JPH02180340A - Belt type continuous transmission - Google Patents

Abstract

PURPOSE:To prevent a threaded part from slackening by furnishing at least either of the two shafts, a primary and a secondary, at its tail part with a male threaded part in the same dia. as the shaft, forming fit parts on both sides thereof in its axial direction, and providing a female threaded part to be in engagement with the mentioned male threaded part at a flange secured to the shaft so as to bear the axial force, and forming a center alignment part on its both sides in the axial direction. CONSTITUTION:An axial force nipping a belt 7 is applied to pulleys 5, 6, wherein for ex. the axial force applied to a movable sheave 5b of the primary pulley 5 acts on a flange 19 through a mechanical actuator 10 and a thrust bearing 20 to be borne by a shaft 2. The belt 7 nipping force acts only where the pulley 5 is wrapped, and a moment is applied also to the flange 19 repeatedly. This moment is borne by center alignment parts 19b, 19c of a female threaded part 19a on its both sides in axial direction and by fit parts 2c, 2d of the shaft 2 on both sides of its male threaded part 2d, and no major moment will be applied to threaded part. This hinders the threaded parts from slackening.

Description

[Detailed description of the invention]

(a) Industrial application field The present invention provides a primary and secondary pulley consisting of a movable sheave and a fixed sheave, respectively, and a belt made of metal or the like (
The present invention relates to a belt-type continuously variable transmission (CVT) in which a belt-type continuously variable transmission (CVT) is wound around (including a chain type), and more specifically to a fixing/supporting device for a flange portion that is fixed to the shaft end with a screw and receives axial force from a pulley. (11) Prior Art Recently, automatic transmissions incorporating belt-type continuously variable transmissions have been attracting attention as automotive transmissions due to demands for improved fuel consumption. Conventionally, as shown in Japanese Unexamined Patent Publication No. 62-13853, the present applicant applied an axial force corresponding to the transmitted torque to the pulley using a pressure regulating cam mechanism, and applied a mechanical actuator such as a pole screw device to the pulley. He devised a belt-type continuously variable transmission device whose effective diameter was adjusted. The belt-type continuously variable transmission device carries the axial force acting on the pulley through a pressure regulating cam mechanism, through a mechanical actuator, or directly by the shaft, thereby increasing the A closed loop is formed in which large axial force acts as tensile stress within the shaft, and the structure is such that large axial force does not act on the case or the like. In addition, the shaft is integrally molded with a flange at one end, and the flange at the other end is attached to the pulley at the top.
It must be fixed to the shaft with screws, and the axial force from the pulley acts on the shaft at these flanges. Generally, a male threaded portion with a small diameter is formed in a stepped shape at the tip of the shaft, and a nut member is screwed into the male threaded portion to prevent and fix the flange portion. (C) Solution to the invention By the way, a large axial force from the pulley acts on the above-mentioned flange part, and a large bending moment due to the belt wrapping around only a part of the pulley acts on the shaft. However, the support structure of the flange part, which is formed by screwing a nut member into the threaded part formed in the small diameter part mentioned above, has a disadvantageous structure in terms of strength against axial force and bending moment. In addition, since the threaded portion is subjected to repeated bending, the nut member is easily loosened. Furthermore, a thrust bearing is interposed between the back of the mechanical actuator and the above-mentioned flange, but the dimensions of the flange are determined by the threaded part, so the flange must have sufficient perpendicular accuracy. Due to this difficulty, there is a risk that the above-mentioned thrust bearing may hit unevenly and reduce its durability. SUMMARY OF THE INVENTION Therefore, an object of the present invention is to provide a belt-type continuously variable transmission which solves the above-mentioned problems by improving the strength of the screws that fix the flange portion and by significantly reducing the moment applied to the screws. It is. (d) Means for Solving the Problems The present invention has been made in view of the above-mentioned circumstances, and for example, when shown with reference to FIGS. 1 and 2, shafts (2) and (3) are provided, respectively. A primary pulley (5) and a secondary pulley (6) consisting of two sheaves supported by and movable relative to each other in the axial direction, and both pulleys (5), (
The belt (7) that is wrapped around the belt (6) and both of these pulleys (
5) Mechanical actuators (1o) and (11) for moving the movable sheaves (5b) and (6b) of (6) in the axial direction, and the shaft is provided with an axial force from the pulleys (5) and (6). In a belt type continuously variable transmission (1) supported by (2) and (3), a shaft (2) and a shaft (2) are connected to the rear end of at least one of the primary and secondary shafts (2). A male threaded portion (2b) having approximately the same diameter is formed, and fitting portions (2c) and (2d) are formed on both sides of the male threaded portion (2b) in the axial direction.
2), which is fixed to the flange part (19) to support the axial force from the pulley (5), and a female threaded part (19a) that is screwed into the male threaded part (2b) The fitting portions (2c) and (2d) are located on both axial sides of the
It is characterized by forming centering portions (19b) and (19c) that fit into the centering portions. Further, the fitting part (2d) on the rear end side of the shaft (2) is made small in diameter to form a shoulder part (2e), and the flange part (2e) is formed with a small diameter.
