JP2015014322A - Belt type stepless speed variator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve the durability of a gear engagement part in a structure which transmits a rotation force from an electric motor to a member having a feed screw at a belt type stepless speed variator.SOLUTION: A belt type stepless speed variator includes an actuator 26 which moves a movable sheave member 28 of a drive pulley 20, which is a one-side pulley, in an axial direction. The actuator 26 includes: a movable feed member 94; a gear case 96; and an electric motor. The movable feed member 94 includes: an inner cylindrical part 103 provided with a movable side feed screw; an outer cylindrical part 104 provided with an outer gear 110; and a lid part. The gear case 96 includes: a fixed cylindrical part 114 provided with a fixed side feed screw; and an outer cover 116. The electric motor drives a motor side gear 98 which engages with the outer gear 110. The outer cover 116 includes an opening part 126 into which the outer cylindrical part 104 is inserted, the opening part 126 which is located close to and faces an outer peripheral surface of the outer cylindrical part 104.

Description

  The present invention relates to a belt-type continuously variable transmission that includes a movable sheave member that clamps a belt with a fixed sheave, and an actuator that moves the movable sheave member in the axial direction.

  2. Description of the Related Art Conventionally, a structure in which a belt type continuously variable transmission is incorporated in a power transmission mechanism that transmits power from a power source of a vehicle to wheels is known. In the belt-type continuously variable transmission, a belt is stretched between a drive pulley on the power source side and a driven pulley on the wheel side in the power transmission direction. At least one of the driving pulley and the driven pulley includes a fixed sheave and a movable sheave that is movable in the axial direction with respect to the fixed sheave. As the belt type continuously variable transmission, an electric type is known in which a movable sheave is moved in an axial direction by an actuator including an electric motor.

  Patent Document 1 describes a structure in which a movable sheave is moved in an axial direction by a feed screw actuator including an electric motor in a belt-type continuously variable transmission. The actuator includes a movable feed screw member supported on the movable sheave via a cylinder and a bearing, and a fixed-side feed screw member that is fixed to the crankcase and is engaged with the movable feed screw member. Here, when the electric motor is driven, the motor side gear supported by the crankcase rotates, meshes with the motor side gear, and the gear integral with the movable feed screw member moves in the axial direction while rotating. Patent Document 2 describes a clutch CVT device on the power source side.

JP 2007-8405 A US Patent Application Publication No. 2013/0092468

  In the configuration described in Patent Document 1, the motor-side gear is rotated by driving the electric motor, and the power is transmitted to the other-side gear, so that the movable sheave approaches or moves away from the fixed sheave. The diameter changes. However, since the gear meshing with the motor-side gear is exposed to the outside in a state before being arranged in the transmission case that houses the pulley, it is desired to improve from the aspect of improving the durability of the gear.

  An object of the present invention is to provide a belt type continuously variable transmission capable of improving the durability of a gear in a structure for transmitting a rotational force from an electric motor to a member having a feed screw.

  A belt-type continuously variable transmission according to the present invention includes a one-side pulley and another pulley, a belt wound around the one-side pulley and the other pulley, and an actuator, and the one-side pulley is fixed to a rotating shaft. A movable sheave member that is disposed so as to be relatively movable in the axial direction with respect to the fixed sheave, and sandwiches the belt with the fixed sheave, wherein the actuator moves the movable sheave member in the axial direction. The continuously variable transmission, wherein the actuator is supported on the outer diameter side of the movable sheave member so as to be rotatable with respect to the center of the rotation shaft, and is provided with a movable side feed screw, and the inner cylindrical portion A movable feed member including an outer cylindrical portion that is disposed on the outer diameter side of the outer cylindrical portion and an outer gear is provided on the outer diameter side, and a lid portion that connects the inner cylindrical portion and the outer cylindrical portion; A fixed cylindrical portion provided with a fixed-side feed screw that is screw-engaged with a screw, and an outer cover provided integrally with the fixed cylindrical portion, having an opening into which the outer cylindrical portion is inserted, A gear case including an outer cover that accommodates the outer gear; and an electric motor that drives a motor-side gear that meshes with the outer gear, wherein the opening is the outer gear with respect to the axial direction of the rotating shaft in the outer cylindrical portion. Further, the outer peripheral surface of the pulley on one side is more closely opposed to the one side pulley.

  According to the belt-type continuously variable transmission according to the present invention, the outer gear of the movable feed member is accommodated by the outer cover of the gear case, and the opening provided in the gear case is formed on the outer cylindrical portion of the movable feed member. In the axial direction, it is closer to the outer peripheral surface on the one pulley side than the outer gear. For this reason, it is possible to improve the durability of the gear in the structure in which the rotational force is transmitted from the electric motor to the member having the feed screw.

1 is a schematic view showing a vehicle power transmission mechanism that includes a belt-type continuously variable transmission according to an embodiment of the present invention and transmits power from an engine to wheels. FIG. FIG. 2 is a cross-sectional view showing a maximum acceleration state of the belt type continuously variable transmission of FIG. 1. FIG. 3 is a perspective view showing the drive pulley of FIG. 2 and a first case element side portion of an actuator for changing the belt winding diameter of the drive pulley. FIG. 4 is a cross-sectional view of FIG. 3. In FIG. 4, it is a schematic exploded perspective view of a movable sheave body and a torque transmission member. FIG. 3 is a cross-sectional view showing a second case element side portion in the actuator of FIG. 2. It is a figure which shows the belt winding position between the driving pulley and a driven pulley in the maximum deceleration state and the maximum acceleration state. It is sectional drawing which shows the maximum deceleration state of the belt-type continuously variable transmission of FIG. FIG. 3 is a diagram corresponding to FIG. 2 in a first example of another example of the embodiment of the present invention. FIG. 10 is a view of the first case element side portion of the actuator taken from FIG. 9 and viewed from the right side of FIG. 9. It is the figure which looked at the 1st case element side part of the actuator from the left side of FIG. It is AA sectional drawing of FIG. It is BB sectional drawing of FIG. FIG. 6 is a schematic diagram showing the principle of detecting the axial position of a movable sheave member by a sheave position sensor in a first example of another example. It is a perspective view which shows a shaft fixing member with the structure of FIG. It is a schematic diagram which shows the shaft fixing member fixed to the fixed sheave by the structure of FIG. It is sectional drawing which shows the movable sleeve and cam mechanism which are arrange | positioned at the drive pulley side in the 1st example of another example. FIG. 5 is a diagram corresponding to FIG. 4 in a second example of another example of the embodiment of the present invention. FIG. 10 is a diagram showing motor torque necessary for changing the distance between sheaves at the drive pulley in the second example of another example when the electric motor rotates backward after forward rotation in comparison with the case where there is no biasing force generating member. . It is a figure which shows the integral structure which integrated the gear reduction mechanism with the continuously variable transmission of embodiment of this invention. FIG. 21 is a schematic diagram showing a positional relationship between an input shaft to which an engine output shaft is coupled and a rotation center axis O of a drive pulley in the configuration of FIG. 20. In 3rd example of another example of embodiment of this invention, it is a schematic diagram which shows the positional relationship of a drive pulley, a driven pulley, and an electric motor. It is a schematic diagram which shows the continuously variable transmission of the 4th example of another example of embodiment of this invention. It is a schematic diagram which shows a part of continuously variable transmission of the 5th example of another example of embodiment of this invention. It is a schematic diagram of the continuously variable transmission of 6th example of another example of the embodiment of the present invention. In 7th Example of another example of embodiment of this invention, it is a figure which shows the relationship between the torque reaction force of an electric motor, and the reduction ratio of a continuously variable transmission.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. Below, the case where the power transmission mechanism containing a belt-type continuously variable transmission is mounted in a vehicle is demonstrated. In this case, as the vehicle, for example, a vehicle having a traction member, an off-road vehicle that travels on rough terrain such as wasteland and rocky mountains, or any one or more of snow removal work, excavation work, civil engineering work, and farm work are performed. It is good also as a work vehicle which has a member for work, or an off-road type multipurpose vehicle (Utility Vehicle) which has a function of both an off-road vehicle and a work vehicle. Further, as a driving system of the vehicle, only front wheels, only rear wheels, or four-wheel drive may be used. In the following description, similar elements are denoted by the same reference numerals in all drawings.

  FIG. 1 is a schematic diagram showing a vehicle power transmission mechanism 10 that includes a belt-type continuously variable transmission 12 according to the present embodiment and transmits power from an engine 14 to wheels 16. The vehicle power transmission mechanism 10 is provided between an engine 14 that is a power source of the vehicle and a wheel 16 that is a front wheel or a rear wheel, and is used to transmit power from the engine 14 to the wheel 16. The power transmission mechanism 10 includes a belt type continuously variable transmission 12 provided between the output shaft of the engine 14 and the gear transmission mechanism 18. The gear transmission mechanism 18 includes a differential mechanism (not shown) connected to the left and right wheels 16. The gear transmission mechanism 18 is configured to allow a user to select a desired gear position by operating a gear shift operation member (not shown) provided in the vehicle. For example, the speed change operation member includes a clutch fork and a link mechanism provided in the gear speed change mechanism 18 and is connected to a slide member engaged with the speed change gear shaft. The slide member moves in the axial direction in accordance with the operation of the speed change operation member, and engages with a gear of a desired speed step, so that the input shaft on the continuously variable transmission 12 side and the output shaft on the wheel 16 side Vary the speed ratio between.

