficult.

[0005] This invention aims to improve the ease of assembly of an electric continuously variable transmission in order to solve the above-mentioned problems. Ultimately, this will contribute to energy efficiency. [Means for solving the problem]

[0006] As a means of solving the above problems, a first aspect of the present invention includes a drive pulley (46) supported on an input shaft (12), a driven pulley (48) supported on an output shaft (47), a transmission belt (49) wrapped around the drive pulley (46) and the driven pulley (48), a transmission case (15a) housing the drive pulley (46), the driven pulley (48), and the transmission belt (49), and a control unit attached to the transmission case (15a) and driven by a control unit, with one of the drive pulley (46) and the driven pulley (48) designated as the controlled pulley (46), and this controlled pulley An electric continuously variable transmission comprising an actuator (50) that applies axial force to a movable sheave (52) of a pulley (46) to change the groove width, wherein the actuator (50) comprises a motor (56) that generates rotational power and a lead screw mechanism (73) that converts the rotational power of the motor (56) into axial power of the drive pulley (46), and a pulley drive member (71) that can apply axial thrust to the movable sheave (52) is connected to the drive pulley (46) so as to be rotatable relative to it, and the pulley drive member (71) and the actuating member (75) of the lead screw mechanism (73) This is connected via a ball joint (76), the ball joint (76) comprising a connecting pin (77) fixed to one of the pulley drive member (71) and the operating member (75), a ball housing (78) provided on the other of the pulley drive member (71) and the operating member (75), and a ball bearing (79) housed within the ball housing (78) and supported by the connecting pin (77), the ball housing (78) being a bottomed cylindrical shape with an opening (78d) on one side of the pulley drive member (71) and the operating member (75), and the opening (78 d) The ball bearing (79) can be inserted into the connecting pin (77), and the connecting pin (77) comprises a support shaft portion (77a) that is fitted into the ball bearing (79), and a flange portion (77b) provided on the base end side of the support shaft portion (77a) and formed to be larger in diameter than the ball bearing (79), and the ball housing (78) comprises a support wall portion (78a) having an inner diameter (D1) capable of supporting the ball bearing (79), and a counterbore portion (78b) connected to the opening (78d) side of the support wall portion (78a) and forming an opening (78d) that is larger in diameter than the support wall portion (78a) and the flange portion (77b),When the connecting pin (77) is tilted from an upright position relative to the ball housing (78), the outer circumference (77b1) of the flange portion (77b) can come into contact with the inner circumference (78b1) of the counterbore portion (78b). With this configuration, when the connecting pin is tilted, the outer circumference of the flange portion of the connecting pin comes into contact with the inner circumference of the counterbore on the opening side of the ball housing, thereby forming a stopper structure that limits the tilt (oscillation) of the connecting pin between the counterbore and the flange portion. Therefore, while allowing the oscillation of the connecting pin to be tolerated and absorbing component tolerances and assembly tolerances, the oscillation angle of the connecting pin can be limited, and the thrust of the lead screw mechanism can be accurately transmitted to the pulley drive member. By making the opening side of the ball housing larger in diameter than the ball bearing and flange portion, the connecting pin with the ball bearing fitted can be inserted into the ball housing from the opening side. Therefore, the ease of assembly around the ball joint can be improved.

[0007] A second aspect of the present invention is that, in the first aspect described above, the flange portion (77b) is at least partially located within the counterbore portion (78b). With this configuration, the flange portion fits into the counterbore, effectively sealing the opening of the ball housing and preventing foreign matter from entering the ball housing. The flange portion also helps to prevent the grease filled into the ball housing from leaking out.

[0008] A third aspect of the present invention is that, in the first or second aspect described above, a flange end (77b1) extending radially of the connecting pin (77) is formed between the outer circumferential portion (77a1) of the support shaft portion (77a) and the outer circumferential portion (77b3) of the flange portion (77b), and an inner circumferential step portion (78c) extending radially of the ball housing (78) is formed between the inner circumferential portion (78a1) of the support wall portion (78a) and the inner circumferential portion (78b1) of the counterbore portion (78b), and in a state in which the connecting pin (77) is upright with respect to the ball housing (78), the inner circumferential step portion (78c) and the flange end (77b1) overlap each other when viewed from the axial direction and face each other with a gap (s1) in the axial direction. With this configuration, when the connecting pin is in an upright position, the inner circumferential step portion and the flange end overlap each other when viewed from the axial direction, and face each other with a gap in the axial direction. This allows the flange portion to suppress the outflow of grease filled in the ball housing, while absorbing tolerances such as the distance between the crankshaft and the shaft, thereby improving the operation of the ball joint.

[0009] A fourth aspect of the present invention is that, in any one of the first to third aspects described above, the ball housing (78) comprises a first outer peripheral portion (78f) formed radially outward of the support wall portion (78a), a second outer peripheral portion (78g) formed radially outward of the counterbore portion (78b) and having a smaller outer diameter than the first outer peripheral portion (78f), and an outer peripheral stepped portion (78h) formed between the first outer peripheral portion (78f) and the second outer peripheral portion (78g) and extending radially, wherein a sealing member (87) surrounding the outer circumference of the flange portion (77b) is attached to the connecting pin (77), and the tip portion (87c) of the sealing member (87) abuts against the outer peripheral stepped portion (78h). This configuration, by providing a sealing member around the outer circumference of the flange portion of the connecting pin, can suppress the leakage of grease filled in the ball housing and prevent foreign matter from entering the ball joint. When inserting the connecting pin with the ball bearing fitted into the ball housing from the opening side, the insertion work can be performed with the sealing member attached to the connecting pin.

[0010] A fifth aspect of the present invention is that, in any one of the first to fourth aspects described above, the connecting pin (77) has a fixed shaft portion (77c) that extends axially from the flange portion (77b) to the side opposite to the support shaft portion (77a) and has a smaller diameter than the flange portion (77b). With this configuration, by providing a fixed shaft portion with a smaller diameter than the flange portion on the connecting pin, this fixed shaft portion can be inserted into and fixed to one of the pin fixing portions of the pulley drive member and the operating member. By making the fixed shaft portion small in diameter, the size of the pin fixing portion is suppressed, and by inserting the fixed shaft portion until it abuts against the flange portion, the axial height of the connecting pin can be defined.

[0011] A sixth aspect of the present invention is that, in any one of the first to fifth aspects described above, the connecting pin (77) is fixed to the pulley drive member (71), and the ball housing (78) is provided on the operating member (75). With this configuration, by fixing the connecting pin to the pulley drive member, the ball bearing can be pre-assembled together with the connecting pin on the pulley drive member side, and the lead screw mechanism can be assembled to the controlled pulley. By providing the ball housing on the operating member, the rotation center of the ball joint (the input point of the reaction force when the pulley operates) approaches the central axis of the lead screw mechanism, and the bending moment acting on the lead screw mechanism can be suppressed.