19) The centering part (19C) on the rear end side has a small diameter, and the axial positioning part (2e) abuts on the shoulder part (2e), (
1-9d). Furthermore, the movable sheave (5b) acts on the flange portion (19) via the mechanical actuator (io).
), and a self-aligning mechanism (22) is interposed between the thrust bearing (20) and the flange (19). (e) Effect Based on the above configuration, the rotation of the primary pulley (5) is transmitted to the secondary shaft (3) via the belt (7) and the secondary pulley (6). At this time, pulley (5
), (6) are subjected to a large axial force that pinches the belt (7), for example, the primary pulley (5 → movable sheave (5)
The axial force acting on b) is applied to the flange portion (1) via a mechanical actuator (10) and a thrust bearing (20).
9), and the flange portion (], 9) (2
). In addition, the clamping force of the belt (7) is determined by the pulley around which the belt (7) is wound.

The winding (5) acts only on a portion (for example, see the upper half of the primary pulley (5) in FIG. 2), and as a result, moment acts repeatedly on the flange portion (19) as the pulley rotates. The flange part (19)
The moment acting on the centering portions (19b) and (19c) located on both sides of the female threaded portion (19a) in the axial direction and the fitting portions on both sides of the male threaded portion (2b) of the shaft (2) (2
c) and (2d), and no large moment acts on the male threaded portion (2b) and female threaded portion (19a), thereby preventing the threaded portions (2b) and (19a) from loosening. be done. Further, the fitting part (2d) and centering part (19C) on the rear end side are formed to have a small diameter, and can be positioned by the shoulder parts (2e) (19d). Furthermore, the above-mentioned axial force is carried by the thrust bearing (20) via the self-aligning mechanism (22), so that the thrust bearing <2o)'' does not hit unevenly, and the moment applied to the flange part (19) is Note that the symbols in parentheses are used to contrast with the drawings to facilitate understanding, and do not limit the structure in any way, and even if the symbols are the same, they do not fall within the scope of the claims. Correspondingly, some names are different from those of the embodiments shown below because they are described in the general concept. First, an outline of the present automatic continuously variable transmission will be described with reference to FIG. Output member 70 consisting of mechanism 40, transfer device 80, reduction gear device 71, etc.
, a forward/reverse switching device 90 consisting of a dual planetary gear mechanism, and a starting device 100 consisting of a fluid coupling 101, a centrifugal lock-up clutch 102, and a slip clutch 103. The planetary gear mechanism 40 has a ring gear 4
0R is interlocked with the secondary shaft 3 of the continuously variable transmission 1, the carrier 40C is interlocked with the output member 70, and the sun gear 40S is connected to a row one-way clutch F and a low coast clutch F, which constitute a locking means via a transfer device 80. It is connected to the reverse brake B1 and also to the input shaft 60 via the high clutch C2. Further, the dual planetary gear mechanism 90 has a sun gear 908 connected to the input shaft 60, a carrier 90C connected to the primary shaft 2 of the continuously variable transmission 1, and connected to the input shaft 60 via the forward clutch C1. Ring gear 90R is connected to reverse brake B2. Based on the above configuration, each clutch, brake, and one-way clutch in the present automatic continuously variable transmission A operate as shown in FIG. 6 at each position. Note that * indicates that the lock-up clutch 102 can be operated appropriately by centrifugal force. To be more specific, in the low speed mode L in the D range, the forward clutch C1 is connected and the row one-way clutch F is operated. In this state, the rotation of the engine crankshaft is transmitted to the input shaft 60 via the lock-up clutch 102 and slip clutch 103 or via the fluid coupling 101, and further directly transmitted to the sun gear 903 of the dual planetary gear device 90. The signal is transmitted to the carrier 90C via the forward clutch C1. Therefore, the dual planetary gear mechanism 90 rotates together with the input shaft 60, transmits the positive rotation to the primary shaft 2 of the belt type continuously variable transmission 1, and further transmits the rotation which is appropriately changed in speed by the continuously variable transmission 1. Secondary shaft 3 to ring gear 4 of single planetary gearing 40
It is transmitted to 0R. On the other hand, in this state, the sun gear 403, which is a reaction force support element that receives a reaction force, is stopped by the row one-way clutch F via the transfer device 80, and therefore the rotation of the link gear 40R is taken out from the carrier 40C as a decelerated rotation. and further a reduction gear device 71
It is transmitted to the axle shaft 73 via etc. Furthermore, in the high speed mode H in the D range, the high clutch C2 is connected in addition to the forward clutch C1. In this state, in the same way as described above, the forward rotation that has been appropriately shifted by the continuously variable transmission 1 is taken out from the secondary shaft 3 and transferred to the ring gear 40R of the single planetary gear device 40.