  The engine 14 may use any of a plurality of types including a gasoline engine and a diesel engine. Also, the vehicle is equipped with an engine 14, a generator that is driven by the engine 14 and generates electric power, and a traveling motor that is driven by supplying electric power generated by the generator directly or via a battery. It is good also as a hybrid type used as a power source.

  The belt-type continuously variable transmission 12 is wound around a drive pulley 20 that is a one-side pulley on the power source side, a driven pulley 22 that is another pulley on the wheel 16 side, and the drive pulley 20 and the driven pulley 22 in the power transmission direction. The belt 24, the actuator 26 provided on the drive pulley 20 side, and a transmission case 27 and a fixed stay 31 shown in FIG.

  The drive pulley 20 includes a fixed sheave 30 and a movable sheave member 28 disposed so as to be movable relative to the fixed sheave 30 in the axial direction. FIG. 2 is a cross-sectional view showing a maximum acceleration state of the belt type continuously variable transmission 12 of FIG. FIG. 3 is a perspective view showing the drive pulley 20 of FIG. 2 and the first case element 132 side portion of the actuator 26. As shown in FIGS. 2 and 3, the fixed sheave 30 has a belt engagement surface V1a provided on one side surface in the axial direction, and rotates relative to the drive shaft 32 that is a rotation shaft by a spline engagement portion. Fixed to impossible. The drive shaft 32 is coaxially coupled and fixed to the output shaft 34 of the engine.

  The movable sheave member 28 is formed by integrally coupling a movable sheave body 29 and a movable cylinder portion 54 (FIGS. 2 and 4) described later. The movable sheave body 29 includes a belt engaging surface V1b and a plurality of claw portions 36 that are opposite to the belt engaging surface V1b and project on the right side of FIG. . As shown in FIG. 5 to be described later, the number of the claw portions 36 is four, but may be other than four as long as it is two or more.

  4 is a cross-sectional view of FIG. As shown in FIG. 4, a needle bearing 38 is provided between the inner peripheral surface of the movable sheave body 29 and the outer peripheral surface of the drive shaft 32. The needle bearing 38 has an outer ring 40 disposed between the outer peripheral surface of the drive shaft 32 via a plurality of needles. The slide bearing 42 is held on the inner peripheral surface of the movable sheave body 29 and is provided so as to be able to slide in the axial direction with respect to the outer peripheral surface of the outer ring 40. The plain bearing 42 is called a “bush”. With this configuration, the movable sheave body 29 is disposed so as to be movable relative to the fixed sheave 30 in the axial direction. A belt engagement groove 44 having a V-shaped cross section is formed between the belt engagement surfaces V1a and V1b of the fixed sheave 30 and the movable sheave body 29. The belt 24 (FIG. 2) is clamped between the belt engagement surfaces V1a and V1b.

  FIG. 5 is a schematic exploded perspective view of the movable sheave body 29 and the torque transmission member 46 in FIG. The claw portions 36 of the drive pulley 20 are arranged around the drive shaft 32, and two sets of claw portions 36 are provided on the opposite side in the diameter direction of the drive shaft 32 (FIG. 4). In each pair of claws 36, the circumferential inner surfaces S <b> 1 facing each other in the circumferential direction are flat surfaces that are substantially parallel to each other along the axial direction of the drive shaft 32.

  As shown in FIG. 4, the torque transmission member 46 is provided so as not to rotate relative to the drive shaft 32. The torque transmission member 46 includes a cylindrical shaft fixing portion 48 fixed to the outer diameter side of the drive shaft 32 by a spline engaging portion or a key engaging portion, and a plurality of locations (two locations in the illustrated example). And a support shaft 50 protruding radially outward at a position, and a roller 52 rotatably supported by each support shaft 50. The roller 52 is made of resin. As will be described later, the roller 52 is guided so as to move in a direction parallel to the axial direction of the drive shaft 32 while rotating between the circumferential inner surfaces S1 of the pairs of claw portions 36 facing each other. In addition, when the drive shaft 32 rotates, the roller 52 presses the circumferential inner surface S <b> 1 of the claw portion 36 in the rotation direction of the drive shaft 32. The tip of each claw portion 36 is fixed to the movable cylinder portion 54 constituting the actuator 26, which will be described later.

  Returning to FIG. 1, the driven pulley 22 includes a fixed sheave 56, a movable sheave 58 that can move in the axial direction with respect to the fixed sheave 56, a first driven-side torque transmission member 60 and a second driven-side torque shown in FIG. 2. A transmission member 62 and a spring 64 are included. As shown in FIG. 2, the fixed sheave 56 is provided on one side of the belt engagement surface V2a and the belt engagement surface V2a is provided on the opposite side in the axial direction and is curved toward the inner peripheral side. Part 65 and a bearing support part 66 provided on the inner peripheral side of the bending part 65. The curved portion 65 has a guide hole 68 that penetrates the inside and outside in the radial direction. The guide hole 68 has two circumferential inner surfaces S2 that face each other in the circumferential direction and are substantially parallel to each other along the axial direction of the driven shaft 70 that is a rotation shaft and face in the circumferential direction.

  The bearing support portion 66 is rotatably supported by a bearing on the outer peripheral surface of the driven shaft 70, and relative movement of the driven shaft 70 in the axial direction is prevented. The driven shaft 70 is coaxially coupled and fixed to the input shaft 72 of the gear transmission mechanism 18 (FIG. 1). The driven shaft 70 may be integrally formed with the input shaft 72.

  The movable sheave 58 includes a belt engagement surface V2b provided on one side and a sliding bearing 74 provided on the inner peripheral surface. The sliding bearing 74 is held on the inner peripheral surface of the movable sheave 58 and is provided so as to be able to slide in the axial direction with respect to the outer peripheral surface of the driven shaft 70. With this configuration, the movable sheave 58 is disposed so as to be movable relative to the fixed sheave 56 in the axial direction. A belt engagement groove 76 having a V-shaped cross section is formed between the belt engagement surfaces V2a and V2b of the fixed sheave 56 and the movable sheave 58. The belt 24 is sandwiched between the belt engaging surfaces V2a and V2b.

  The first driven torque transmission member 60 includes a sheave fixing member 78 fixed to the movable sheave 58 and a first roller 80 supported by the sheave fixing member 78. The sheave fixing member 78 includes an inner cylindrical portion 84 that holds the sliding bearing 82 on the inner peripheral surface, and a sheave fixing portion 86 and a claw portion 88 that are provided on the outer diameter side of the inner cylindrical portion 84. The slide bearing 82 is provided on the outer peripheral surface of the driven shaft 70 so as to be slidable in the axial direction.

  The claw portion 88 extends from one axial end portion (the right end portion in FIG. 2) of the inner cylindrical portion 84 to the outer diameter side, and then extends to the other axial side (the left side in FIG. 2). It has a split tip. Circumferential inner side surfaces S <b> 3 that face the bifurcated circumferential direction of the distal end portion are flat surfaces that are substantially parallel to each other along the axial direction of the driven shaft 70. The first roller 80 is made of resin and is rotatably supported by a support shaft 83 protruding outward in the radial direction of the driven shaft 70 at the sheave fixing portion 86, and the axial direction of the driven shaft 70 inside the guide hole 68. Is arranged to allow movement.

  The second driven-side torque transmission member 62 is rotatably supported by a shaft fixing cylinder portion 90 fixed to the driven shaft 70 and a support shaft 91 protruding radially outward of the shaft fixing cylinder portion 90. Including. The shaft fixing cylinder 90 is provided closer to the movable sheave 58 in the driven shaft 70 than the inner cylinder 84 of the sheave fixing member 78 in the axial direction.

  The second roller 93 is made of resin and is arranged so that the driven shaft 70 can move in the axial direction inside the claw portion 88. As will be described later, when the driven pulley 22 rotates, the inner circumferential surface S <b> 2 of the guide hole 68 of the fixed sheave 56 presses the first driven torque transmitting member 60 in the rotation direction of the fixed sheave 56, The circumferential inner surface S <b> 3 presses the second driven side torque transmission member 62 in the rotational direction of the movable sheave 58.

  The spring 64 is provided between the inner surfaces of the shaft fixing cylinder portion 90 and the sheave fixing member 78 facing each other in the axial direction, and is in the right direction of FIG. Energize.

  The axial positional relationship between the fixed sheaves 30 and 56 and the movable sheave member 28 and the movable sheave 58 is reversed between the driving pulley 20 and the driven pulley 22. This is for smoothly changing the winding diameter of the belt 24 on the driven pulley 22 in accordance with the change of the winding diameter of the belt 24 on the driving pulley 20 by the actuator 26 described later.

