JPH038420B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a general-purpose continuously variable transmission device suitable for equipping industrial machinery, conveyance equipment, and the like.

(Prior Art) Stepped transmissions have problems in that shocks occur during stepwise shifting, and optimum output rotation cannot always be obtained.

Continuously variable transmissions are intended to solve these problems, but many conventional mechanical continuously variable transmissions include friction wheel type continuously variable transmissions. One example is the one disclosed in Japanese Utility Model Publication No. 49-29168.

(Problems to be Solved by the Invention) The conventional friction wheel type continuously variable transmission described above performs continuously variable speed transmission mainly by steplessly changing the rotation radius of the friction transmission contacts of the conical wheel. It is something. However, in the friction transmission contact of a conical wheel, the contact trajectory corresponding to the pitch line becomes band-shaped due to Hertzian stress, so there is a positive slip on one side and a negative slip on the other on the large diameter side and the small diameter side on the contact trajectory. As a result, there is a problem in that this results in internal friction loss and reduces transmission efficiency. Furthermore, when the gear ratio is at its highest or lowest, the ratio of the pitch line diameter of the friction transmission contact to the driving friction wheel and the driven friction wheel becomes large, such as 1:2 to 1:4, so that the positive and negative slip mentioned above increases. rapidly increasing,
There was a problem in that the transmission efficiency was significantly reduced during so-called top and low transmission.

In order to solve the above-mentioned problems, the present inventors first provided a rotatable drive friction wheel whose eccentricity can be freely adjusted with respect to the input shaft, and attached an internal gear concentric with the drive friction wheel to the drive friction wheel. two internal gears that are integrally formed with the input shaft and that are concentric with the input shaft; one of the internal gears and the internal gear that is integral with the drive friction wheel are interposed between the two internal gears that are concentric with the input shaft; A hollow cylindrical driven rotary body is meshed and connected via a transmission gear and rotatable around the input shaft, and a driven friction wheel is provided on the inner periphery of the driven rotary body to rotate together with the driven rotary body. The driven friction wheel and the driving friction wheel are press-fitted together, a planetary carrier is integrally provided on the driven rotating body, and the planetary gear pivotally supported on the planetary carrier is connected to the other internal gear integral with the input shaft. He invented a continuously variable transmission (Japanese Patent Application No. 61-272921) in which the output shaft, which is concentric with the input shaft, is meshed with an integral sun gear.

However, since this device transmits power by pressing the driving friction wheel and the driven friction wheel into contact with each other by spring force, there is a problem in that slips tend to occur when the load becomes large.

(Means for Solving the Problems) In order to solve the above-mentioned problems, the present invention provides a friction wheel type continuously variable transmission in which a driving friction wheel and a driven friction wheel are eccentrically pressed into contact with each other to transmit power. In this method, a driving friction ring is spline-fitted to the outer periphery of a driving friction wheel, a movable driven rotating body is rotatably provided on the inner periphery of a hollow cylindrical driven rotating body, and each of the driven rotating body and the movable driven rotating body is A driven friction wheel sandwiching the driving friction ring is provided, and a cylindrical end face cam is provided on the inner periphery of the driven rotating body to rotate together with the driven rotating body and apply a thrust to the movable driven rotating body, and a cylindrical end face cam is provided on the opposing cam surface. A continuously variable transmission is constituted by providing teeth respectively, and interposing a freely rotatable gear between these tooth rows, and pressing the driven friction wheel against the driving friction ring by the action of the cam. .

(Function) As described above, in the present invention, the driving friction ring spline-fitted with the driving friction wheel is clamped by the driven friction wheels provided on the driven rotating body and the movable driven rotating body, respectively. When a slip occurs between the driven friction ring and the driven friction ring, a rotational phase difference occurs between the driven rotary body and the movable driven rotary body, so that by using a cylindrical end cam, the driven friction wheel is moved against the driven friction ring. The pressure will be stronger than before.

That is, this cylindrical end surface cam acts as a boosting mechanism that increases the pressing force between the friction wheels when slip occurs between the friction wheels.

In particular, in the present invention, teeth are provided on each of the opposing cam surfaces of the cylindrical end cam, and a rotatable gear is interposed between these tooth rows, so that the differential movement between the two opposing cam surfaces is not a slip. , it operates reliably through the meshing of the tooth row and gears. Therefore, the device of the present invention can reduce the resistance associated with the action of the cylindrical end cam and ensure reliable operation.