[0012] A seventh aspect of the present invention is that, in any one of the first to fifth aspects described above, the connecting pin (77) is fixed to the operating member (75), and the ball housing (78) is provided on the pulley driving member (71). With this configuration, by fixing the connecting pin to the operating member, it is possible to reduce the size of the operating member and, consequently, the lead screw mechanism compared to when a ball housing is provided on the operating member. By providing the ball housing on the pulley drive member, the distance from the base of the pulley drive member to the rotation center of the ball joint (the input point of the reaction force when the pulley operates) is shortened, and the bending moment acting on the pulley drive member can be reduced. [Effects of the Invention]

[0013] According to the present invention, the ease of assembly of an electric continuously variable transmission can be improved. [Brief explanation of the drawing]

[0014] [Figure 1] This is a left side view of a motorcycle according to an embodiment of the present invention. [Figure 2] This is a left side view showing the area around the power unit of the above-mentioned motorcycle. [Figure 3] This is a plan view including an expanded cross-section of the area around the drive pulley of the transmission of the power unit described above. [Figure 4] It is a cross-sectional view showing an enlarged developed cross-section of FIG. 3. [Figure 5] It is a cross-sectional view showing an enlarged periphery of the feed screw mechanism of FIG. 4. [Figure 6] It is an exploded perspective view of the electric continuously variable transmission device of the embodiment. [Figure 7] It is a cross-sectional view showing an enlarged periphery of the ball joint of FIG. 5. [Figure 8] It is a perspective view of a sub-assembly including a drive pulley and a pulley drive arm. [Figure 9] It is a cross-sectional view corresponding to FIG. 5 showing the periphery of the ball joint of a modified example of the embodiment.

Mode for Carrying Out the Invention

[0015] Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following description, the directions such as front, rear, left, and right are the same as those in the vehicle described below unless otherwise specified. Also, in the figures used in the following description, at appropriate positions, an arrow FR indicating the front of the vehicle, an arrow LH indicating the left side of the vehicle, an arrow UP indicating the upper side of the vehicle, and a line CL indicating the center of the vehicle body left and right are shown. In the present embodiment, the term "intermediate" is intended to include not only the center between both ends of the object but also the inner range between both ends of the object.

[0016] <Vehicle as a Whole> FIG. 1 is a left side view of a motorcycle 1 in an embodiment of the present invention. The motorcycle 1 is an example of a saddle-riding type vehicle. The motorcycle 1 is a scooter type vehicle having a floor-like step (footrest) and a straddling space K1 for boarding and alighting in front of the seat 28, but may also be a vehicle having a bar type step or a vehicle having a knee grip portion. The motorcycle 1 is a unit swing type vehicle in which an engine (prime mover) 11 and a transmission 15 are integrated and can swing up and down together with a rear wheel (drive wheel) 4, but may also be a vehicle in which at least one of the engine 11 and the transmission 15 is fixedly supported by a vehicle body frame 20.

[0017] The motorcycle 1 comprises a front wheel 3 steered by a handle 2 and a rear wheel 4 driven by a power unit 10 including a power source. The steering system components, including the handle 2 and the front wheel 3, are steerably supported by a head pipe 21 located at the front end of the vehicle frame 20. The front part of the power unit 10 is supported in the middle of the vehicle frame 20 via a suspension link or the like so that it can swing up and down. The rear end of the power unit 10 is supported at the rear of the vehicle frame 20 via a rear cushion 9, which is a shock absorber.

[0018] The vehicle frame 20 includes a head pipe 21 that extends vertically and is inclined so that the upper part is positioned further rearward when viewed from the side; an upper down frame 22 that extends downward to the rear from the upper and lower middle part of the head pipe 21; a lower down frame 23 that extends downward from the lower part of the head pipe 21 and then bends to the rear; a seat rail 24 that extends upward to the rear from the longitudinal middle part of the upper down frame 22; and a center frame 25 that extends upward to the rear from the rear end of the lower down frame 23 and supports the longitudinal middle part of the seat rail 24 from below.

[0019] The body frame 20 is covered by a body cover 30. A seat 28 for the occupant is provided at the upper rear of the body cover 30. The vehicle body cover 30 comprises a pair of left and right step floors 31 on which the driver seated on the seat 28 places their feet, a center tunnel 32 extending in the longitudinal direction of the vehicle between the left and right step floors 31, a front body cover 33 connected to the front of the center tunnel 32 and the left and right step floors 31, and a rear body cover 34 connected to the rear of the center tunnel 32 and the left and right step floors 31. Above the center tunnel 32, a straddle space K1 is formed between the seat 28 and the steering wheel 2 to make it easier for the occupant to straddle the vehicle body.

[0020] A main stand 36, which supports the vehicle in an upright position, is supported on the underside of the power unit 10. Figure 1 shows the main stand 36 in its retracted state, flipped up towards the rear of the vehicle. A side stand 37, which supports the vehicle in an upright position tilted to the left, is supported on the lower left of the lower down frame 23. Figure 1 shows the side stand 37 in an upright position, supporting the vehicle in an upright position.

[0021] <Power Unit 10> Figure 2 is a left side view showing the area around the power unit 10 of the motorcycle 1. Figure 3 is a plan view including an unfolded section of the area around the drive pulley 46 of the V-belt type continuously variable transmission 16 of the power unit 10. Figure 4 is a cross-sectional view showing an enlarged unfolded section of Figure 3. As shown in Figures 2 to 4, the power unit 10 comprises a water-cooled single-cylinder engine (internal combustion engine) 11 and a transmission device 15 connected to the engine 11 and the rear wheel 4, which transmits the output of the engine 11 to the rear wheel 4. The transmission case 15a of the transmission device 15 is integrally coupled (for example, integrally formed) to the body (crankcase 13) of the engine 11.

[0022] Referring also to Figure 1, the engine 11 comprises a crankcase 13 supporting the crankshaft 12 and a cylinder 14 coupled to the front of the crankcase 13. An intake device 18A is connected to the upper part of the cylinder head of the cylinder 14, and an exhaust device 19A is connected to the lower part of the cylinder head. An air cleaner 18, connected to the intake device 18A, is supported on the upper part of the transmission case 15a. An exhaust muffler 19, connected to the exhaust device 19A, is supported on a rear arm (not shown) located to the right of the rear wheel 4.

[0023] The crankcase 13 is divided into left and right case halves in the left-right direction (only the left case half 13a is shown in Figures 3 and 4). The left and right case halves are joined together to form a crank chamber inside. The crank chamber houses the crank web and crank pin (neither shown) of the crankshaft 12. The piston is connected to the crank pin via a connecting rod (neither shown).

[0024] The left journal portion 12a of the crankshaft 12 is rotatably supported in the left case half 13a via the left main bearing 48b. Although not shown in the figure, the right journal portion of the crankshaft 12 is rotatably supported in the right case half via the right main bearing. Line C1 in the figure indicates the rotational axis of the crankshaft 12 (the central axis of the journal portion).