  The movable sheave member 28 may be disposed on the engine 14 side with respect to the fixed sheave 30 with the drive pulley 20, and the movable sheave 58 may be disposed on the opposite side of the gear transmission mechanism 18 with respect to the fixed sheave 56 with the driven pulley 22. Good.

  Next, the actuator 26 will be described in detail with reference to FIGS. The actuator 26 reciprocates the movable sheave member 28 of the drive pulley 20 in the axial direction using a feed screw mechanism with the power of the electric motor 92 to change the sheave interval, which is the interval between the fixed sheave 30 and the movable sheave member 28. Used for. By changing the sheave interval, the reduction ratio between the drive shaft 32 and the driven shaft 70 is changed. The actuator 26 includes a movable feed member 94, a gear case 96, an electric motor 92, a gear mechanism 100 having a motor side gear 98, and an elastic member 102 which is a pulley side blocking means.

  As shown in FIG. 4, the movable feed member 94 includes an inner cylinder portion 103, an outer cylinder portion 104, and a lid portion 106. The movable feed member 94 is supported on the outer diameter side of the movable cylindrical portion 54 fixed to the movable sheave main body 29 by a ball bearing 108 so as to be rotatable with respect to the central axis O of the drive shaft 32 that is the rotational axis center.

  The movable cylinder portion 54 is supported on the outer peripheral surface of the drive shaft 32 so as to be slidable in the axial direction. A sliding bearing that slides with respect to the outer peripheral surface of the drive shaft 32 may be provided on the inner peripheral surface of the movable cylinder portion 54. One end portion in the axial direction of the movable cylinder portion 54 is fixed by bolting to the distal end surface of the claw portion 36 of the movable sheave body 29.

  The inner cylinder portion 103 has a movable-side feed screw 109 provided on the outer peripheral side. In the inner cylinder part 103, the inner peripheral surface on the opposite side to the drive pulley 20 in the axial direction is formed in a cylindrical shape. The ball bearing 108 includes an outer ring and an inner ring fixed to the movable cylinder part 54 and the inner cylinder part 103 by means including a locking ring in order to prevent relative displacement in the axial direction of the movable feed member 94 with respect to the movable cylinder part 54. Have.

  The outer cylindrical portion 104 is coaxially disposed on the outer diameter side around the inner cylindrical portion 103, and an outer gear 110 provided on the outer diameter side on the opposite side (right side in FIG. 2) from the drive pulley 20 in the axial direction. Have. In the outer cylindrical portion 104, the outer peripheral surface on the drive pulley 20 side (left side in FIG. 2) in the axial direction with respect to the outer gear 110 is formed in a cylindrical surface.

  The lid portion 106 is formed in a substantially circular plate shape, and connects the outer peripheral side of the inner cylindrical portion 103 and the inner peripheral side of the outer cylindrical portion 104 to the drive pulley 20 side (left side in FIG. 2) by bolt coupling.

  The gear case 96 is formed by a first case element 132 on the drive shaft 32 side shown in FIGS. 3 and 4 and a second case element 134 on the electric motor 92 side shown in FIG. 6. As shown in FIG. 4, the first case element 132 includes a fixed cylinder part 114, an outer cover 116, and a second fixed cylinder part 118. The fixed cylinder part 114 has a fixed-side feed screw 120 provided on the inner peripheral side, and is provided coaxially on the outer diameter side of the inner cylinder part 103. The fixed-side feed screw 120 is screw-engaged with the movable-side feed screw 109. The fixed-side feed screw 120 and the movable-side feed screw 109 form a feed screw mechanism. Moreover, a three-piece trapezoidal screw is used as the feed screw. However, it is not limited to this configuration, and one or two trapezoidal screws may be used.

  The outer cover 116 is provided integrally with the fixed cylinder portion 114 so as to cover the periphery of the fixed cylinder portion 114. The outer cover 116 is provided on the driving pulley 20 on the side opposite to the driving pulley 20 in the axial direction, the cylindrical wall portion 124 provided on the outer peripheral side of the bottom portion 122, and the driving portion 20 side of the wall portion 124. And a distal end side plate portion 128. The fixed cylindrical portion 114 is fixed to the bottom portion 122 so as to protrude from the inner surface of the bottom portion 122 toward the drive pulley 20.

  The front end side plate portion 128 is provided on the drive pulley 20 side (left side in FIG. 4) in the axial direction with respect to the outer gear 110 of the movable feed member 94 and has a cylindrical opening 126. A pulley-side portion that is a portion closer to the drive pulley 20 than the outer gear 110 in the axial direction of the drive shaft 32 is inserted into the opening 126 in the outer cylinder portion 104. The opening 126 is in close proximity to the outer peripheral surface of the pulley side portion. Note that “adjacently facing” means that a small radial gap is formed between the opening 126 and the outer peripheral surface of the pulley-side portion, or the opening 126 and the outer peripheral surface of the pulley-side portion are substantially the same. It means to face each other without a gap. As a result, the outer cover 116 houses the outer gear 110.

  The elastic member 102 is provided between the opening 126 and the outer cylindrical portion 104. The elastic member 102 is an O-ring formed of rubber. The elastic member 102 is locked to a locking groove formed on the inner peripheral surface of the opening 126 over the entire circumference in the front end side plate portion 128 of the outer cover 116, and the outer cylindrical portion. 104 is in sliding contact with the cylindrical outer peripheral surface. The elastic member 102 prevents foreign matter from entering the outer gear arrangement space P in which the outer gear 110 is arranged from the drive pulley 20 side. The elastic member 102 is locked in a locking groove formed on the outer peripheral surface on the drive pulley 20 side of the outer gear 110 in the axial direction of the drive shaft 32 in the outer cylindrical portion 104, and the inner periphery of the opening 126. It is good also as a structure slidably contacted with the surface.

  The second fixed cylinder portion 118 is formed in a cylindrical shape having an outer peripheral surface that is a cylindrical surface, and is coaxial with the fixed cylinder portion 114 on the inner diameter side of the fixed cylinder portion 114 and protrudes from the inner surface of the bottom portion 122 toward the drive pulley 20. It is fixed to the bottom part 122 so as to. The second fixed cylinder portion 118 has a bearing support portion 131 that supports the bearing 130 between the outer peripheral surface of the drive shaft 32 on the inner peripheral surface side, and is driven by the bearing 130 as the center of the rotation shaft with respect to the drive shaft 32. The shaft 32 is supported so as to be rotatable with respect to the central axis O.

  As will be described later, the second fixed cylindrical portion 118 is the entire movable range in the axial direction of the inner cylindrical portion 103 in all cases where the movable sheave member 28 moves relative to the fixed sheave 30. It is in sliding contact with the inner peripheral surface of the inner cylindrical portion 103 or opposed to the inner peripheral surface via a minute gap. A second elastic member (not shown) may be provided between the outer peripheral surface of the second fixed cylindrical portion 118 and the inner peripheral surface of the inner cylindrical portion 103. The second elastic member is an O-ring formed of rubber. For example, the second elastic member is locked in a locking groove formed on the outer peripheral surface of the second fixed cylindrical portion 118, and the cylindrical inner peripheral surface of the inner cylindrical portion 103. Slid in contact. Note that the second elastic member may be locked in a locking groove formed on the inner peripheral surface of the inner cylindrical portion 103 and slidably contacted with the outer peripheral surface of the cylindrical second fixed cylindrical portion 118.

  The first case element 132 accommodates and supports a part of the gear mechanism 100 described later, and the second case element 134 of FIG. 6 accommodates and supports the remaining part of the gear mechanism 100. Furthermore, the first case element 132 includes a one-side case element 158 and an other-side case element 160 that are separated along the axial direction of the drive shaft 32 and are coupled to each other by fastening means 156 (FIG. 4) such as bolts. Configured as follows. For example, the one-side case element 158 includes a part of the wall portion 124 and the tip side plate portion 128, and the other-side case element 160 includes the remaining portion of the wall portion 124, the bottom portion 122, the fixed cylinder portion 114, and the second fixed portion. It is comprised so that the cylinder part 118 may be included. A screw formed in the one-side case element 158 with fastening means 156 inserted into an insertion hole (not shown) formed in the other-side case element 160 in a state where the ends of the one-side case element 158 and the other-side case element 160 are butted together. The two case elements 158 and 160 are coupled and fixed to each other by screws. The screw hole may be formed in the other case element 160, and the insertion hole may be formed in the one side case element 158. The second case element 134 has a cylindrical portion 140 projecting to one side, and the cylindrical portion 140 is inserted into and fixed to the hole 142 provided in the first case element 132 of FIG. 2) is formed. The inside of the hole 142 is blocked from the outside by the second case element 134. The gear case 96 is provided in a portion that is distant from the belt 24 toward the movable feed member 94 in the axial direction of the drive shaft 32.