is input. Meanwhile, at the same time, the rotation of the input shaft 60 is transmitted to the sun gear 408 of the single planetary gear mechanism 40 via the high clutch C2 and the transfer device 80, whereby the torques of the ring gear 40R and the sun gear 40S are combined in the planetary gear mechanism 40. The signal is output from the carrier 40C. At this time, since the rotation against the reaction force is transmitted to the sun gear 403 via the transfer device 80, a predetermined plus torque is transmitted via the transfer device 80 without causing torque circulation. Then, the combined torque from the carrier 40C is transmitted to the axle shaft 73 via the reduction gear device 71 and the like. In addition, in operation in D range, it becomes free when reverse torque is applied (during engine braking) based on one-way clutch F, but in S range, in addition to low one-way clutch F, low coast reverse brake B1 is activated.
operates and transmits power even when reverse torque is applied. Furthermore, in the R range, the 9-verse brake B2 operates together with the low coast reverse brake B1. In this state, the rotation of the input shaft 60 is input to the belt-type continuously variable transmission 1 as reverse rotation from the carrier 90C because the ring gear 90R is fixed by the dual planetary gear mechanism 90. On the other hand, the sun gear 40S of the single planetary gear device 40 is fixed based on the operation of the low coast reverse brake B1, so that the reverse rotation from the continuously variable transmission device 1 is decelerated by the planetary gear mechanism 40 and taken out to the output member 70. Ru. Next, an embodiment embodying the present invention will be described with reference to FIG. This continuously variable transmission A has a transmission case 25 that is divided into three parts, and an input shaft 60 and a primary shaft 2 of the continuously variable transmission l are rotatably supported coaxially on the case 25. The secondary shaft 3 and the gear shaft 70a of the continuously variable transmission 1 are coaxially and rotatably supported to form a second shaft. Further, on the first shaft, a starting device 1oO, an operating section 50 consisting of a forward clutch C1, a high clutch C2, a low coast reverse brake B1, a reverse brake B2, a row one-way clutch F, and a forward/reverse switching device are configured. A dual planetary gear mechanism 90 and a hydraulic pump 61 are disposed, and a single planetary gear mechanism 40 is disposed on the second shaft. The starting device 100 includes a fluid coupling 101, a lock-up clutch 102 consisting of a centrifugal clutch, and a slip clutch 103. And slip clutch 103
is a cam mechanism 105 that generates an axial force corresponding to the load torque.
The cam mechanism 105 has a slip clutch 1.
Presses and acts on the clutch plate and disc of 03,
The torque capacity of the slip clutch 103 is increased in accordance with the increase in load torque. Further, a protrusion 25a protrudes from the case 25 on the engine side of the input shaft 60, and an input block block 81 of the transfer device 80 is supported by the protrusion 25a via a bearing. Further, the hub portion of the sprocket 81 is connected to the case protrusion 25a via a one-way clutch F, and the flange extending radially outward from the sprocket 81 has a flange on its inner circumferential surface. The input shaft 60 is connected via a high clutch C2 consisting of a multi-plate clutch, and the outer peripheral surface of the input shaft 60 is connected to the case 2.
A low coast & reverse brake B1 consisting of a multi-disc brake is interposed between the brake and the brake 5. Further, a sun gear 90S (see FIG. 5) of the dual planetary gear mechanism 90 is spline-coupled to the tip of the input shaft 60, and a flange extends in the outer diameter direction. Further, the tip of the input shaft 60 is fitted with the primary shaft 2 of the belt type continuously variable transmission 1 via a bushing.
The carriers 90C are aligned and splined to the shaft 2. Furthermore, a first pinion 90P1 and a second pinion 90P2 are supported by the carrier 90C, and a connecting member extends in the outer diameter direction,
A forward clutch C1 consisting of a multi-disc clutch is interposed between the inner diameter side of the connecting member and the outer diameter side of the flange from the input shaft 60. Further, a reverse brake B2 consisting of a multi-disc brake is interposed between the outer peripheral side of the support member fixing the ring gear 90R and the case 25. An actuator unit 51 is disposed between the low coast & reverse brake B1 and high clutch C2 and the reverse spray VB2 and forward clutch C1 in the operation section 50. It consists of an actuator 51a for a forward/reverse switching device and an actuator 51b for a low/high speed mode switching device, which are arranged adjacent to each other. The actuator unit 51 has a motor for a forward/reverse switching device and a motor for a low/high speed mode switching device which are arranged at a predetermined distance in the circumferential direction, and these motors include a commutator motor, a step motor, etc. The motor is comprised of an electric motor such as a rotating magnetic field motor, a servo motor, or an ultrasonic motor, and is provided with holding means such as an electromagnetic brake to maintain the motor at a predetermined rotational position. Further, the female threaded portions of ball screw devices 52 and 53 for the forward/reverse switching device and the low/high speed mode switching device are respectively fixed to the case 25, and the male threaded portions of the ball screw devices are respectively fixed to the case 25. It meshes with the output gear of the motor via a gear, and a connecting member is connected to each male threaded portion, respectively. The connecting member connected to the ball screw device 52 for the forward/reverse switching device engages the forward clutch C1 by moving axially in one direction, and engages the reverse brake B2 by moving axially in the other direction. Furthermore, the connecting member connected to the ball screw device 53 for the low-high speed motor switching device engages the high clutch C2 by moving in the axial direction in one direction, and engages the high clutch C2 by moving in the axial direction in the other direction. Engage rake B1. Further, as shown in FIGS. 1 to 4, the continuously variable transmission Tt, 1 consists of a primary pulley 5, a secondary pulley 6, and a belt 7 wound around these two pulleys, and both pulleys are fixed respectively. It consists of sheaves 5a, 6a and movable sheaves 5b, 6b. Further, the fixed sheet 5a of the primary pulley 5 is rotatably supported by the case 25 by a roller bearing 30, and the base end of the primary shaft 2 bulges in the outer radial direction to form a flange portion 2a. A pressure regulating cam mechanism 9 is interposed between the flange portion 2a and the back surface of the fixed sheave 5a. The pressure regulating cam mechanism 9 is connected to the flange portion 2 which is connected to the carrier 90C of the dual planetary gear mechanism 90 via the primary shaft 2.