[0025] <Electric continuously variable transmission> Figure 6 is an exploded perspective view of an electrically operated continuously variable transmission according to an embodiment. Referring to Figures 2 to 4 and Figure 6, the transmission 15 comprises a V-belt type continuously variable transmission 16 housed in a transmission case 15a that continuously changes the speed of the rotational power transmitted from the crankshaft 12, and a reduction gear mechanism 17 housed in the rear of the transmission case 15a that reduces the output of the V-belt type continuously variable transmission 16 and transmits it to the axle 4a of the rear wheel 4. The line C4 in the figure indicates the central axis of the rear wheel axle 4a.

[0026] The transmission case 15a comprises a case body 42 that extends continuously from the left side (left case half 13a) of the crankcase 13 to the rear of the vehicle, a case cover 43 fastened to the outside of the case body 42 in the vehicle width direction and partitioning the transmission chamber 43a between it and the case body 42, and a gear cover (not shown) fastened to the inside of the rear of the case body 42 in the vehicle width direction and partitioning the gear chamber housing the reduction gear mechanism 17 between it and the case body 42. A V-belt type continuously variable transmission 16 is housed in the transmission chamber 43a. The case body 42 and the case cover 43 constitute an integrated transmission case 41 that forms the transmission chamber 43a.

[0027] The V-belt type continuously variable transmission 16 includes a drive pulley 46 located in the transmission chamber 43a and coaxially mounted to the left side (small diameter shaft portion 12b) of the crankshaft 12, which serves as the drive shaft, and a driven pulley 48 located in the transmission chamber 43a and mounted to a driven shaft 47 that protrudes from the transmission chamber 43a into the gear chamber. The axial directions of the crankshaft 12, drive pulley 46, and driven pulley 48 are parallel to the left-right direction (vehicle width direction) of the vehicle. Lines C2 and C3 in the figure indicate the central axes of the drive pulley 46 and driven pulley 48, respectively. The drive pulley 46 is coaxially positioned with the crankshaft 12.

[0028] An endless V-belt (transmission belt) 49 is wound around the drive pulley 46 and the driven pulley 48. The belt winding diameter of the drive pulley 46 changes due to the action of the centrifugal weight 66 and the drive of the actuator unit 50. The belt winding diameter of the driven pulley 48 changes in accordance with the change in the belt winding diameter of the drive pulley 46. The actuator unit 50 is equipped with an electric motor (hereinafter simply referred to as "motor") 56 as a drive source. The V-belt type continuously variable transmission 16 is combined with the actuator unit 50 and a control device (not shown) to constitute an electric continuously variable transmission. The actuator unit 50 controls the operation of the drive pulley 46 as the controlled pulley.

[0029] The drive pulley 46 comprises a fixed sheave 51 fixed to the crankshaft 12, and a movable sheave 52 positioned on the inside of the fixed sheave 51 in the vehicle width direction, with its umbrella-shaped face facing the fixed sheave 51, and supported by the crankshaft 12 so as to be movable in the axial direction. The movable sheave 52 is positioned between the left case half 13a of the crankcase 13 and the fixed sheave 51. A V-groove is formed between the fixed sheave 51 and the movable sheave 52, around which the V-belt 49 is wound. The movable sheave 52 has a movable sheave boss 52a through which the crankshaft 12 is inserted. The movable sheave boss 52a protrudes toward the left case half 13a from the umbrella-shaped sheave body that forms the face surface.

[0030] The V-belt type continuously variable transmission 16 includes a first shift mechanism 53 actuated by a centrifugal weight 66 and a second shift mechanism 54 actuated by an actuator unit 50. In response to the operation of the first shift mechanism 53 and the second shift mechanism 54, the movable sheave 52 of the drive pulley 46 is moved axially, changing the winding radius of the V-belt 49. The first shift mechanism 53 and the second shift mechanism 54 will be described in detail later.

[0031] The driven pulley 48 comprises a fixed sheave 57 supported on the driven shaft 47 so as not to move axially, and a movable sheave 58 supported so as to move axially. A V-belt 49 is wound around the V-groove between the fixed sheave 57 and the movable sheave 58. The movable sheave 58 moves axially toward and away from the fixed sheave 57. The movable sheave 58 is biased axially toward the fixed sheave 57.

[0032] A centrifugal clutch 59 is coaxially supported on the outer side of the driven shaft 47 in the vehicle width direction. The centrifugal clutch 59 disconnects and reconnects the power transmission between the driven pulley 48 and the driven shaft 47. The centrifugal clutch 59 disconnects and reconnects the rotational power transmission transmitted to the driven pulley 48. The rotation of the drive pulley 46 is transmitted to the driven pulley 48. When the drive pulley 46 increases the winding radius of the V-belt 49, the driven pulley 48 acts to move the movable sheave 58 away from the fixed sheave 57 against the biasing force, thereby decreasing the winding radius of the V-belt 49. This causes a change in speed between the two pulleys 46 and 48 of the V-belt type continuously variable transmission 16.

[0033] The centrifugal clutch 59 does not engage (transmit power) when the rotational speed of the driven pulley 48 is low, but engages to transmit the rotation of the driven pulley 48 to the driven shaft 47 when the driven pulley 48 rotates above a specified rotational speed. When the rotational speed of the driven pulley 48 and, consequently, the engine 11 exceeds a specified rotational speed, the centrifugal clutch 59 establishes a power transmission state.

[0034] The reduction gear mechanism 17 includes a drive gear fixed to or formed on the driven shaft 47 within the gear chamber, a final gear fixed to the axle 4a of the rear wheel 4, and an intermediate gear shaft positioned between the drive gear and the final gear (none of which are shown). The rotation of the driven shaft 47 is reduced in multiple stages by the reduction gear mechanism 17 and transmitted to the axle 4a of the rear wheel 4.

[0035] The first shift mechanism 53 includes a cam member 65 positioned between the fixed sheave 51 of the drive pulley 46 and the left case half 13a of the crankcase 13. The cam member 65 is disc-shaped and coaxial with the crankshaft 12. The small diameter shaft portion 12b, which is the left side of the crankshaft 12, has the cam member 65, sleeve 67, and fixed sheave 51 mounted on it in order from the left case half 13a. A nut 68 is screwed onto the left end of the small diameter shaft portion 12b, fastening each component mounted on the small diameter shaft portion 12b via a washer 68a. In this way, each component is fixed to the crankshaft 12. A movable sheave 52 is supported on the outer circumference of the sleeve 67 so as to be axially movable.

[0036] A centrifugal weight 66 is sandwiched between the cam surface 65a of the cam member 65 and the back surface of the movable sheave 52. The cam surface 65a is inclined to approach the movable sheave 52 as it moves radially outward from the rotation axis C1 of the crankshaft 12. The back surface of the movable sheave 52 is inclined to approach the cam member 65 as it moves radially outward from the rotation axis C1 of the crankshaft 12.