  As shown in FIG. 2, the electric motor 92 has a motor case 137 fixed to the second case element 134 on the opposite side to the drive pulley 20 in the axial direction. The drive of the electric motor 92 is controlled by a control device (not shown), and drives the motor side gear 98 (FIG. 4) via a gear mechanism 100 described later. The electric motor 92 can be rotationally driven in both directions. For example, one or both of detection signals of the engine speed and the throttle opening of the throttle valve are transmitted to the control device from one or more sensors (not shown). The control device calculates the target rotation direction and the target rotation amount of the electric motor 92 based on the detection signal of one or both of the engine rotation speed and the throttle opening, and is electrically driven so as to rotate by the target rotation amount in the target rotation direction. The drive of the motor 92 is controlled. Instead of the throttle opening detection signal, a detection signal indicating the pedal position of the accelerator pedal detected by the accelerator pedal sensor may be used.

  For example, a three-phase synchronous motor or a three-phase induction motor is used as the electric motor 92. In this case, the control device controls driving of the electric motor 92 via a motor driver (not shown) according to a shift pattern set in advance according to the detected values of the engine speed and the throttle opening. For example, the speed reduction ratio may be reduced as the engine speed increases. The motor driver has an inverter connected to a battery which is a DC power source. The inverter converts a direct current supplied from the battery into an alternating current. The inverter drives the electric motor 92 by generating a desired alternating current that is a driving current of the electric motor 92 in accordance with a control signal from the control device. Note that the control device may control the driving of the electric motor 92 so as to change the reduction ratio according to the detected position of the accelerator pedal in a state where the rotation speed of the engine is constant.

  The gear mechanism 100 includes a large-diameter gear 146 fixed to the first gear shaft 144 supported by the first case element 132 and a plurality of second gear shafts 145, 147, 149 supported by the second case element 134. And fixed gears 138, 139, 141. The plurality of second gear shafts 145, 147, 149 include a gear shaft 145 connected to the rotation shaft of the electric motor 92 and a gear shaft 149 to which a gear 141 that meshes with the large-diameter gear 146 is fixed. The gear shaft 149 is rotatably supported by both the first case element 132 and the second case element 134. The gear 141 is fixed to a portion of the gear shaft 149 that protrudes from the cylindrical portion 140 and is inserted into the first case element 132.

  The motor-side gear 98 is fixed to the first gear shaft 144 integrally with the large-diameter gear 146 and has a total length that covers the entire movable range of the outer gear 110 in the axial direction. The gear mechanism 100 transmits power while decelerating from the electric motor 92 to the motor side gear 98. When driven, the motor-side gear 98 rotates the movable feed member 94 as described later, and moves in the axial direction by the action of a feed screw mechanism.

  As shown in FIG. 6, the fixed stay 148 includes a cylindrical portion 150 and plate portions 152 and 154 provided at both ends of the cylindrical portion 150. The plate portion 152 on one side is fixed to the side surface of the second case element 134 on the belt 24 (FIG. 2) side by fastening means including a bolt, and the cylindrical portion 150 protrudes toward the belt 24 side.

  As shown in FIG. 2, the transmission case 27 is made of metal such as iron or aluminum alloy, and accommodates the drive pulley 20, the actuator 26, the driven pulley 22, and the belt 24 inside. A plate portion 154 on the other side of the fixed stay 148 is fixed to the inner surface of the transmission case 27 by fastening means including bolts. The fixed stay 148 is disposed so as to penetrate the inside of the belt 24 in a state where the belt 24 is stretched around the driving pulley 20 and the driven pulley 22. In this case, as shown in FIG. 7, the transfer position of the belt 24 changes between the maximum deceleration state at the position “a” and the maximum acceleration state at the position “b”. It is arranged so as to penetrate the oblique lattice range of FIG. 7 in the space which becomes the inner region of the belt 24 in the set state. The transmission case 27 can be fixed to a frame forming a vehicle body (not shown) or to the case of the gear transmission mechanism 18.

  The belt type continuously variable transmission 12 configured as described above changes the gear ratio between the drive shaft 32 and the driven shaft 70 as follows. First, based on the detection value detected by one or more sensors as described above, the control device rotates the electric motor 92 by a predetermined amount in a predetermined direction. In this case, for example, the gear mechanism 100 is rotated by rotation of the electric motor 92 in one direction, and the outer gear 110 that meshes with the motor-side gear 98 is driven to rotate in one direction. In this case, the inner cylinder portion 103 also rotates in the same direction as the outer gear 110, but because the screw is engaged with the fixed cylinder portion 114 fixed to the gear case 96, the inner cylinder portion 103 is rotated by the action of the feed screw mechanism. While moving to one side in the axial direction (left side in FIG. 2). In this case, the movable cylinder part 54 also moves to one side in the axial direction, and the movable sheave member 28 of the drive pulley 20 approaches the fixed sheave 30 as shown in FIG. The winding diameter of the belt 24 is increased.

  On the other hand, in relation to the tension applied to the belt 24, the movable sheave 58 is moved from the fixed sheave 56 by the belt 24 against the urging force of the spring 64 so that the winding diameter of the belt 24 becomes small in the driven pulley 22. keep away. As a result, the power of the drive shaft 32 is accelerated by the belt 24 and transmitted to the driven shaft 70. FIG. 2 shows the case of the maximum acceleration state.

  Further, in this case, since the torque transmission member 46 is guided to the inner circumferential surface S1 of the claw portion 36, the movable sheave member 28 can move in the axial direction of the drive shaft 32 with respect to the torque transmission member 46. Become. Further, when the drive shaft 32 rotates, the roller 52 of the torque transmission member 46 presses the circumferential inner surface S <b> 1 in the rotation direction of the drive shaft 32, so that torque is transmitted from the drive shaft 32 to the movable sheave member 28.

  The first driven side torque transmission member 60 is pressed in the rotational direction of the fixed sheave 56 by the circumferential inner surface S2 of the guide hole 68 of the fixed sheave 56, and the second driven side torque transmission member 62 is moved to the movable sheave 58. The movable sheave 58 is pressed in the rotational direction by the circumferential inner surface S3 of the fixed sheave fixing member 78. For this reason, torque is transmitted from the driven pulley 22 to the driven shaft 70.

  On the other hand, when the electric motor 92 is rotationally driven in the reverse direction, the outer gear 110 is rotationally driven in the reverse direction to the above via the gear mechanism 100. Also in this case, since the inner cylinder portion 103 rotates in the same direction as the outer gear 110, the inner cylinder portion 103 moves to the other side in the axial direction (right side in FIG. 2) by the action of the feed screw mechanism. In this case, the movable cylinder portion 54 moves to the other side in the axial direction while rotating, and the movable sheave member 28 of the drive pulley 20 moves away from the fixed sheave 30 as shown in FIG. In this case, the sheave interval is increased, and the winding diameter of the belt 24 on the drive pulley 20 is decreased.

  On the other hand, due to the tension applied to the belt 24, the movable sheave 58 approaches the fixed sheave 56 in the driven pulley 22 by the biasing force of the spring 64. For this reason, the winding diameter of the belt 24 is increased, and the power of the drive shaft 32 is decelerated and transmitted to the driven shaft 70.

  Also in this case, the torque of the drive shaft 32 is transmitted to the drive pulley 20 and the torque of the driven pulley 22 is transmitted to the driven shaft 70 by the torque transmitting members 46, 60, 62.

  Further, the outer gear 110 of the movable feed member 94 is accommodated by the outer cover 116 of the gear case 96, and the opening 126 provided in the gear case 96 is in the axial direction of the drive shaft 32 in the outer cylindrical portion 104 of the movable feed member 94. The outer gear 110 is closer to the outer peripheral surface on the drive pulley 20 side than the outer gear 110. For this reason, it is difficult for foreign matter to enter the meshing portion of the outer gear 110. Further, in a state before the drive pulley 20 and the driven pulley 22 are accommodated in the transmission case 27, foreign matter or another member does not collide with the outer gear 110. For this reason, it is possible to improve the durability of the gear in the structure in which the rotational force is transmitted from the electric motor 92 to the member having the feed screw. Furthermore, the elastic member 102 provided between the outer cylinder portion 104 and the outer cover 116 can suppress the intrusion of foreign matter from the drive pulley 20 side into the outer gear arrangement space P, thereby further improving the durability of the gear meshing portion. It can be improved. In addition, the electric motor 92 is fixed to a gear case 96 provided at a portion that is distant from the belt 24 toward the movable feed member 94, the fixed sheave 30 is fixed to the drive shaft 32, and the movable sheave member 28 is fixed to the fixed sheave 30. The sliding bearing 42 is disposed so as to be relatively movable in the axial direction. For this reason, the drive shaft 32, the drive pulley 20, and the actuator 26 can be handled as an integral part with a small structure in a state before being arranged in the transmission case 27 that houses the drive pulley 20 during the assembly work. Therefore, the assembling work can be facilitated without deteriorating the durability of the gear.