Therefore, according to the present invention, even if the load increases and slip occurs, the pressure contact force between the friction wheels increases correspondingly to the slip, thereby significantly reducing the occurrence of slip due to increase in load. , transmission efficiency can be increased.

(Example) Hereinafter, an example of the present invention will be described with reference to FIGS. 1 to 8.

In the figure, 1 is a hollow cylindrical case body, 2 is a base formed integrally with the case body 1, 3 is an input side case lid connected to the input side of the case body 1 with a bolt 4, and 5 is the output side of the case body 1. 7 is the oil cap provided on the top of the case body 1, and 8 is the case body 1.
This is an oil drain plug installed at the bottom of the tank.

In this embodiment, an output shaft 9 passing through the boss portion 5a of the output case lid 5 is rotatably provided via bearings 10 and 11, and a circular recess 9a is provided at the inner end of the output shaft 9. At the same time, a sun gear 12 is integrally formed with the output shaft 9 on its outer periphery. 13
is a bearing retainer attached to the outside of the boss portion 5a with bolts 14.

An input shaft 15 coaxial with the output shaft 9 passes through the input case lid 3, and its inner end is rotatably inserted into the circular concave portion 9a of the output shaft 9 via a bearing 16. 17 is a bearing provided at the part where the input shaft 15 passes through the case lid 3; 18 is a bolt 19;
20 is a bearing holder attached to the case lid 3.

In addition, two internal gears 21 concentric with the input shaft 15,
22 are connected back to back with a bolt 23, and this combined body is connected with a bolt 24 and a key 2.
It is fixed to the input shaft 15 via 5.

Further, as shown in FIGS. 4 and 5, an inner eccentric cam 26 eccentric by l ₁ with respect to the center O ₁ of the input shaft 15 is rotatably fitted to the input shaft 15, and the outer end thereof The part is fitted into the case lid 3 as shown in FIG. 28 is a bearing interposed between the input shaft 15 and the inner eccentric cam 26.

Further, as shown in FIGS. 4 and 5, an outer eccentric cam 29 eccentric by l ₂ with respect to the center O ₂ of the inner eccentric cam 26 is rotatably fitted to the inner eccentric cam 26. In this case, l ₁ =l ₂ .

In addition, a hollow cylindrical portion 2 is provided on the input side of the outer eccentric cam 29.
A worm wheel 30 having the inner eccentric cam 26 as a central axis is fixedly provided with a bolt 31 on the input side end surface of the hollow cylindrical portion 29a, and a worm 32 that meshes with the worm wheel 30 is integrally formed with the worm wheel 30. A shaft 32a is provided rotatably with respect to the case lid 3 as shown in FIG. 33 is a bush, 34 is a cylindrical set screw, and 35 is a shaft 3.
This is a handle fixed to 2a.

Further, a hollow cylindrical drive rotor 36 is rotatably provided on the outer periphery of the outer eccentric cam 29 via a bearing 37, and a drive friction wheel 38 is integrated with the drive rotor 36 at the input side end of the drive rotor 36. In addition to providing
A spline 38a is provided on the outer periphery of the drive friction wheel 38, and a ring-shaped drive friction ring 39 having a spline 39a on the inner periphery that fits with the spline 38a is spline-fitted to the outer periphery of the drive friction wheel 38. Further, an internal gear 40 similar to the internal gear 22 is provided on the output side end face of the drive rotary body 36 and fixed with a bolt 41 so as to be concentric with the drive rotary body 36 . Note that 42 is a bearing holding plate fixed to the output side end face of the outer eccentric cam 29 with bolts 43.

Furthermore, as shown in FIGS. 1 and 3, even when the outer eccentric cam 29 rotates around the inner eccentric cam 26, the band meshes with the internal gear 40 and the intermediate gear that also meshes with the internal gear 22. The transmission gear 44 is connected to the bearing 45
It is rotatably provided on the inner eccentric cam 26 via.
46 is washer and 47 is color.