[0037] As the crankshaft 12 rotates, centrifugal force acts on the centrifugal weight 66, causing it to move radially outward. This creates an action that attempts to move the movable sheave 52 axially to the fixed sheave 51, following the inclination of the cam surface 65a and its back surface. By driving the actuator unit 50 in response to this action, it is possible to achieve gear shift control by the actuator unit 50 with minimal energy.

[0038] The second shift mechanism 54 comprises an actuator unit 50 and a pulley drive arm 71 mounted on the rear side (inward in the vehicle width direction) of the movable sheave 52 of the drive pulley 46. On the rear side of the movable sheave boss 52a, a cylindrical intermediate wall portion 52b is formed, rising axially from the radial middle portion of the rear side toward the left case half 13a side (inward in the vehicle width direction). A ball bearing 72 is mounted on the intermediate wall portion 52b. The inner ring of the ball bearing 72 is fitted onto the outer circumference of the intermediate wall portion 52b, and the inner circumference of the pulley drive arm 71 is fitted onto the outer ring. The movable sheave 52 and the pulley drive arm 71 are connected so that they can rotate relative to each other but cannot move relative to each other in the axial direction.

[0039] The actuator unit 50 includes a motor 56 that generates rotational power by having a drive shaft 56a parallel to the axial direction of both pulleys 46 and 48, a lead screw mechanism 73 that converts the rotational power of the motor 56 into axial power of the controlled pulley, and a gear mechanism 91 as a transmission mechanism positioned between the motor 56 and the lead screw mechanism 73. In the figure, line C5 indicates the central axis of the motor 56, and line C6 indicates the central axis of the lead screw mechanism 73.

[0040] The motor 56 of the actuator unit 50 is electrically driven and controlled by a control device (not shown). The actuator unit 50 designates the drive pulley 46 of the two pulleys 46 and 48 as the controlled pulley, and applies an axial force to the movable sheave 52 of the drive pulley 46, thereby moving the movable sheave 52 axially in cooperation with the centrifugal weight 66. By changing the groove width of the drive pulley 46 due to the axial movement of the movable sheave 52, the winding radius of the V-belt 49 changes, and the V-belt type continuously variable transmission 16 changes speed.

[0041] The actuator unit 50 includes a unit casing 55 that is attached to the case cover 43 from the outside in the vehicle width direction. A gear mechanism 91 is housed in a mechanism chamber partitioned between the unit casing 55 and the case cover 43. The gear mechanism 91 includes a drive gear 56b fixed or formed on the drive shaft 56a of the motor 56 within the mechanism chamber, a final gear 74a fixed to the shaft 74 of the lead screw mechanism 73, and a pair of intermediate gear shafts 92 and 93 positioned between the drive gear 56b and the final gear 74a. Hereinafter, of the pair of intermediate gear shafts 92 and 93, the one on the motor 56 side will be referred to as the first intermediate gear shaft 92, and the one on the shaft 74 side will be referred to as the second intermediate gear shaft 93. A pair of intermediate gears 92a and 92b are fixed or formed on the first intermediate gear shaft 92. A pair of intermediate gears 93a and 93b are fixed or formed on the second intermediate gear shaft 93.

[0042] One intermediate gear 92a on the first intermediate gear shaft 92 has a larger diameter than the drive gear 56b. When the drive gear 56b meshes with this intermediate gear 92a, the rotation of the drive gear 56b is reduced and transmitted to the first intermediate gear shaft 92. The other intermediate gear 92b has a smaller diameter than one intermediate gear 93a on the second intermediate gear shaft 93. When one intermediate gear 93a on the second intermediate gear shaft 93 meshes with this intermediate gear 92b, the rotation of the first intermediate gear shaft 92 is reduced and transmitted to the second intermediate gear shaft 93. The pair of intermediate gears 93a and 93b on the second intermediate gear shaft 93 are, for example, of the same diameter. The other intermediate gear 93b on the second intermediate gear shaft 93 has a smaller diameter than the final gear 74a on the shaft 74. When the final gear 74a meshes with this intermediate gear 93b, the rotation of the second intermediate gear shaft 93 is reduced and transmitted to the shaft 74. In this way, the rotation of the drive shaft 56a of the motor 56 is reduced in multiple stages and transmitted to the shaft 74 of the lead screw mechanism 73.

[0043] The first intermediate gear shaft 92 has an end that protrudes inward in the vehicle width direction from one of the intermediate gears 92a, which is located inward in the vehicle width direction, and this inward end is supported by the outer wall portion 43b of the case cover 43 via a bearing 92c. The first intermediate gear shaft 92 has the other intermediate gear 92b at its outer end in the vehicle width direction. The intermediate portion of the first intermediate gear shaft 92, located between the pair of intermediate gears 92a and 92b in the vehicle width direction, is supported by the casing body 55a of the unit casing 55 via a bearing 92d.

[0044] The second intermediate gear shaft 93 has an end that protrudes inward in the vehicle width direction from the first intermediate gear 93a, which is located inward in the vehicle width direction, and this inward end is supported by the casing body 55a of the unit casing 55 via a bearing 93c. The second intermediate gear shaft 93 has an end that protrudes outward in the vehicle width direction from the other intermediate gear 93b, which is located outward in the vehicle width direction, and this outward end is supported by the casing cover 55b of the unit casing 55 via a bearing 93d. Around the opening 43d that supports the feed screw mechanism 73 in the outer wall portion 43b of the case cover 43, a recess 43e is formed that opens outward in the vehicle width direction. The opening of the recess 43e is closed by the unit casing 55, forming a mechanism chamber that houses the gear mechanism 91.

[0045] Figure 5 is a cross-sectional view showing an enlarged view of the area around the feed screw mechanism 73 in Figure 4. Referring to Figures 4 and 5, the unit casing 55 and case cover 43 support the feed screw mechanism 73, which is the output mechanism of the actuator unit 50. The feed screw mechanism 73 includes a shaft 74 that is arranged parallel to the axial direction of both pulleys 46 and 48 and rotates around its axis by the output of the actuator unit 50, and a nut member (actuator) 75 that is separate from the unit casing 55 and case cover 43, is arranged coaxially with the shaft 74 and through which the shaft 74 is inserted, and strokes in the axial direction by the rotational motion of the shaft 74.

[0046] The shaft 74 extends with its axis centered on the central axis C6. The inner end 74b of the shaft 74 in the vehicle width direction is rotatably supported in the bearing portion of the case body 42 via a bearing 94 and a thrust bearing 95. The outer end 74c of the shaft 74 in the vehicle width direction is rotatably supported in the bearing portion of the unit casing 55 via a bearing 96 and a thrust bearing 97. The unit casing 55 includes a casing cover 55b that is removable from the casing body 55a. The bearing portion of the unit casing 55 is provided in the casing cover 55b.