  Further, the second fixed cylindrical portion 118 is in sliding contact with the inner peripheral surface of the inner cylindrical portion 103 or has a minute gap with the inner peripheral surface over the entire movable range of the inner cylindrical portion 103 in the axial direction. Opposite through. For this reason, it can suppress that a foreign material penetrate | invades into the arrangement | positioning part of the engaging part of the feed screws 109 and 120 of the inner side cylinder part 103 and the fixed cylinder part 114 from the inner diameter side of the outer side gear arrangement | positioning space P. The engaging portions of the feed screws 109 and 120 are arranged in the outer gear arrangement space P. For this reason, coupled with the fact that the opening 126 of the outer cover 116 is closely opposed to the outer peripheral surface of the outer cylindrical portion 104, the outer gear arrangement space P is sealed from the outside, and the gear meshing portion and the feed screw of the outer gear 110 are sealed. The durability of both the engagement portions 109 and 120 can be improved. The elastic member 102 provided between the opening 126 of the outer cover 116 and the outer peripheral surface of the outer cylindrical portion 104, and the locking groove provided in the opening 126 or the outer cylindrical portion 104 for locking the elastic member 102. And may be omitted.

  The torque transmission member 46 includes a shaft fixing portion 48, a support shaft 50, and a roller 52. The movable sheave member 28 is disposed around the drive shaft 32, protrudes toward the actuator 26, and has a circumferential surface that faces each other. A plurality of claw portions 36 for guiding the roller 52 between the direction inner side surfaces S1 are included. Further, the roller 52 presses the circumferential inner surface S <b> 1 of the claw portion 36 in the rotation direction of the drive shaft 32 when the drive shaft 32 rotates. For this reason, unlike the case where torque is transmitted from the drive shaft to the movable sheave by the key, it is not necessary to increase the processing accuracy of the key. Further, it is not necessary to use a lubricant between the roller 52 and the engaging portion, and it is not necessary to provide a sealing structure for the lubricant, so that the structure can be simplified. Further, since the sliding resistance between the roller 52 and its engaging portion is small, the efficiency of the continuously variable transmission 12 can be improved.

  As a torque transmission member that transmits torque between the drive shaft 32 and the movable sheave member 28, a spline engagement between ball splines or spline engagement grooves can be used. Also in this case, since it is not necessary to use a lubricant, the structure can be simplified. Further, when the ball spline is used, the sliding resistance can be reduced, so that the efficiency of the continuously variable transmission 12 can be improved.

  In addition, the fixing stay 31 is used to fix the gear case 96 to the transmission case 27, which is another member, and the belt 24 penetrates through a space serving as an inner region of the belt 24 when the belt 24 is fully set. A fixed stay 31 arranged as described above is provided. Therefore, unlike the case where the fixed stay is disposed outside the belt 24, the continuously variable transmission 12 including the actuator 26 can be downsized. Further, since the belt 24 can be replaced while the fixed stay 31 is attached to the transmission case 27, maintenance can be improved.

  Note that the gear case 96 may be directly attached to the case of the gear transmission mechanism 18, which is another member, by the fixed stay 31 without providing the transmission case 27. In this case, since the gear transmission mechanism 18 and the actuator 26 can be formed as one unit, the size can be reduced. Further, the gear case 96 can be directly attached to the frame forming the vehicle body as another member by the fixed stay 31.

  2, the drive shaft 32 is provided with a bearing between the end opposite to the output shaft 34 and the transmission case 27, and the output shaft 34 is rotatably supported by the transmission case 27. May be. Further, another rotating shaft is integrally coupled to the opposite side of the input shaft 72 of the driven shaft 70, a bearing is provided between the other rotating shaft and the transmission case 27, and the other rotating shaft is connected to the transmission case 27. It may be supported rotatably.

  In this example, the movable sheave member 28 is formed by the movable sheave body 29 and the movable cylinder portion 54, but the movable sheave member may be formed by only the movable sheave body. Further, the coupling side of the input shaft 72 of the engine 14 and the gear transmission mechanism 18 with respect to the drive shaft 32 and the driven shaft 70 may be reversed from the case of FIG. In addition, the internal / external relationship in the radial direction between the inner cylindrical portion 103 and the fixed cylindrical portion 114 forming the feed screw mechanism may be reversed.

  FIG. 9 is a diagram corresponding to FIG. 2 in a first example of another example of the embodiment of the present invention. 10 is a view of the first case element 132 side portion of the actuator 26A taken from FIG. 9 and viewed from the right side of FIG. 9, and FIG. 11 is a view of the first case element 132 side portion of the actuator 26A shown in FIG. It is the figure seen from the left side. In FIG. 9, the winding diameter of the belt 24 between the driving pulley 20 and the driven pulley 22 is minimum, but this is the maximum deceleration state and the maximum increase in the driving pulley 20 and the driven pulley 22, respectively. The speed state is shown, and in the same actual state, the magnitude relationship of the winding diameter of the belt 24 between the driving pulley 20 and the driven pulley 22 is reversed or the same winding diameter.

  In the case of this example, in the configuration shown in FIGS. 1 to 8, the drive pulley 20 and the driven pulley 22 are provided with an actuator 26A for changing the sheave interval on the driven pulley 22 side. In this case, the driven pulley 22 corresponds to a one-side pulley, and the drive pulley 20 corresponds to the other-side pulley. The movable sheave member 300 is disposed on the left side in FIG. 9, which is the gear transmission mechanism 18 (see FIG. 1) side with respect to the fixed sheave 304. The movable sheave member 300 is formed by fixing the movable cylinder portion 54 to the movable sheave body 302. The structure of the movable sheave body 302 is the same as the structure in which the claw portion 176 is formed on the belt engagement surface side with the left and right sides reversed in the movable sheave body 29 shown in FIGS. As shown in FIG. 12, a sliding bearing 306 is held on the inner peripheral surface of the movable sheave body 302 and is supported so as to be relatively movable in the axial direction with respect to the driven shaft 70. The detailed structure of the fixed sheave 304 will be described later.

  Returning to FIG. 9, some of the gears 138, 139 forming the gear mechanism 100 and the second case element 134 that houses these some gears 138, 139 are driven shafts 70 relative to the motor side gear 98. Is provided on the side opposite to the driven pulley 22 (right side in FIG. 9).

  The belt-type continuously variable transmission 12 of this example includes a sheave position sensor 157 that detects the axial position of the movable sheave member 300. As shown in FIG. 11, the sheave position sensor 157 is attached to the first case element 132 that forms the gear case 96. The sheave position sensor 157 includes a rotary shaft 159 supported so as to protrude from the sensor case fixed to the first case element 132 to the inside of the first case element 132, and a swing fixed to the tip of the rotary shaft 159. Moving arm 161. As shown in FIG. 12, one end portion of the swing arm 161 faces the end surface in the axial direction of the outer cylindrical portion 104.

  13 is a cross-sectional view taken along the line BB in FIG. As shown in FIG. 13, the swing arm 161 is disposed so as to be rotatable about the rotation shaft 159, and the other end of the swing arm 161 is connected to the outer cylinder by one end of the swing arm 161 of FIG. It is pressed in a direction approaching the portion 104.

  FIG. 14 is a schematic diagram illustrating the principle of detecting the axial position of the movable sheave member 300 (FIG. 12) by the sheave position sensor 157. When one end of the swing arm 161 is pressed in the direction indicated by the arrow α by the axial end surface of the outer cylindrical portion 104, the swing arm 161 swings about the rotating shaft 159 against the biasing force of the spring 162. To do. According to the sheave position sensor 157, it is possible to detect the axial position of the movable sheave member 300 that moves in synchronization with the outer cylindrical portion 104 from the rotation position of the rotation shaft 159. A detection signal indicating the axial position of the movable sheave member 300 detected by the sheave position sensor 157 is transmitted to the control device.

  The sheave position sensor 157 has a function of detecting only the rotational position of the swing arm 161, and can also transmit a signal representing the detected value to the control device. In this case, the control device stores in advance a relationship between the axial position of the movable sheave member 300 and the rotational position of the swing arm 161 in the storage unit, and the movable sheave member 300 is detected from the detected value of the rotational position of the swing arm 161. It is possible to calculate and detect the position in the axial direction. In such a configuration using the sheave position sensor 157, compared to a configuration in which the axial position of the movable sheave member 300 is detected from the rotational position of the gear of the gear mechanism 100, the detection position is on the member on the movable sheave member 300 side. The detection error of the sensor can be reduced. The sheave position sensor 157 may be employed in the configuration shown in FIGS.

  Further, as shown in FIG. 16 to be described later, a through hole 164 is formed in the center portion of the fixed sheave 304. The fixed sheave 304 has protrusions 166 that protrude radially inward from two diametrically opposite locations on the inner peripheral surface of the through hole 164.

  A shaft fixing member 170 is fixed to the side surface (the right side surface in FIG. 9) opposite to the belt engaging surface of the fixed sheave 304 as described below.

  The shaft fixing member 170 has the shape shown in FIGS. 15 and 16, and includes a cylindrical portion 171 and a pair of arm portions 172 protruding from the opposite side of the cylindrical portion 171 in the radial direction to the outer diameter side. Each arm 172 is formed in a flat plate shape, and has a through hole 174 at the tip. The shaft fixing member 170 overlaps each protrusion 166 of the fixed sheave 304 with an arm 172, and a bolt inserted into the through hole 174 is screwed to a screw hole formed in each protrusion 166, thereby fixing the fixed sheave 304. Is fixed to the side opposite to the belt engaging surface (front side in FIG. 16). The cylindrical portion 171 is fixed so as not to rotate relative to the driven shaft 70 by the engagement of the spline groove 175 formed inside and the spline groove formed on the outer peripheral surface of the driven shaft 70. A claw portion 176 of the movable sheave member 300 is penetrated through a portion that is not blocked by the shaft fixing member 170 inside the through hole 174 so as to be relatively movable in the axial direction.