Further, a slave rotating body 48, in which a hollow cylindrical body 48a, an input side flange 48b, and an output side flange 48c are integrally connected by bolts 49, is arranged around the input shaft 15 and the output shaft 9. A hollow cylindrical ball race 52 is fitted to the input side inner periphery of the body 48a of the driven rotating body 48, and the body 48a is rotatably provided in the case body 1 via bearings 50, 51. A hollow cylindrical ball race 53 is fitted onto the inner periphery of the output side. The ball race 52 and the input side flange portion 48b
A driven friction wheel 54 on one side, which is connected to the shoulder of the drive friction ring 39, is fixed by a bolt 55 at the corner of the drive friction ring 39.

Further, a movable driven rotary body 57 having a hollow cylindrical shape has another driven friction wheel 56 provided opposite to this driven friction wheel 54 rotatably provided within the driven rotary body 48.
The driven friction wheels 54 and 56 are integrally connected with the driving friction ring 39 and are provided to sandwich the driving friction ring 39.
58 is a ring-shaped connecting plate that connects the driven friction wheel 56 and the movable driven rotating body 57, and 59 is a bolt.

The bearing 60 that rotatably supports the combined body of the driven friction wheel 56 and the movable driven rotating body 57 with respect to the driven rotating body 48 is provided between the ball race 52 and the driven friction wheel 56, and between the ball race 53 and the driven friction wheel 56. It is provided between the inner race 61 provided at the output end of the movable driven rotor 57.

That is, 62 is a ball of the bearing 60, 63 is a retainer placed on both sides of the ball 62, and 64 is an elastic ring provided outside the retainer 63.

Further, a cylindrical end face cam 65 is provided at a corner of the body portion 48a of the driven rotary body 48 and the output side flange portion 48c so as to rotate together with the driven rotary body 48. 6
6 is an elastic plate inserted between the base of the cylindrical end cam 65 and the output side flange 48c, and 67 is an elastic plate inserted between the holes provided at multiple locations in the base of the cylindrical end cam 65 and the output side flange 48c. The interposed coil spring 65a is located at the base of the cylindrical end cam 65,
The notched groove 68 provided in the axial direction is a torque transmission pin that penetrates the driven rotating body 48 and fits into the notched groove 65a.

Reference numeral 69 denotes a cylindrical end cam fixed to the movable driven rotating body 57 with a bolt 70, facing the cylindrical end cam 65.
The cylindrical end surfaces, which are the cam surfaces of Nos. 5 and 69, are formed into a continuous mountain shape as shown in FIGS.
b, 69b are provided. and each annular groove 6
The inner edges of 5b and 69b have teeth 6 that mesh with the gears.
5c and 69c are formed, respectively, and cam surfaces 65d and 69d that come into rolling contact with the rollers are formed on the outer edges of each of the annular grooves 65b and 69b, respectively.

A band-shaped ring 71 whose side edges fit into the annular grooves 65b and 69b, respectively, is rotatably provided between the cylindrical end cams 65 and 69.
The shaft 72 is placed at three equal positions on the circumference of the ring 71.
A gear 73 that meshes with the teeth 65c, 69c is rotatably fitted into the inner protrusion of the shaft 72, and a roller is connected to the outer protrusion of the shaft 72 with the cam surfaces 65d, 69d. 74 is rotatably fitted.

Further, as shown in FIGS. 1 and 6, a planetary carrier 75 is fixed to the inside of the output side flange portion 48c of the driven rotor 48 with bolts 76, and a plurality of planetary carriers (in this embodiment, three ) are rotatably provided by a shaft 78 and a bearing 79, and these planetary gears 77 are internally meshed with the internal gear 21 and externally meshed with the sun gear 12, which is integrated with the output shaft 9. Note that 80 indicates the boss portion of the internal gear 21 and the planetary carrier 75.
This is a bearing installed between the

Next, the operation of the apparatus of the present invention constructed as described above will be explained. In FIG. 2, when the handle 35 is rotated, the worm 32 and the worm wheel 30 are rotated.
Since the outer eccentric cam 29 rotates with respect to the inner eccentric cam 26 fixed to the case lid 3 via
The amount of eccentricity can be freely changed. 1 and 4 show the case where the amount of eccentricity of the outer eccentric cam 29 with respect to the input shaft 15 is zero, and in this state, the driving friction wheel 38 and the driving friction ring 39 are concentric with the driven friction wheels 54 and 56. Therefore, the driving friction ring 39 and the driven friction wheels 54, 56 are in contact with each other around the entire circumference, and since the driven friction wheel 56 presses the driving friction ring 39 against the driven friction wheel 54 by the action of the coil spring 67, the driving friction is reduced. When the wheel 38 rotates, the driven friction wheels 54 and 56 also rotate together with almost no slippage.