[0047] The outer ring of the bearing 94 is press-fitted into the bearing portion of the case body 42. The outer circumference of a cup-shaped thrust bearing 95, which opens outward in the vehicle width direction, is press-fitted into the inner ring of the bearing 94. The inner end 74b of the shaft 74 in the vehicle width direction is inserted into the bottomed recess 95a of the thrust bearing 95 so as to be removable until it bottoms out. A flange portion 95b is formed on the outer circumference of the thrust bearing 95, which abuts the inner ring of the bearing 94 from the axial outside.

[0048] The outer ring of the bearing 96 is press-fitted into the bearing portion of the unit casing 55. The outer circumference of a cup-shaped thrust bearing 97, which opens inward in the vehicle width direction, is press-fitted into the inner ring of the bearing 96. The bottomed recess 97a of the thrust bearing 97 is removably fitted into the outward-projecting end 74c of the final gear 74a on the shaft 74 until it bottoms out. A flange portion 97b is formed on the outer circumference of the thrust bearing 97, which abuts the inner ring of the bearing 96 from the axially inward side.

[0049] The nut member 75 comprises a nut body (member body) 81 which is cylindrical through which the shaft 74 is inserted and has a female thread 81a formed on the inner circumference within a specified range from the outer end in the vehicle width direction; a ball screw nut 82 which holds a plurality of steel balls arranged in a spiral and is inserted into the nut body 81 from the outer end in the vehicle width direction of the nut body 81; and a fixing member 83 which is screwed into the female thread 81a inside the nut body 81 outside the ball screw nut 82 in the vehicle width direction and tightens and fixes the ball screw nut 82 which bottoms out to a stepped portion 81b inside the nut body 81. The nut member 75 is treated as a small assembly in which the nut body 81, ball screw nut 82 and fixing member 83 are assembled together as a single unit.

[0050] The nut member 75 is separate from the unit casing 55, and its outer circumference in the vehicle width direction is slidably supported in the axial direction on the inner circumference of an opening 43d formed in the outer wall portion 43b of the case cover 43. An annular sealing member 84 is held on the outer side of the opening 43d in the vehicle width direction in the outer wall portion 43b, in contact with the outer circumference of the nut member 75. The outer portion of the nut member 75 in the vehicle width direction forms an outer surface parallel to the axial direction up to the outer end in the vehicle width direction, and is axially insertable and detachable from the opening 43d. The inner portion of the nut member 75 in the vehicle width direction is slidably supported on the outer circumference of the shaft 74 at the inner end of an inner flange 85 formed on its inner circumference. An annular sealing member 86 is held on the inner side of the inner flange 85 in the vehicle width direction, in contact with the outer circumference of the shaft 74.

[0051] <Ball Joint 76> Referring to Figures 4 and 5, the nut member 75, which is the output member of the feed screw mechanism 73, is connected to the pulley drive arm 71 via a ball joint 76. The ball joint 76 comprises a connecting pin 77 fixed to one of the pulley drive member and nut member 75, a ball housing 78 formed on the other of the pulley drive member and nut member 75, and a ball bearing (spherical body) 79 housed within the ball housing 78 and supported by the connecting pin 77. In the figure, line C7 indicates the central axis of the connecting pin 77, line C8 indicates the central axis of the ball housing 78, and point CP indicates the center of the ball bearing 79 (the rotation center of the ball joint 76).

[0052] The ball joint 76 in Figures 4 and 5 shows the state in which the connecting pin 77 and the ball housing 78 have their axes C7 and C8 aligned (a state in which the connecting pin 77 is not tilted relative to the ball housing 78; hereinafter referred to as the upright state of the connecting pin 77). In this embodiment, the connecting pin 77 is fixed to the nut member 75, and the ball housing 78 is provided on the pulley drive member.

[0053] The connecting pin 77 comprises a support shaft portion 77a that fits into the connecting hole 79a of the ball bearing 79, and a flange portion 77b provided on the base end side of the support shaft portion 77a, which is formed to be larger in diameter than the ball bearing 79 and smaller in diameter than the counterbore portion 78b. A clip 77e can be attached to a groove portion 77d that runs along the circumferential direction on the tip side of the support shaft portion 77a. The clip 77e prevents the ball bearing 79, which is supported through the support shaft portion 77a, from coming loose.

[0054] The ball housing 78 is provided at the end of the pulley drive arm 71 opposite the movable sheave 52 in the radial direction, and has a cup shape that opens radially outward (towards the nut member 75) of the movable sheave 52. A recess is formed on the outer circumference of the nut member 75 on the inner side in the vehicle width direction, recessing radially inward from the nut member 75, and the fixed shaft portion 77c of the connecting pin 77 is press-fitted into this recess and fixed. The ball bearing 79, supported by the support shaft portion 77a of the connecting pin 77, is removably fitted and held within the ball housing 78 of the pulley drive arm 71 together with the support shaft portion 77a.

[0055] Figure 7 is a cross-sectional view showing an enlarged view of the area around the ball joint 76 in Figure 5. Referring also to Figure 7, the ball housing 78 comprises a cylindrical support wall portion 78a that directly or via an intermediate member circumstantial to the ball bearing 79, and a counterbore portion 78b formed on the opening 78d side of the support wall portion 78a, having an inner diameter D3 that is larger than the inner diameter D1 of the support wall portion 78a and the outer diameter D2 of the flange portion 77b. The ball housing 78 has a bottomed cylindrical shape with an opening 78d radially on the nut member 75 side. The ball bearing 79 and connecting pin 77 are inserted into the ball housing 78 through the opening 78d of the ball housing 78. In this embodiment, the support wall portion 78a directly circumstantial to support the ball bearing 79. The inner diameter D1 of the support wall portion 78a is substantially the same as the outer diameter D4 of the ball bearing 79.

[0056] Between the inner circumference 78a1 of the support wall 78a and the inner circumference 78b1 of the counterbore 78b, an inner circumferential step portion 78c is formed that is displaced radially from the ball housing 78. The inner circumferential step portion 78c includes, for example, a planar portion perpendicular to the axial direction, but may also be formed in a curved shape, such as a continuous S-shaped arc in a cross-sectional view along the axial direction (see Figure 7).

[0057] The inner circumferential step portion 78c faces the flange end portion 77b1 of the flange portion 77b of the connecting pin 77 in the axial direction, which faces the ball housing 78 side. The flange end portion 77b1 is formed between the outer circumference portion 77a1 of the support shaft portion 77a and the outer circumference portion 77b3 of the flange portion 77b. The flange end portion 77b1 is, for example, planar in a direction perpendicular to the axial direction of the connecting pin 77. The flange end portion 77b1 may also be tapered, for example, inclined with respect to a plane perpendicular to the axial direction. The flange end portion 77b1 may include about half the circumference of the chamfered portion r1 (see Figure 7) with a cross-sectional arc shape formed on the outer edge.