A fixed side cam portion 9a whose axial movement is restricted at point a, a movable side cam portion 9b spline-coupled to the fixed sheave 5a and pressed into contact via a disk spring, and a movable side cam portion 9b interposed between both cam portions. The fixed sheave 5a is composed of a roller and applies an axial force corresponding to the transmitted torque to the fixed sheave 5a. In addition, the movable sheave 5b
is slidably supported by the hub portion of the fixed sheave 5a via a ball spline (linear ball bearing) 31, and a ball screw assembly HtO is disposed at the back thereof. The ball screw device 10 has a ball circulation passage 10
A large number of balls 10C1 are made up of a male threaded part 10a and a female threaded part 10b circulating at
The rear end portion is fixed to an adjusting member 26 which is restrained and supported in the axial direction and radial direction by the shoulder portion of 5. The adjusting member 26 rotatably supports the hub portion of the fixed sheave 5a and hence the primary shaft 2 by means of a roller bearing 33, and is also engaged with a worm 34, and is rotated based on the operation of the worm 34 to open the male thread. The initial tension of the belt 7 and the running center of the belt can be adjusted by rotating the portion 10a relative to the female threaded portion 10b. Further, a self-aligning mechanism 13 is fixed to the female screw portion 10b, and a thrust ball bearing 12 is interposed between the self-aligning mechanism 13 and the back surface of the movable sheave 5b. The thrust bearing 12 has a large number of balls 12b held by a cage 12c, and the balls 12b are in direct contact with four parts formed on the back surface of the movable sheave 5b, and are in contact with the movable sheave 5b. The opposite side is in contact with the race 12a. The other side surface of the race 12a has a spherical convex surface, and the spherical support surface 13a of the self-aligning mechanism 13 is in close contact with the spherical convex surface. The spherical support surface 13a is a concave surface that faces obliquely downward and has its focal point at the axis of the primary shaft 2, and the self-aligning mechanism 13 includes a protrusion extending obliquely along the spherical support surface 13a. It has a gear part 13b formed at the tip of the part and a key fixing part 13c which is integrally fixed to the female screw part 10b in the rotational direction and the axial direction. Further, as shown in detail in FIG. 3, the inner race 33 of the roller bearing 33 held by the adjustment member 26
a is a small diameter portion 5a in the boss portion 5a of the fixed sheave 5a;
, are retained and supported by a snap ring 33b, and the support plate 17 constituting a spring receiving member comes into contact with the other end of the inner race 33a, so that the support plate 17 is fixed to the fixed sheave boss portion 5a, It is installed in such a way that it is prevented from moving outward in the axial direction. That is, the inner lace 33
The stop on the right side of a is unnecessary. The support plate 17 has a cup-like shape, and is attached to the male threaded portion 10a of the ball screw device 10.
A large number of disc springs are provided between the edge 17a of the support plate 17 and the back surface of the movable sheave 5b in the gap formed between the inner peripheral surface of the retainer 12c of the thrust bearing 12, the boss portion 5a, and the outer peripheral surface. 15a... has been shortened,
Further, a coil spring 15b is compressed between the bottom 17b of the support plate 17 and the tip spring 15a. Therefore, these disc springs 15a and coil springs 15
b constitutes a spring means 15 that is interposed in parallel with the thrust bearing 12 and the mechanical actuator 10 and directly bears a part of the axial force from the movable sheave 5b, and the disc spring 15a is a belt-type spring means 15. When the continuously variable transmission device 1 is in a low-speed transmission state (upper half of Figure 2), it is in a predetermined compression state and applies a large axial force to the belt 7 required for low-speed transmission. High speed transmission state of device 1 (second
In the lower half of the figure), the belt 7 is in its natural length state and no axial force is applied to the belt 7. Additionally, a flange portion 1 is provided at the tip of the primary shaft 2.