  On the other hand, referring back to FIG. 9, the drive pulley 20 and a fixed sheave 178 integrally formed with the drive shaft 32 and a movable sheave arranged around the drive shaft 32 and movable relative to the fixed sheave 178 in the axial direction. 179, a spring 180, a spider 181, a base member 182, and a fly weight mechanism 184. The fixed sheave 178 may be formed as a separate member from the drive shaft 32 and may be fixed to the drive shaft 32 by screw connection or the like.

  The spider 181 is supported by screw connection so as not to move in the axial direction with respect to the drive shaft 32 and also to prevent relative rotation. The base member 182 is disposed on the outer diameter side of the drive shaft 32, is connected to the movable sheave 179 via the connecting member 186, and is formed to move integrally with the movable sheave 179.

  The spider 181 and the connecting member 186 are provided with an engagement structure including a hole or a groove for engaging the movable sheave 179 so as to rotate in synchronization with the spider 181. The connecting member 186 engages with the hole or the groove.

  The spring 180 is provided between the drive shaft 32 and the base member 182, and biases the movable sheave 179 in a direction away from the fixed sheave 178 via the base member 182.

  The flyweight mechanism 184 includes a plurality of blade-like flyweights 188 supported on a side opposite to the belt engaging surface of the movable sheave 179 and swingable about an axis orthogonal to the radial direction, and a spider 181. And a supported engagement member 190.

  When the rotational speed of the drive shaft 32 increases, the flyweight mechanism 184 opens so that the tip of the flyweight 188 is displaced to the outer diameter side by the action of centrifugal force, and presses the engaging member 190 to As a reaction, the movable sheave 179 is displaced so as to approach the fixed sheave 178 against the biasing force of the spring 180.

  A movable sleeve 192 and a one-way clutch 194 are provided between the belt 24 and the drive shaft 32. The movable sleeve 192 is supported to be rotatable relative to the drive shaft 32 in the axial direction and to be rotatable.

  As shown in FIG. 17, the movable sleeve 192 includes a cylindrical portion 200 fitted and arranged on the outer diameter side of the drive shaft 32, and an end portion on the fixed sheave 178 side (left side in FIG. 17) in the cylindrical portion 200. It has a flange portion 196 protruding to the outer diameter side and a spiral groove 202 formed in the cylindrical portion 200 so as to be inclined in the axial direction.

  Returning to FIG. 9, the one-way clutch 194 is disposed on the outer diameter side of the cylindrical portion 200 of the movable sleeve 192 so as to be in contact with the inner peripheral surface of the belt 24. The one-way clutch 194 is formed so as to transmit the rotational force in the forward rotation direction from the belt 24 to the movable sleeve 192 but not to transmit the rotational force from the movable sleeve 192 to the belt 24.

  A cam mechanism 201 is provided between the movable sleeve 192 and the drive shaft 32. As shown in FIG. 17, the cam mechanism 198 is formed by a spiral groove 202 formed in the movable sleeve 192 and a protrusion 204 that protrudes and is fixed to the outer peripheral surface of the drive shaft 32 and engages with the spiral groove 202. . When the movable sleeve 192 rotates relative to the drive shaft 32 in the normal rotation direction, the cam mechanism 198 moves the flange portion 196 of the movable sleeve 192 in the axial direction so as to approach the side surface of the belt 24 (FIG. 9). Specifically, due to the relative rotation of the movable sleeve 192 in the forward rotation direction with respect to the drive shaft 32, the spiral groove 202 relatively moves in the direction of the arrow β in FIG. In this case, the movable sleeve 192 moves in the axial direction in the direction of the arrow γ in FIG.

  With the above-described configuration, it is possible to prevent the occurrence of the creep phenomenon in which the rotational force is transmitted from the drive shaft 32 to the driven shaft 70 and the wheels are driven at a minute speed in the idle rotation state of the engine as follows. When the operation of the accelerator pedal is canceled while the vehicle is traveling, the engine brake can be used effectively.

  First, when the engine is idling, the tip of the flyweight 188 of the flyweight mechanism 184 is displaced toward the inner diameter side. In this case, the distance between the sheaves increases so that the belt 24 is not sandwiched between the fixed sheave 178 and the movable sheave 179 due to the urging force of the spring 180, so that the inner peripheral surface of the belt 24 is the one-way clutch 194. Contact the outer ring. In this state, the one-way clutch 194 does not transmit power from the drive shaft 32 to the belt 24, so that the occurrence of a creep phenomenon can be prevented.

  On the other hand, when the engine output increases and the rotational speed increases, the tip of the flyweight 188 of the flyweight mechanism is displaced to the outer diameter side, so the distance between the sheaves is reduced against the biasing force of the spring 180. Thus, the belt 24 is sandwiched between the fixed sheave 178 and the movable sheave 179, power is transmitted from the drive shaft 32 to the driven shaft 70, and the reduction ratio of the continuously variable transmission 12 is gradually reduced, so that the wheel The speed increases gradually.

  When the engine brake is applied as in the case where the vehicle is traveling on a downhill, the driver decelerates by releasing the accelerator pedal. On the other hand, since the inertial force is transmitted from the wheels to the driven shaft 70, the driven shaft 70 rotates at a higher speed than the drive shaft 32. In this case, the flyweight mechanism 184 displaces the tip of the flyweight 188 toward the inner diameter side, so that the movable sheave 179 is separated from the fixed sheave 178 by the biasing force of the spring 180.

  Further, the rotational force in the forward rotation direction is transmitted from the belt 24 to the outer ring of the one-way clutch 194, and the one-way clutch 194 transmits power from the belt 24 to the movable sleeve 192. In this case, since the movable sleeve 192 rotates in the forward rotation direction relative to the drive shaft 32, the movable sleeve 192 is moved to the movable sheave 179 side by the cam mechanism 201, and the flange portion 196 of the movable sleeve 192 is moved to the belt 24. Press close to the side. In this state, the belt 24 is sandwiched between the flange portion 196 and the movable sheave 179, and the inertial force applied from the driven shaft 70 is transmitted, which is applied as a load to the engine, so that the engine brake can be used effectively. .

  The drive pulley 20 does not use such a cam mechanism 201, and the configuration used in the driven pulley 22 in the configuration shown in FIGS. 1 to 8 described above is used to reduce the sheave distance by the biasing force of the spring. It is also possible to use a configuration in which a spring is arranged.

  Also in the case of the above configuration, the durability of the gear can be improved as in the configurations of FIGS. Further, the distance between sheaves at the driven pulley 22 can be arbitrarily set by the control of the electric motor 92, and the reduction ratio can be arbitrarily set.

  In the case of this example, the second case element 134 side portion of the actuator 26 </ b> A is provided on the opposite side of the driven pulley 22 with respect to the motor side gear 98 in the axial direction. Therefore, despite the movement of the movable sheave member 300, the second case element 134 side portion of the actuator 26A is closer to the belt 24 and the fixed sheave 304 side than the configurations of FIGS. It is possible to effectively prevent interference between the actuator 26A and the belt 24 and the fixed sheave 304, thereby realizing a small configuration.

  In the case of this example, the torque transmission member 46 is disposed on the actuator 26A side of the movable sheave member 300, and the claw portion 176 that engages with the torque transmission member 46 is disposed on the inner diameter side of the fixed sheave 304. For this reason, the torque transmission member 46 can be moved so as to pass inside the belt 24, and the belt-type continuously variable transmission 12 can be further downsized. Other configurations and operations are the same as those in FIGS. 1 to 8.

  FIG. 18 is a diagram corresponding to FIG. 4 in a second example of another example of the embodiment of the present invention. In the case of this example, in the configuration shown in FIG. 1 to FIG. 8 described above, the gear case 96 and the lid portion of the movable feed member 94 on the outer diameter side of the fixed cylinder portion 114 and the inner cylinder portion 103 inside the gear case 96. An urging force generation member 206 is disposed between the urging force generation member 206 and the urging force generation member 206. The urging force generation member 206 is formed by a coil spring and urges the movable feed member 94 toward the drive pulley 20 in the axial direction.

  In such a configuration, referring to FIG. 2, the driving pulley 20 pushes the belt 24 from the belt 24 to the movable sheave member 28 so as to increase the sheave distance by the biasing force of the spring 64 provided on the driven pulley 22. Pressure is applied. On the other hand, in the drive pulley 20, force is applied to the movable sheave member 28 so as to reduce the distance between the sheaves against the urging force of the spring 64 by the generation of torque in the forward rotation direction of the electric motor 92. In this case, in the configuration of this example, the torque of the electric motor 92 can be assisted by the urging force of the urging force generating member 206, and the maximum value that is the peak of the necessary generated torque of the electric motor 92 can be reduced.