[0058] In the upright position of the connecting pin 77, the inner circumferential step portion 78c and the flange end portion 77b1 overlap each other when viewed from the axial direction, and face each other with a gap s1 in the axial direction. The gap s1 between the inner circumferential step portion 78c and the flange end portion 77b1 allows the ball joint 76 to be adjusted to function (tolerance absorption) even if the distance between the crankshaft 12 and the shaft 74 varies due to tolerances or other reasons. The opening 78d of the ball housing 78 faces axially the portion of the nut member 75 where the fixed shaft portion 77c of the connecting pin 77 is press-fitted and fixed (hereinafter referred to as the pin fixing portion 75a). The fixed shaft portion 77c extends coaxially from the flange portion 77b to the opposite side of the support shaft portion 77a. The fixed shaft portion 77c has the same diameter as, for example, the support shaft portion 77a, and both of these shaft portions 77a and 77c have a smaller diameter than the flange portion 77b. The connecting pin 77, fixed to the pin fixing portion 75a, is inserted into and housed in the bottomed housing portion that forms the support wall portion 78a of the ball housing 78, with the ball bearing 79 fitted onto the support shaft portion 77a.

[0059] When the connecting pin 77 is tilted from its upright position, the outer circumference 77b1 of the flange portion 77b comes into contact with the inner circumference 78b1 of the counterbore portion 78b. In Figure 7, a dashed line shows a portion of the flange portion 77b in the state where the connecting pin 77 is tilted from its upright position and in contact with the inner circumference 78b1 of the counterbore portion 78b. The outer periphery 77b1 may include not only the cylindrical outer periphery surface but also about half the circumference of the chamfered portion r1 between the outer periphery surface and the flange end 77b1. The inner circumference portion 78b1 may include not only the cylindrical inner circumference surface but also about half the circumference of the chamfered portion r2 (see Figure 7) with a circular arc cross-section formed at the leading edge of the inner circumference surface.

[0060] In the upright position of the connecting pin 77, a radial gap s2 is formed between the outer circumference 77b1 of the flange portion 77b and the inner circumference 78b1 of the counterbore portion 78b. The connecting pin 77 can be tilted relative to the ball housing 78 by a specified angle in any direction from the upright position. When the connecting pin 77 is tilted relative to the ball housing 78 from the upright position, the outer circumference 77b1 of the flange portion 77b and the inner circumference 78b1 of the counterbore portion 78b approach and come into contact with each other on the side where the connecting pin 77 is tilted. The radial contact between the flange portion 77b and the counterbore portion 78b limits the tilt of the connecting pin 77 to a specified angle.

[0061] The connecting pin 77, both in its upright position and when tilted from the upright position until the tilt is limited by the flange portion 77b, has at least a portion of the flange portion 77b (about half of its axial thickness) inserted into the counterbore portion 78b. As a result, the opening 78d of the ball housing 78 is largely closed by the flange portion 77b, preventing foreign matter from entering the ball housing 78 and preventing grease from leaking out of the ball housing 78.

[0062] The connecting pin 77 is held in the ball housing 78, which restricts the rotation of the nut member 75 around its axis C6. This prevents the nut member 75 from rotating along with the shaft 74, allowing the rotational power of the shaft 74 (and consequently the rotational power of the motor 56) to be accurately converted into thrust for the nut member 75, enabling the movable sheave 52 to move in the axial direction.

[0063] The connecting pin 77 is oscillating within a range where the flange portion 77b does not contact the inside of the ball housing 78. This allows for the absorption of component tolerances and assembly tolerances of the actuator unit 50. Furthermore, it absorbs vibrations of the pulley drive member caused by pulley vibrations, preventing the generation of vibration noise and improving the durability of the actuator 50. Since the maximum oscillation angle of the connecting pin 77 is determined by the contact between the flange portion 77b and the inside of the ball housing 78, the axial driving force of the feed screw mechanism 73 can be transmitted from the connecting pin 77 to the ball housing 78 with minimal loss while allowing the connecting pin 77 to oscillate.

[0064] The ball housing 78 includes a first outer peripheral portion 78f formed radially outward of the support wall portion 78a, a second outer peripheral portion 78g formed radially outward of the counterbore portion 78b and having a smaller outer diameter than the first outer peripheral portion 78f, and an outer peripheral stepped portion 78h formed between the first outer peripheral portion 78f and the second outer peripheral portion 78g and extending radially. The first outer circumference 78f and the second outer circumference 78g form a cylindrical outer surface. The outer periphery step portion 78h forms, for example, a planar portion perpendicular to the axial direction, but it may also form, for example, a tapered surface inclined with respect to a plane perpendicular to the axial direction.

[0065] A cup-shaped sealing member 87 is attached to the connecting pin 77, surrounding the outer circumference of the flange portion 77b. The sealing member 87 is made of a soft resin such as synthetic rubber. It comprises an annular base portion 87a sandwiched between the second flange end portion 77b2 facing the pin fixing portion 75a side of the flange portion 77b and the pin fixing portion 75a, a cup portion 87b extending from the outer circumference of the base portion 87a and curving outward in the cross-sectional view in Figure 7, extending toward the ball housing 78 side, and a tip portion 87c formed on the side of the cup portion 87b opposite to the base portion 87a. The sealing member 87 is made to contact (closely fit) the tip portion 87c in the axial direction with the outer peripheral stepped portion 78h while the cup portion 87b is bent to generate an elastic reaction force. This allows the connecting pin 77 to swing while the area around the opening 78d of the ball housing 78 is sealed by the sealing member 87. A stepped notch 77f is formed on the outer circumference of the second flange end portion 77b2 to accommodate the base portion 87a of the sealing member 87.

[0066] <Pulley drive arm 71> Figure 8 is a perspective view of the small assembly including the drive pulley 46 and the pulley drive arm 71. As shown in Figures 4 and 8, the pulley drive arm 71 comprises an annular body 71a mounted on the outer circumference of the intermediate wall portion 52b via a ball bearing 72 on the rear side (inward in the vehicle width direction) of the movable sheave 52 of the drive pulley 46, and an arm body 71b fastened and fixed to a specified circumferential portion of the annular body 71a by a pair of bolts B1. By making the arm body 71b, which extends radially from the movable sheave 52, a compact assembly of the movable sheave 52 and the annular body 71a is formed, and maintenance around the ball joint 76 is made easier.