9 is fixed by screw connection, and the flange portion 19
An automatic alignment machine jI422 is fixed to the. The automatic centering machine 'M422 has a spherical support surface 22 which has a convex surface facing obliquely outward and whose focal point is located on the axial extension line of the shaft 2.
It has a. Further, a thrust ball bearing 20 is interposed on the back side of the self-aligning mechanism 22 and the adjusting member 26, and the bear song 20 has a large number of balls 20b held in a cage and one race 20a. The ball 20b is in direct contact with a recess formed on the back surface of the adjustment member 26, and the race 20a in contact with the other side of the ball 20b has a spherical surface that is in close contact with the spherical support surface 22a of the self-aligning mechanism 22. It has a concave surface. That is,
The adjustment member 26, which is a support member, forms one race of the thrust bearing. On the other hand, as shown in FIG. 2, the fixed sheave 6a of the secondary pulley 6 is rotatably supported by the case 25 together with the secondary shaft 3 via a roller bearing 37, and the movable sheave 6b is rotatably supported by the secondary shaft 3.
It is slidably supported via a ball spline 31'. Furthermore, a ball screw device 11 is provided on the back side of the movable sheave 6b.
is disposed, and its male threaded portion 11a is fixed to an adjustment member 26' similar to the adjustment member 26. Therefore, the adjustment member 26' supports the secondary shaft 3 via a roller bearing 33'. At the same time, based on the rotation of the ohm 34', the adjustment member 2 on the primary side
6, the initial tension and running center line of the belt 7 can be adjusted. Further, a self-aligning mechanism 13' is fixed to the female threaded portion 11b, similar to the above-mentioned primary side.
And the automatic alignment mechanism 1! l13' and movable sheave 6b
A thrust ball bearing 12' is interposed on the back side of the. That is, the self-aligning mechanism 13' has a spherical support surface 13 made of a concave surface whose focal point is located at the axis of the secondary shaft 3.
′a, and further extends diagonally along the support surface, and a gear portion 13′b formed at the tip of the projection.
and a spline fixing portion 13'C. The thrust ball bearing 12' includes a ball 2'b which is in direct contact with a recess on the back surface of the movable sheave 6b, and a race 12 which has a spherical convex surface that is in close contact with the spherical support surface 13'a.
'a. Further, a spring means 16 consisting of a large number of disc springs 16a is disposed between the support plate 18 fixed to the shaft 3 and the back surface of the movable sheave 6b, as in the case of the primary side. The inner race 33'a of the roller bearing 33' mounted on the adjustment member 26' supports the stepped portion of the expanded diameter portion 3b of the secondary shaft 3, and A support plate 18 constituting a spring receiving member comes into contact with the end portion, so that the support plate 18 is attached to the shaft 3 so as to be prevented from moving inward in the axial direction. The support plate 18 has a cup-like shape and is connected to the male screw portion 11a of the ball screw device 11 and the thrust bearing 12' and the glue turner 12'.
A large number of disc springs 16a are compressed between the edge 18a of the support plate 18 and the back surface of the movable sheave 6b in the gap formed between the inner peripheral surface of C and the outer peripheral surface of the shaft 3. has been done. Therefore, these disc springs 16a constitute a spring means 16 that is interposed in parallel with the thrust bearing 12' and the mechanical actuator 11 and directly carries a part of the axial force from the movable sheave 6b. ,
In addition, when the belt-type continuously variable transmission 1 is in a high-speed transmission state (lower half of Figure 2), the disc spring 16a is in a predetermined compressed state and applies a large axial force to the belt 7, which is necessary for high-speed transmission. In the low-speed transmission mode B (upper half of FIG. 2) of the continuously variable transmission 1, the disc spring 16a is in a predetermined extended state and applies a predetermined axial force to the belt 7. Further, the secondary shaft 3 has a proximal end having an enlarged diameter and a hole 3a for receiving the gear shaft 70a, and an end of the shaft enlarged diameter portion 3b protrudes in the outer radial direction to form a flange portion 19'. A fixed sheave 6a is fitted to the tip of the shaft 3 via a key k, and a nut 38 is screwed to prevent the fixed sheave 6a from coming out.
Fixed. Similarly to the primary side, a self-aligning mechanism 22' is fixed to the flange portion 19', and has a spherical support surface 22'a which is a convex surface and whose focal point is located on the axial extension line of the shaft 3. and the automatic alignment machine f
i1122' and the rear surface of the adjustment member 26' are provided with a ball 2o'b that directly contacts the rear surface of the member and a race 20'a that has a spherical concave surface that is in close contact with the spherical support surface 22'a.
A thrust ball bearing 20' having a diameter is interposed. In FIG. 2, the reference numerals 39 and 39' indicate the fixed sheaves 5a and 6 on the primary side and the secondary side.
This is a groove for detection formed at the tip of the groove 3.