  This will be described in detail with reference to FIG. FIG. 19 is a diagram illustrating motor torque necessary for changing the distance between sheaves in the drive pulley 20 when the electric motor 92 rotates in the reverse direction after the normal rotation in the second example. FIG. 19 shows a case where the motor-side gear operates with a certain load when the electric motor 92 rotates forward and backward.

  In the case of this example shown by the solid line a in FIG. 19, the torque necessary to reduce the distance between the sheaves of the drive pulley 20 is reduced to T1 when the electric motor 92 is rotated forward. This is because the urging force generating member 206 presses the movable feed member 94 toward the drive pulley 20 and generates a urging force in a direction in which the movable sheave member 28 approaches the fixed sheave 30. A two-dot chain line b in FIG. 10 is a configuration in which the urging force generation member 206 is omitted in the configuration of this example, and the torque required during the forward rotation of the electric motor 92 is larger than that in this example.

  On the other hand, at the time of reverse rotation of the electric motor 92, it is necessary to displace the movable feed member 94 against the urging force of the urging force generating member 206 in the configuration of this example, and the absolute amount of necessary torque of the electric motor 92 is T2. However, the difference in the absolute amount of the required torque can be reduced when the electric motor 92 rotates forward and backward. For this reason, since the maximum value of the required torque of the electric motor 92 can be reduced as a whole including during forward rotation and reverse rotation, the required capacity of the electric motor 92 can be reduced and the size can be reduced.

  Further, the urging force generating member 206 can be disposed in the gear case 96 without enlarging the gear case 96, and the actuator 26 is not excessively enlarged. Further, since the load fluctuation in the forward rotation and the reverse rotation can be reduced when the electric motor 92 is driven, the control can be simplified and the controllability can be improved. Other configurations and operations are the same as those shown in FIGS.

  In the configuration of this example, the urging force generating member 206 may be disposed at a position indicated by a two-dot chain line δ in FIG. Specifically, even if the urging force generation member 206 is disposed between the gear case 96 and the fixed member fixed to the inner peripheral side of the inner cylinder portion 103 on the inner diameter side of the fixed cylinder portion 114 and the inner cylinder portion 103. Good. The fixing member may be a locking member locked in a locking groove formed on the inner diameter side of the inner cylindrical portion 103 or an outer ring of the bearing 108. Also in this case, the maximum value of the necessary generated torque of the electric motor 92 can be reduced by the urging force generating member 206. Further, the urging force generating member 206 can be disposed in the gear case 96 without enlarging the gear case 96.

  Further, in the configuration in which the actuator 26A is provided in the driven pulley 22 as in the first example of another example shown in FIGS. 9 to 17, the same position as in FIG. 18 or the same as the two-dot chain line δ in FIG. The biasing force generating member 206 may be disposed at the position. In this case, in the driven pulley 22, the maximum value of the necessary generated torque of the electric motor 92 when the movable sheave member 300 is moved in the direction of increasing the sheave distance by the biasing force generating member 206 can be reduced.

  FIG. 20 is a view showing an integrated structure 210 in which the gear reduction mechanism 208 is integrated with the continuously variable transmission 12 according to the embodiment of the present invention. In the case of this example, the integrated structure 210 includes a reduction gear element 212 that is provided between the drive shaft 32 and the engine 14 that is a power source and is provided on the drive shaft 32 side of the continuously variable transmission 12. The reduction gear element 212 includes a reduction gear case 214 which is a reduction gear housing portion fixed to the transmission case 27, and a gear reduction mechanism 208 housed in the reduction gear case 214. The gear reduction mechanism 208 is integrated with an input shaft 216 coaxially connected to the output shaft 34 of the engine 14, a small-diameter gear fixed to the input shaft 216, and a drive shaft 32 disposed in the speed reducer case 214. A large-diameter gear fixed to the shaft portion 218 and meshing with the small-diameter gear. Since the gear reduction mechanism 208 decelerates the rotation of the input shaft 216 and transmits it to the shaft portion 218, the rotation of the engine 14 is decelerated and transmitted to the drive shaft 32.

  The reduction gear case 214 is fixed to the transmission case 27 in a state in which a wall portion 222 is provided so as to be partitioned from the belt arrangement space 220 in which the belt 24 of the continuously variable transmission 12 is arranged. Lubricating oil is placed in the speed reducer case 214.

  According to the above configuration, the inside of the reduction gear case 214 can be set as an oil lubrication region, and the inside of the transmission case 27 can be set as a non-lubrication region. Further, since the rotation of the output shaft 34 is decelerated and transmitted to the drive shaft 32 by the gear reduction mechanism 208, even when the engine 14 rotates at high speed, the load on the bearing provided on the support portion of the drive shaft 32 is reduced. Durability. Further, since the transmission case 27 and the speed reducer case 214 are integrated, the number of parts can be reduced, and the structure having the function of reducing the speed of the drive shaft 32 can be reduced.

  Further, as indicated by a broken line in FIG. 21, the input shaft 216 to which the output shaft 34 of the engine 14 is connected may be positioned below the rotation center axis O of the drive pulley 20. In this case, since the input shaft 216 rotates integrally with the output shaft 34, the rotational speed increases. However, the lubricating oil contained in the speed reducer case 214 in FIG. 20 is absorbed by the input shaft 216 and its rotation support portion. Easily supplied to some bearings. For this reason, the lifetime improvement of the integral structure 210 can be aimed at. Further, since the gear reduction mechanism 208 is formed by a large gear and a small gear, the structure can be simplified and various reduction ratios can be easily set. Note that the gear reduction mechanism may be formed to have a reduction function of two or more stages instead of a one-stage reduction. Further, instead of the gear reduction mechanism, a reduction device including a belt or a chain may be used. Other configurations and operations are the same as those shown in FIGS. The configuration of this example can be combined with the configurations shown in FIGS.

  FIG. 22 is a schematic diagram showing a positional relationship between the drive pulley 20 and the driven pulley 22 and the electric motor 92 in a third example of another example of the embodiment of the present invention. The continuously variable transmission 12 of this example has the maximum inscribed circle of the outer peripheral surface of each pulley 20 and 22 when the driving pulley 20 and the driven pulley 22 are viewed in the axial direction in the configuration shown in FIGS. The first straight line L1 and the second straight line L2 that are connected to each other, the third straight line L3 that connects one ends of the two straight lines L1 and L2, and the fourth straight line L4 that connects the other ends of the two straight lines L1 and L2. Are formed so that the electric motor 92 of the actuator 26 is disposed in a rectangular region (region indicated by hatching in FIG. 22).

  In the case of this example, the continuously variable transmission 12 including the electric motor 92 can be reduced in size. In addition, since the transmission case that houses the continuously variable transmission 12 can have a simple shape that is not significantly affected by the structure of the electric motor 92, the manufacturing cost can be reduced. Note that the configuration of this example may be combined with any one of the configurations of the other examples of FIGS. 9 to 21 described above.

  Further, as shown by the broken line in FIG. 22 in the electric motor 92A, in any one of the above examples, two actuators 26 for changing the distance between sheaves on both sides of the drive pulley 20 and the driven pulley 22 are provided. 26A can also be provided. In this case, when the pulleys 20 and 22 are viewed in the axial direction, the electric motors 92 and 92A of the two actuators 26 and 26A can be formed so as to be disposed in the rectangular region. . In this case, since the distance between sheaves can be arbitrarily controlled by controlling both pulleys 20 and 22, it is easy to perform more precise control.

  FIG. 23 is a schematic diagram showing a continuously variable transmission of a fourth example of another example of the embodiment of the present invention. In the case of this example, in the configuration shown in FIGS. 9 to 17, the transmission case 27 is omitted, and the actuator 26A is disposed on the gear transmission mechanism 18 side with respect to the driven pulley 22 in the axial direction of the driven pulley 22. The gear case 96 of the actuator 26A is fixed to the case of the gear transmission mechanism 18 by a fixed stay 224. In this case, the degree of freedom of the arrangement position of the fixed stay 224 can be increased, and the belt can be easily replaced without removing the components of the actuator 26A. For this reason, the maintenance property can be improved.

  FIG. 24 is a schematic diagram showing a part of a fifth continuously variable transmission according to another example of the embodiment of the present invention. In the case of this example, in the configuration of FIG. 23 described above, an actuator 26A is arranged on the opposite side of the gear transmission mechanism 18 with respect to the driven pulley 22 with respect to the axial direction of the driven pulley 22, and the actuator 26A is connected to the gear transmission mechanism by the fixed stay 224. It is fixed to 18 cases. In this case, since the actuator 26A is on the same side as the flyweight mechanism 184 (see FIG. 23) of the drive pulley 20 in the axial direction, the size can be reduced.

  FIG. 25 is a schematic diagram of a sixth continuously variable transmission according to another example of the embodiment of the present invention. In the case of this example, in the configuration shown in FIGS. 9 to 17, the fixed stay 224 is fixed to the gear case 96 of the actuator 26A on the opposite side to the gear transmission mechanism 18 in the axial direction. The actuator 26 </ b> A is fixed by a fixed stay 224 on the inner surface of the transmission case 27 on the opposite side to the gear transmission mechanism 18 in the axial direction. In this case, there is no need to penetrate the fixing stay 224 inside the belt 24.