[0067] As described above, the electric continuously variable transmission in the above embodiment includes a drive pulley 46 supported on the input shaft (crankshaft 12), a driven pulley 48 supported on the output shaft (driven shaft 47), a transmission belt 49 wrapped around the drive pulley 46 and the driven pulley 48, a transmission case 15a housing the drive pulley 46, the driven pulley 48 and the transmission belt 49, and a control device attached to the transmission case 15a that drives one of the drive pulley 46 and the driven pulley 48 (the drive pulley 46). In an electrically operated continuously variable transmission comprising a pulley and an actuator 50 that applies axial force to a movable sheave 52 of the drive pulley 46 to change the groove width, the actuator 50 comprises a motor 56 that generates rotational power and a lead screw mechanism 73 that converts the rotational power of the motor 56 into axial power of the drive pulley 46, and a pulley drive member (pulley drive arm 71) that can apply axial thrust to the movable sheave 52 is connected to the drive pulley 46 so as to be rotatable relative to it, and the pulley drive arm 71 and the lead screw mechanism 7 The nut member 75 of 3 is connected via a ball joint 76, the ball joint 76 comprises a connecting pin 77 fixed to the nut member 75, a ball housing 78 provided on the pulley drive arm 71, and a ball bearing 79 housed within the ball housing 78 and supported by the connecting pin 77, the ball housing 78 being a bottomed cylindrical shape with an opening 78d on the nut member 75 side, and the ball bearing 79 being able to be fitted through the opening 78d, the connecting pin 77 having a support shaft portion 77a fitted into the ball bearing 79 and The ball housing 78 comprises a support wall portion 78a having an inner diameter capable of supporting the ball bearing 79, and a counterbore portion 78b connected to the opening 78d side of the support wall portion 78a, forming an opening 78d that is larger in diameter than the support wall portion 78a and the flange portion 77b, and when the connecting pin 77 is tilted from an upright position relative to the ball housing 78, the outer circumference 77b1 of the flange portion 77b can come into contact with the inner circumference 78b1 of the counterbore portion 78b.

[0068] With this configuration, when the connecting pin 77 is tilted, the outer circumference 77b1 of the flange portion 77b of the connecting pin 77 comes into contact with the inner circumference 78b1 of the counterbore portion 78b on the opening 78d side of the ball housing 78. This creates a stopper structure between the counterbore portion 78b and the flange portion 77b that limits the tilting (oscillation) of the connecting pin 77. Therefore, while allowing the oscillation of the connecting pin 77 to be absorbed to accommodate part tolerances and assembly tolerances, the oscillation angle of the connecting pin 77 can be limited, and the thrust of the feed screw mechanism 73 can be accurately transmitted to the pulley drive arm 71. By making the opening 78d side of the ball housing 78 larger in diameter than the ball bearing 79 and the flange portion 77b, the connecting pin 77 with the ball bearing 79 fitted can be inserted into the ball housing 78 from the opening 78d side. Therefore, the ease of assembly around the ball joint 76 can be improved.

[0069] In the above-described electric continuously variable transmission, at least a portion of the flange portion 77b is located within the counterbore portion 78b. With this configuration, the flange portion 77b fits into the counterbore portion 78b, thereby largely blocking the opening 78d of the ball housing 78 and preventing foreign matter from entering the ball housing 78. The flange portion 77b also helps to prevent the grease filled into the ball housing 78 from leaking out.

[0070] In the above-described electric continuously variable transmission, a flange end portion 77b1 extending radially from the connecting pin 77 is formed between the outer circumference 77a1 of the support shaft portion 77a and the outer circumference 77b3 of the flange portion 77b, and an inner circumferential step portion 78c extending radially from the ball housing 78 is formed between the inner circumference 78a1 of the support wall portion 78a and the inner circumference 78b1 of the counterbore portion 78b, and when the connecting pin 77 is upright with respect to the ball housing 78, the inner circumferential step portion 78c and the flange end portion 77b1 overlap each other when viewed from the axial direction and face each other with a gap s1 in the axial direction. With this configuration, in the upright position of the connecting pin 77, the inner circumferential step portion 78c and the flange end portion 77b1 overlap each other when viewed from the axial direction, and face each other with a gap s1 in the axial direction. This allows the flange portion 77b to suppress the outflow of grease filled in the ball housing 78, while absorbing tolerances such as the distance between the crankshaft 12 and the shaft 74, thereby improving the operation of the ball joint 76.

[0071] In the above-described electric continuously variable transmission, the ball housing 78 includes a first outer peripheral portion 78f formed radially outward of the support wall portion 78a, a second outer peripheral portion 78g formed radially outward of the counterbore portion 78b and having a smaller outer diameter than the first outer peripheral portion 78f, and an outer peripheral stepped portion 78h formed between the first outer peripheral portion 78f and the second outer peripheral portion 78g and extending radially. A sealing member 87 surrounding the outer circumference of the flange portion 77b is attached to the connecting pin 77, and the tip portion 87c of the sealing member 87 abuts against the outer peripheral stepped portion 78h. With this configuration, by providing a sealing member 87 that surrounds the outer circumference of the flange portion 77b of the connecting pin 77, it is possible to suppress the outflow of grease filled in the ball housing 78 and to suppress the intrusion of foreign matter into the ball joint 76. When inserting the connecting pin 77 with the ball bearing 79 fitted into the ball housing 78 from the opening 78d side, the insertion work can be performed with the sealing member 87 attached to the connecting pin 77.

[0072] In the above-described electric continuously variable transmission, the connecting pin 77 extends axially from the flange portion 77b to the side opposite the support shaft portion 77a and has a fixed shaft portion 77c that has a smaller diameter than the flange portion 77b. With this configuration, by providing the connecting pin 77 with a fixed shaft portion 77c that has a smaller diameter than the flange portion 77b, this fixed shaft portion 77c can be inserted into and fixed to one of the pin fixing portions 75a of the pulley drive arm 71 and the nut member 75. By making the fixed shaft portion 77c small in diameter, the size of the pin fixing portion 75a is suppressed, and by inserting the fixed shaft portion 77c until it abuts against the flange portion 77b, the axial height of the connecting pin 77 can be defined.

[0073] In the above-described electric continuously variable transmission, the connecting pin 77 is fixed to the nut member 75, and the ball housing 78 is provided on the pulley drive arm 71. With this configuration, by fixing the connecting pin 77 to the nut member 75, the size of the nut member 75 and, consequently, the feed screw mechanism 73 can be kept down compared to the case where the ball housing 78 is provided on the nut member 75. By providing the ball housing 78 on the pulley drive arm 71, the distance from the base of the pulley drive arm 71 to the pivot point of the ball joint 76 (the input point of the reaction force when the pulley is operating) is shortened, and the bending moment acting on the pulley drive arm 71 can be suppressed.

[0074] <Modified version of ball joint 76> Figure 9 is a cross-sectional view corresponding to Figure 5, showing a modified ball joint 76' of the embodiment. In the embodiment, the ball joint 76 has a connecting pin 77 fixed to a nut member and a ball housing 78 provided on the pulley drive arm 71. In contrast, in the modified ball joint 76', the connecting pin 77 is fixed to the pulley drive arm 71 and the ball housing 78 is provided on a nut member 75. Other components identical to those in the embodiment are denoted by the same reference numerals. With this configuration, by fixing the connecting pin 77 to the pulley drive arm 71, the ball bearing 79 can be pre-assembled together with the connecting pin 77 on the pulley drive arm 71 side, and the lead screw mechanism 73 can be assembled to the controlled pulley. By providing the ball housing 78 on the nut member 75, the rotation center of the ball joint 76' (the input point of the reaction force when the pulley is operating) approaches the central axis of the lead screw mechanism 73, and the bending moment acting on the lead screw mechanism 73 can be suppressed.