9.39' is counted by the electromagnetic sensors 5r-8t, thereby detecting the rotational speeds of the primary shaft 2 and the secondary shaft 3, respectively. And primary shaft 2 and secondary shaft 3
An operating device 130 is disposed at a portion that forms a triangle. The operating device 130 has a first operating shaft 131 and a 215th operating shaft supported by the case 25. The first operating shaft 131 rotatably supports a boss having a large gear 133 and a small gear 135, and a large gear 136 is integrally fixed thereto. Further, a large gear 137 is integrally fixed to the second operating shaft 132, and a boss having a small gear 139 and a large gear 140 is rotatably supported, and the small gear 135 of the first operating shaft 131 is meshed with the large gear 137 of the second operating shaft, and the large gear 136 of the 1st I operating shaft is meshed with the small gear 139 of the 2nd t1 operating shaft weight 32, respectively. Furthermore, non-circular gears 141, 142 that mesh with each other are fixed at the tip portions of these operating axle loads 131, 132 that protrude from the bearings, and are interlocked with each other in a non-linear relationship. The large gear 133 of the first operating shaft 131 meshes with a gear portion 13b formed on the primary self-aligning mechanism 13, and the large gear 140 of the second operating shaft is formed on the secondary self-aligning mechanism 13'. It meshes with the gear portion 13'b. Further, as shown in FIG. 3, a reduction gear mechanism 143 consisting of a large number of spur gears, etc. is engaged with the large gear 133 of the first operating shaft on the opposite side of the engagement with the gear portion.
The reduction gear mechanism 143 meshes with the output gear of the electric motor 29. Note that the electric motor 29 is an electromagnetic plate that can hold the motor at a predetermined position, similar to the electric motor in the operation section 50 described above. It has f145. Further, the single planetary gear mechanism 40 is disposed on a gear shaft 70a constituting a second shaft, and its ring gear 40R is connected to the flange portion 19' of the secondary shaft 3 of the belt type continuously variable transmission 1. ing. Also, the gear shaft 70a has a sprocket 8 integrated with the sun gear 409.
2 is rotatably supported, and a carrier 4 further rotatably supports a pinion 40P on the gear shaft 70a.
0C is fixed. On the other hand, a silent chain 8 is connected between the sprocket 82 integrated with the sun gear 403 on the second shaft and the sprocket 81 supported by the row one-way clutch F.
3 is wound around, and these sprockets and chains constitute a transfer equipment r1180. Further, the gear shaft 70a integrally constitutes the output member 70 with a gear 71a, and the gear 71a meshes with a gear 71c fixed to the intermediate shaft 72. Further, a small gear 71d is formed on the intermediate shaft 72, and the gear 71d meshes with a ring gear 75a fixed to the differential gear device 75, thereby forming the speed reduction device 71. Further, left and right front axle shafts 73 extend from the differential gear device 75. Further, the relationship between the flange portion 19 and the primary shaft 2 will be described in detail with reference to FIG. This male threaded portion 2b
A cylindrical fitting part 2c is formed on the front side, and a small-diameter fitting part 2d is formed on the rear side. Further, the male threaded portion 19 is provided on the inner peripheral surface of the flange portion 19.
b is formed, and a small diameter centering part 19c is formed on the rear side to be fitted into the fitting part 2d, and this centering part 1
A positioning portion 19d forming a stepped end surface is provided at the end of the centering portion 9c, and the tip of the centering portion 19C is formed into a thin cylinder 19e. Then, this thin cylinder 19e is connected to the notch 2.
It is bent to f. Next, the operation of this embodiment will be explained. The rotation of the engine crankshaft is transmitted to the input shaft 60 via the fluid coupling 101 when the vehicle is started, and thereafter via the centrifugal lock-up clutch 102 and the slip clutch 103. The rotation of the input shaft 60 is controlled by an actuator 51 for the forward/reverse switching device in the operation section 50.
By operating the forward clutch C1 or reverse brake B2 based on step a, the forward/reverse switching device 90 consisting of a dual planetary gear mechanism is switched, and forward rotation or reverse rotation is transmitted to the fixed side cam portion 9a of the pressure regulating cam mechanism 9. The operation of the high clutch C2 or the low coast reverse brake B1 based on the actuator 51b for the low/high speed mode switching device in the operating section 50 and the locking/overrun of the row one way clutch F result in a single planetary gear mechanism as described above. The low/high speed mode switching device 40 is set to low speed mode L or high speed mode H.