  FIG. 26 is a diagram illustrating a relationship between the torque reaction force of the electric motor 92 and the reduction ratio of the continuously variable transmission 12 in a seventh example of another example of the embodiment of the present invention. In the configuration of this example, in the configuration of FIGS. 9 to 17 described above, a control device (not shown) controls the driving of the electric motor 92 so that the sheave interval holding function is provided by the torque of the electric motor 92. Further, the pitch of the feed screw mechanism formed by the inner cylinder portion 103 and the fixed cylinder portion 114 provided on the driven pulley 22 side is increased so that the sheave interval is not held by screw engagement. In addition, a current sensor (not shown) that detects the drive current of the electric motor 92 is provided.

  Further, the control device calculates a necessary torque of the electric motor 92 for keeping the sheave position constant in a state where the reduction ratio is constant from the detected value of the drive current. Further, the control device controls the drive of the electric motor 92 so as to generate this necessary torque. Furthermore, when the required torque of the electric motor 92 exceeds a predetermined value K1 set in advance, the control device performs stepless control according to the increase in the required torque as special control different from normal control executed using a control map or the like. The drive of the electric motor 92 is controlled so as to increase the reduction ratio of the transmission 12.

  According to such a configuration, the tension applied to the belt 24 can be estimated from the calculated value of the necessary torque of the electric motor 92 for keeping the sheave position constant. Further, when the required torque exceeds the predetermined value K1, the reduction ratio of the continuously variable transmission 12 increases. In this case, since it can be determined that the engine is overloaded, an overload condition can be avoided by increasing the speed reduction ratio.

  The configuration of the continuously variable transmission is not limited to the configurations of the above examples, and various configurations can be adopted without departing from the gist of the present invention. For example, a configuration in which the belt 24 is sandwiched between two fixed sheaves of the drive pulley 20 and the driven pulley 22 that do not change the distance between the sheaves 20 (or 22) may be employed.

  DESCRIPTION OF SYMBOLS 10 Vehicle power transmission mechanism, 12 Belt type continuously variable transmission, 14 Engine, 16 wheels, 18 Gear transmission mechanism, 20 Drive pulley, 22 Driven pulley, 24 Belt, 26, 26A Actuator, 27 Transmission case, 28 Movable sheave Member, 29 Movable sheave body, 30 Fixed sheave, 31 Fixed stay, 32 Drive shaft, 34 Output shaft, 36 Claw portion, 38 Needle bearing, 40 Outer ring, 42 Sliding bearing, 44 Belt engagement groove, 46 Torque transmission member, 48 Shaft fixed portion, 50 Support shaft, 52 Roller, 54 Movable cylinder portion, 56 Fixed sheave, 58 Movable sheave, 59 Movable sheave body, 60 First driven torque transmitting member, 62 Second driven torque transmitting member, 64 Spring, 65 curved portion, 66 bearing support portion, 68 guide hole, 70 driven shaft, 72 input shaft, 74 bearing, 76 belt engagement groove, 78 sheave fixing member, 80 first roller, 82 plain bearing, 83 support shaft, 84 inner cylinder portion, 86 sheave fixing portion, 88 claw portion, 90 shaft fixing cylinder portion, 91 support shaft, 92, 92A electric motor, 93 second roller, 94 movable feed member, 96 gear case, 98 motor side gear, 100 gear mechanism, 102 elastic member, 103 inner cylinder part, 104 outer cylinder part, 106 lid part, 108 ball bearing, 109 feed Screw, 110 Outer gear, 114 Fixed cylinder part, 116 Outer cover, 118 Second fixed cylinder part, 120 Feed screw, 122 Bottom part, 124 Wall part, 126 Opening part, 128 Tip side plate part, 130 Bearing, 131 Bearing support part, 132 1st case element, 134 2nd case element, 137 Motor case, 138, 139 Gear, 140 cylinder Portion, 141 gear, 142 hole portion, 144 first gear shaft, 145 second gear shaft, 146 large diameter gear, 147 second gear shaft, 148 fixed stay, 149 second gear shaft, 150 cylinder portion, 152, 154 plate Part, 156 fastening means, 157 sheave position sensor, 158 one-side case element, 159 rotating shaft, 160 other-side case element, 161 swing arm, 162 spring.

Claims (12)

One side pulley and the other side pulley, a belt wound around the one side pulley and the other side pulley, and an actuator,
The one-side pulley includes a movable sheave member that is disposed so as to be relatively movable in an axial direction with respect to a fixed sheave fixed to a rotating shaft, and sandwiches the belt with the fixed sheave.
The actuator is a belt-type continuously variable transmission that moves the movable sheave member in the axial direction,
The actuator is
The movable sheave member is supported on the outer diameter side of the movable shaft so as to be rotatable with respect to the center of the rotation axis, and is disposed around the inner cylinder portion provided with a movable-side feed screw, and the outer gear is disposed on the outer diameter side. A movable feed member including a provided outer cylinder part, and a lid part connecting the inner cylinder part and the outer cylinder part;
A fixed cylinder portion provided with a fixed-side feed screw that is screw-engaged with the movable-side feed screw; and an outer cover provided integrally with the fixed cylinder portion, wherein an opening portion into which the outer cylinder portion is inserted is provided. A gear case including an outer cover that houses the outer gear;
An electric motor that drives a motor side gear that meshes with the outer gear;
The belt-type continuously variable transmission according to claim 1, wherein the opening portion is opposed to the outer peripheral surface of the one-side pulley side closer to the outer gear than the outer gear in the axial direction of the rotating shaft in the outer cylinder portion. The belt-type continuously variable transmission according to claim 1,
In the outer cylinder portion, an elastic member that is locked to one of the outer peripheral surface on the one-side pulley side and the inner peripheral surface of the opening with respect to the axial direction of the rotating shaft and slidably contacts the other is provided. A belt-type continuously variable transmission. The belt-type continuously variable transmission according to claim 1 or 2,
The fixed cylinder part is provided on the outer diameter side of the inner cylinder part,
The gear case includes a second fixed cylinder portion that is provided coaxially with the fixed cylinder portion on the inner diameter side of the fixed cylinder portion and has a support portion that supports a bearing between the rotation shaft and the inner peripheral surface side. ,
The belt, wherein the second fixed cylinder part is in contact with the inner peripheral surface of the inner cylinder part or through a minute gap over the entire axially movable range of the inner cylinder part. Type continuously variable transmission. The belt-type continuously variable transmission according to any one of claims 1 to 3,
A torque transmission member having a shaft fixing portion fixed to the outer diameter side of the rotating shaft, a support shaft protruding to the outer diameter side of the shaft fixing portion, and a roller rotatably supported by the support shaft. ,
The movable sheave member includes a plurality of claw portions that are arranged around the rotation shaft, project to the actuator side, and guide the roller between inner circumferential surfaces facing each other.
The belt-type continuously variable transmission, wherein the roller presses a circumferential inner surface of the claw portion in a rotation direction of the rotation shaft when the rotation shaft rotates. The belt type continuously variable transmission according to any one of claims 1 to 4,
A belt-type continuously variable transmission comprising a biasing force generating member that is provided between the gear case and the movable feed member and biases the movable feed member toward the one pulley side. The belt-type continuously variable transmission according to claim 5,
The belt-type continuously variable transmission according to claim 1, wherein the urging force generating member is disposed on an outer diameter side of the fixed cylinder part and the movable cylinder part inside the gear case. The belt-type continuously variable transmission according to claim 5,
The belt-type continuously variable transmission is characterized in that the urging force generating member is disposed on an inner diameter side of the fixed cylinder part and the movable cylinder part. The belt-type continuously variable transmission according to any one of claims 1 to 7,
The belt-type continuously variable transmission according to claim 1, wherein the one-side pulley is a drive pulley on the power source side. The belt type continuously variable transmission according to claim 8,
A belt-type continuously variable transmission, comprising: a reduction gear provided between the rotary shaft and the power source and configured to decelerate rotation of the power source and transmit the reduced speed to the rotary shaft. The belt-type continuously variable transmission according to claim 9,
A belt-type continuously variable transmission comprising: a reduction gear housing portion that is provided integrally with the gear case so as to be partitioned with respect to a belt arrangement space, houses the reduction gear, and contains lubricating oil therein. The belt-type continuously variable transmission according to any one of claims 1 to 10,
A fixing stay for fixing the gear case to another member, and arranged so as to pass through a space serving as a belt inner region in all belt position setting states in the belt spanned between the driving pulley and the driven pulley. A belt-type continuously variable transmission comprising a fixed stay. The belt-type continuously variable transmission according to any one of claims 1 to 11,
When the one-side pulley and the other-side pulley are viewed in the axial direction, the first straight line and the second straight line that join the maximum inscribed circles of the outer peripheral surfaces of the pulleys, and the first straight line and the second straight line The electric motor is formed in a rectangular area formed by a third straight line connecting the one ends and a fourth straight line connecting the other ends of the first straight line and the second straight line. A belt-type continuously variable transmission.

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