[0075] It should be noted that the present invention is not limited to the above embodiments. For example, the electric continuously variable transmission of this embodiment may be applied to saddle-type vehicles other than motorcycles. The saddle-type vehicles include all vehicles on which the driver straddles the vehicle body, and include not only motorcycles (including motorized bicycles and scooter-type vehicles) but also three-wheeled vehicles (including vehicles with one front wheel and two rear wheels, as well as vehicles with two front wheels and one rear wheel) or four-wheeled vehicles (such as four-wheeled buggies). Furthermore, it includes not only scooter-type vehicles with a straddling space but also vehicles with a straddling section. It may also be applied to vehicles that include an electric motor as the power source.

[0076] In an electrically operated continuously variable transmission, the operation of the driven pulley may be controlled by an actuator. Alternatively, the controlled pulley may be operated solely by the actuator without the use of centrifugal weights. In the actuator, the motor may be configured so that its axial direction is perpendicular to the vehicle width direction. Alternatively, the connecting pin may be fixed to the pulley drive member, and the ball housing may be provided on the nut member. Alternatively, the shaft of the lead screw mechanism may be the operating member. Furthermore, the configuration in the above embodiment is just one example of the present invention, and various modifications are possible without departing from the spirit of the invention, such as replacing the components of the embodiment with well-known components. [Explanation of symbols]

[0077] 1. Motorcycle (saddle-type vehicle) 12 Crankshaft (Input Shaft) 15a Transmission case 46. ​​Drive pulley (controlled pulley) 47 Driven shaft (output shaft) 48 Driven pulley 49 V-belt (power transmission belt) 50 Actuator Unit (Actuator) 52 Movable Sheave 56 Motor 71 Pulley drive arm (pulley drive component) 73 Lead screw mechanism 75 Nut component (operating component) 76 Ball joint 77 Connecting pins 77a Support shaft part 77a1 outer periphery 77b Flange section D2 outer diameter 77b1 Flange end 77b3 Outer periphery 77c Fixed shaft part 78 Ball Housing D1 Inner diameter 78a Support wall section 78a1 Inner circumference 78b Counterbore section D3 Inner Diameter 78b1 Inner circumference 78c Inner circumference step section 78d aperture 78f First outer circumference D5 outer diameter 78g Second outer periphery D6 outer diameter 78h Outer perimeter step section 79 Ball bearing D4 outer diameter 87 Sealing member 87c Tip s1 gap

Claims

1. An electric continuously variable transmission comprising: a drive pulley (46) supported on an input shaft (12); a driven pulley (48) supported on an output shaft (47); a transmission belt (49) wrapped around the drive pulley (46) and the driven pulley (48); a transmission case (15a) housing the drive pulley (46), the driven pulley (48), and the transmission belt (49); and an actuator (50) attached to the transmission case (15a) and driven by a control device, which designates one of the drive pulley (46) and the driven pulley (48) as a controlled pulley (46), and applies axial force to a movable sheave (52) of the controlled pulley (46) to change the groove width, wherein The actuator (50) comprises a motor (56) that generates rotational power, and a feed screw mechanism (73) that converts the rotational power of the motor (56) into axial power of the controlled pulley (46). A pulley drive member (71) is connected to the controlled pulley (46) so as to be rotatable relative to it, enabling the application of axial thrust to the movable sheave (52). The pulley drive member (71) and the operating member (75) of the feed screw mechanism (73) are connected via a ball joint (76). The ball joint (76) comprises a connecting pin (77) fixed to one of the pulley drive member (71) and the operating member (75), a ball housing (78) provided on the other of the pulley drive member (71) and the operating member (75), and a ball bearing (79) housed within the ball housing (78) and supported by the connecting pin (77), The ball housing (78) is a bottomed cylindrical shape with an opening (78d) on one side of the pulley drive member (71) and the operating member (75), and the ball bearing (79) can be fitted into the opening (78d). The connecting pin (77) comprises a support shaft portion (77a) fitted into the ball bearing (79), and a flange portion (77b) provided on the base end side of the support shaft portion (77a) and having an outer diameter (D2) larger than the outer diameter (D4) of the ball bearing (79), The ball housing (78) comprises a support wall portion (78a) having an inner diameter (D1) capable of supporting the ball bearing (79), and a counterbore portion (78b) connected to the opening (78d) side of the support wall portion (78a) and forming the opening (78d) which is larger in diameter than the support wall portion (78a) and the flange portion (77b), When the connecting pin (77) is tilted from an upright position relative to the ball housing (78), the outer circumference (77b1) of the flange portion (77b) can come into contact with the inner circumference (78b1) of the counterbore portion (78b). The connecting pin (77) is fixed to the operating member (75), The ball housing (78) is an electrically operated continuously variable transmission provided on the pulley drive member (71).

2. The electric continuously variable transmission according to claim 1, wherein at least a portion of the flange portion (77b) is located within the counterbore portion (78b).

3. Between the outer periphery (77a1) of the support shaft portion (77a) and the outer periphery (77b3) of the flange portion (77b), a flange end portion (77b1) extending radially from the connecting pin (77) is formed. Between the inner circumference (78a1) of the support wall portion (78a) and the inner circumference (78b1) of the counterbore portion (78b), an inner circumferential step portion (78c) extending in the radial direction of the ball housing (78) is formed. The electric continuously variable transmission according to claim 1, wherein, in a state in which the connecting pin (77) is upright with respect to the ball housing (78), the inner circumferential step portion (78c) and the flange end portion (77b1) overlap each other when viewed from the axial direction and face each other with a gap (s1) in the axial direction.

4. In a state in which the connecting pin (77) is upright with respect to the ball housing (78), a radial gap (s2) is formed between the outer circumference (77b1) of the flange portion (77b) and the inner circumference (78b1) of the counterbore portion (78b), The electrically operated continuously variable transmission according to claim 3, wherein the radial gap (s2) is smaller than the axial gap (s1).

5. The ball housing (78) comprises a first outer peripheral portion (78f) formed radially outward of the support wall portion (78a), a second outer peripheral portion (78g) formed radially outward of the counterbore portion (78b) and having a smaller outer diameter than the first outer peripheral portion (78f), and an outer peripheral stepped portion (78h) formed between the first outer peripheral portion (78f) and the second outer peripheral portion (78g) and extending radially. A sealing member (87) is attached to the connecting pin (77) and surrounds the outer circumference of the flange portion (77b). The electric continuously variable transmission according to claim 1, wherein the tip (87c) of the sealing member (87) abuts against the outer peripheral stepped portion (78h).

6. The electric continuously variable transmission according to claim 1, wherein the connecting pin (77) extends in the axial direction from the flange portion (77b) to the side opposite to the support shaft portion (77a) and has a fixed shaft portion (77c) having a smaller diameter than the flange portion (77b).

7. The connecting pin (77) is fixed to the pulley drive member (71), The electric continuously variable transmission according to any one of claims 1 to 6, wherein the ball housing (78) is provided on the operating member (75).

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