can be switched to The torque transmitted to the fixed side cam part 9 of the pressure regulating cam mechanism 9 is transmitted to the fixed sheave 5a of the primary pulley 5 via the roller and the movable side cam part 9b, and the axial force corresponding to the transmitted torque is transmitted to the fixed sheave 5a of the primary pulley 5. is applied to the fixed sheave 5a, and therefore an axial force corresponding to the transmitted torque is applied to the entire associated belt type continuously variable transmission 1 via the belt 7. Further, the torque of the fixed sheave 5a is transmitted to the movable sheave 5b via the ball spline 31, and the belt 7 is held by the axial force based on the pressure regulating cam machine jR9, and the torque of the fixed sheave 5a is transmitted to the secondary pulley 6 via the belt 7. transmitted to. On this occasion,
The axial reaction force from the belt 7 acts on the fixed sheave 5a and the movable sheave 5b, but the axial force from the fixed sheet 5a is carried by the flange portion 2a of the shaft via the pressure regulating cam mechanism 9, and the axial force is carried by the flange portion 2a of the shaft via the pressure regulating cam mechanism 9, and the axial force from the fixed sheave 5a The axial force is applied to the shaft 2 via the thrust ball bearing 12, the self-aligning mechanism 13, the ball screw device 10 in a predetermined state, the adjusting member 26, the thrust ball bearing 20, and the self-aligning mechanism 22.
The primary shaft 2 is supported by a flange portion 19 fixed to the primary shaft 2, thereby receiving the axial force in a closed loop that serves as the tensile stress of the primary shaft 2. In addition, the movable sheave 5b
A part of the axial force acting on the sheave is directly received by the shaft 2 via the spring means 15 and the support plate 17 from the back surface of the sheave. The axial force acting on the movable sheave 5b is received by the closed loop acting as a tensile stress on the primary shaft 2, and a part of the axial force acting on the movable sheave 5b is directly transmitted via the spring means 15. A thrust ball bearing 12 and a ball screw device 1 constitute the closed loop because they are received by the primary shaft 2.
0, the load acting on the thrust ball bearing 2o is reduced. The torque from the belt 7 is transmitted to the secondary pulley 6, and further transmitted to the secondary shaft 3 via the key k and the ball spline 31'. At this time, similarly to the primary side, on the secondary side, the axial reaction force acting on the fixed sheet 6a is carried directly by the shaft 3 by the nut 38, and the axial reaction force acting on the movable sheet 6b is carried by the thrust ball bearing 12. ', ball screw device a11, adjustment member 26' thrust ball bearing 2
0' and the flange portion 19'. Similarly, a portion of the axial force acting on the movable sheet 6b is directly received by the shaft 3 via the spring means 16 and the support plate 18 fixed to the shaft 2. Similarly to the primary side, the axial force acting on the movable sheave 5b is received by the closed loop, which acts as bow tension stress on the secondary shaft 3, and a part of the axial force acting on the movable sheave 6b is Since it is directly received by the secondary shaft 3 via the spring means 16, the load acting on the thrust ball bearing 12', the ball screw device 11, and the thrust ball bearing 20' that constitute the leap loop is reduced. Also, based on the speed change command from the control unit, the electric motor 29
When the first operation shaft 13 rotates, the first operating shaft 13
1, the large gear 133 rotates, and the gear 13
3 rotates the self-aligning mechanism 13 and the female screw portion 10b integrated therewith. Then, the female threaded portion 10b moves in the axial direction with respect to the male threaded portion 10a whose rotation is prevented by the adjustment member 26, and moves the movable sheave 5b via the thrust ball bearing 12.
Change the belt effective diameter of the primary pulley 5. on the other hand,
The rotation of the large gear 133 is caused by the rotation of the small gear 135 and the large gear 1.
37, the speed is significantly reduced and transmitted to the second operating shaft 132, and further via the non-circular gears 132, 131, the first operating shaft
The signal is transmitted to the operating shaft 131. Then, the first operating shaft 13
1 rotation is the large gear 136 and the small gear 139, and then the large gear 1
40, and the rotation of the large gear 140 is transmitted to the gear portion 13'b of the secondary self-aligning mechanism 13'. As the gear part 13'b rotates, the female threaded part 11b integrated therewith rotates relative to the fixed female threaded part 11a and moves in the axial direction, and the movable sheave is moved through the thrust ball bearing link 12'. 6b to change the belt effective diameter of the secondary pulley 6. At this time, although the amount of movement of the primary and secondary pulleys 5.6 and the amount of movement of the belt 7 do not correspond linearly, the non-circular gear 141
, 142, the difference in the amount of re-movement is appropriately absorbed. Furthermore, due to the structure, the non-circular gears 141, 142 are held within one rotation, but by providing the non-circular gears on the first and second operation shafts 131, 132 that are mutually decelerated, the non-circular gears 141, 142 can be rotated within one rotation. Although the rotation of the ball screw device 10.11 is suppressed to within one rotation, the gear portions 13b and 13'b on the primary and secondary sides are linked with accelerated rotation, enabling multiple rotations of the ball screw device 10.11. It is possible for the ball screw device to obtain a predetermined stroke with a predetermined lead. The rotation of the primary shaft 3 is controlled by the flange portion 1.
9' to the ring gear 40R of the single planetary gear mechanism 40, and as described above, the rotation is simply reduced by the planetary gear mechanism or combined with the rotation from the transfer 80 and transmitted to the gear shaft 70a. Further, the rotation of the gear shaft 70a is transmitted to the differential gear device 75 via the reduction gear device 71, and then to the left and right front axle shafts 73. Further, to explain the action of the flange portion 19 and the primary shaft 2 in detail with reference to FIG. 1, the belt 7 is wound only around the upper part of the primary pulley 5, and a strong clamping force of the belt 7 is applied to this part. Due to
It is digested by stepping on the centering parts 19b and 19c,
No moment is applied to the male threaded portion 2b and the female threaded portion 19a. Further, the moment applied to the flange portion 19 via the aforementioned thrust bearing 20 is also alleviated by the self-aligning mechanism 22, and uneven contact of the thrust bearing 20 is prevented. Further, since the female screw 19a and the male screw 2b are formed to have a large diameter so as to have approximately the same diameter as the primary shaft 2, the burden on the threaded portion of the axial force is reduced.Furthermore, By crimping the thin cylindrical portion 19e of the flange portion 19 into the cutout portion 2f of the primary shaft 2, the flange portion 19 and the primary shaft 2 are surely prevented from loosening.The above-mentioned embodiment is a belt type continuously variable transmission ff. 1 was applied to an automatic transmission A that switches between a low-speed mode and a high-speed mode in combination with a single planetary gear mechanism 40, but other automatic transmissions such as an automatic transmission that combines a torque converter and a belt-type continuously variable transmission have been described. It goes without saying that the invention may be applied to automatic transmissions of this type. Also, although ball bearings are used as the thrust bearings, it is equally applicable to roller bearings. (G) Detailed Description of the Invention According to the present invention, the flange portion (
19) is the moment applied to the fitting parts (2c), (2d) on both sides of the male threaded part (2b) and the female threaded part (19a).
) on both sides of the centering parts (19b) and (19c), and the male threaded part (2b) and the female threaded part (
No moment is applied to 19a), and the male threaded portion (2
b) and the diameter of the female thread part (19a) is the same as that of the shaft (3).
The male threaded portion (2b
) and the female threaded portion (19a), the male threaded portion (2b) and the female threaded portion (], 9 a
) can be prevented from loosening. Further, the automatic alignment mechanism (22) is connected to the flange portion (19).
Since it is interposed between the thrust bearing (20) and the mechanical actuator (10), uneven contact of the thrust bearing (20) can be prevented and the life of the thrust bearing (20) can be extended.

[Brief explanation of the drawing]

Fig. 1 is an enlarged sectional view of the flange portion of the belt type continuously variable transmission according to the present invention, Fig. 2 is an exploded sectional view showing the belt type continuously variable transmission, and Fig. 3 shows the movable sheave portion on the primary side thereof. It is an enlarged sectional view. FIG. 4 is an overall sectional view showing an automatic transmission to which the belt-type continuously variable transmission is applied, FIG. 5 is a schematic diagram of the automatic transmission, and FIG. 6 shows the operation of each element at each position. FIG. DESCRIPTION OF SYMBOLS 1... Belt type continuously variable transmission, 2... (Primary) shaft, 2b... Male screw part 2c, 2d
...Fitting part, 2e...Shoulder part 20.19d...
Positioning part, 3... (secondary) shaft,
5... (Primary) pulley, 5a... Fixed sheave, 5b, 6b... Movable sheave, 6.
...(Secondary) pulley 10...Mechanical actuator, 19...Flange part, 19a...
・Female screw part, 9b, 9C...centering part, 20
...Thrust bearing, 22...Self-aligning mechanism Fig. 1 0a Fig. 3 Fig. 5

Claims (1)

[Claims] 1. A primary pulley and a secondary pulley each consisting of two sheaves supported by a shaft and capable of relative movement in the axial direction, a belt wound around these two pulleys, and a movable sheave of these two pulleys. a mechanical actuator that moves the pulley in the axial direction, and in which the axial force from the pulley is supported by the shaft; , a male threaded portion having approximately the same diameter as the shaft is formed, and fitting portions are formed on both sides of the male threaded portion in the axial direction; A belt-type belt-type belt type belt type belt type belt type belt type belt type belt type belt type belt type belt type belt type belt type belt type belt type belt type belt type device, in which a female screw portion that is screwed into the male screw portion and a centering portion that is located on both sides of the female screw portion in the axial direction and that fits into the fitting portion are formed on the supporting flange portion; Continuously variable transmission. 2. The fitting part on the rear end side of the shaft is made small in diameter to form a shoulder, and the centering part of the rear end steel of the flange part is made small in diameter to form an axial positioning part that comes into contact with the shoulder. The belt-type continuously variable transmission according to claim 1. 3. A thrust bearing that carries an axial force from the movable sheave acting through the mechanical actuator is supported on the flange portion, and a self-aligning mechanism is interposed between the thrust bearing and the flange portion. The belt type continuously variable transmission device according to claim 1, wherein the belt type continuously variable transmission device is equipped with a belt type continuously variable transmission device.