However, the load increases and the drive friction ring 3
9 and the driven friction wheel 54, the other driven friction wheel 56 is rotatable relative to the driven rotating body 48, so even if slipping occurs between the driving friction ring 39 and the driven friction wheel 54, Even if this happens, the other driven friction wheel 56 tries to rotate together with the driving friction ring 39.

For this reason, the cylindrical end face cam 65 which is integrally connected to one driven friction wheel 54 and the other driven friction wheel 5
6 and the cylindrical edge cam 69 which is integrally connected thereto, a rotational phase difference occurs.

In other words, when there is no slippage between the driving wheel and the driven wheel, the cylindrical end cams 65 and 69 rotate at the same time, but when there is slipping between the driving wheel and the driven wheel, as shown in FIG. As shown, the cam 65 rotates at a slightly slower speed, eg, arrow A, due to slippage, whereas the cam 69 rotates at a faster speed, arrow B, without slippage. Therefore, a rotational phase difference occurs between the cams 65 and 69, and a thrust force is applied to the cam 69 in the direction of arrow C by the action of the resulting slope of the cam.

This thrust becomes a clamping force for the drive friction ring 39 by the driven friction wheels 54 and 56, so according to the present invention, when slippage occurs in the friction transmission section, the contact force of the friction transmission section is further increased to eliminate slippage. It acts on

In the case of this embodiment, the cylindrical end cams 65 and 69
When differential movement occurs, the roller 74 supported by the shaft 72 engages the cam surfaces 65d, 69 via the shaft 72 of the gear 73 that meshes with the teeth 65c, 69c, respectively.
Correctly roll and make contact with d. Therefore, with this device, the action of the cam can be reliably transmitted through rolling contact that is smaller than the sliding resistance.

Further, as mentioned above, the outer eccentric cam 29 is connected to the input shaft 1.
5, when the input shaft 15 rotates in the direction of arrow D in FIG. 4, the internal gears 21 and 22 integral with the input shaft 15 rotate in the direction of arrow E in FIG. an intermediate transmission gear 44 that meshes with the gear 22;
Through the internal gear 40 that meshes with the intermediate transmission gear 44, the drive friction wheel 38 integrally connected to the internal gear 40 also rotates integrally with the input shaft 15 in the direction of arrow F in FIG. do. As described above, when the driving friction wheel 38 rotates, the driving friction ring 39 also rotates via the splines 38a and 39a, so that the driven friction wheels 54 and 56 also move toward the input shaft in the direction of the arrow G in FIG. It rotates integrally with 15. Furthermore, when the driven friction wheels 54 and 56 rotate, the driven rotary body 48 integrally connected to the driven friction wheel 54 also rotates together with the input shaft 15. Therefore, each planetary gear 77 also has an internal gear 21 connected to the input shaft 1.
Since it rotates integrally with the input shaft 15, it revolves integrally with the input shaft 15. As a result, as shown in Figure 6,
The sun gear 12 meshing with these planetary gears 77 also rotates together with the output shaft 9 and the input shaft 15 . That is, in this case, the rotation ratio of the input shaft 15 to the output shaft 9 is 1:1. This state is the so-called top shift state of the continuously variable transmission.

Next, when the outer eccentric cam 29 is rotated approximately 180 degrees by operating the handle 35 shown in FIG. 2 from this top gear shifting state, the outer eccentric cam 29 will be in the maximum eccentric state shown in FIGS. 3 and 5. Accordingly, the driving friction wheel 38 and the driving friction ring 39 are also eccentric with respect to the driven friction wheels 54 and 56, as shown in FIGS. 3 and 5. Therefore, the driving friction ring 39 and the driven friction wheel 5
The contact portion with 4 and 56 is only near point H shown in FIGS. 3 and 5. In this state, when the driving friction ring 39 rotates in the direction of arrow I in FIG. 5 via the input shaft 15, the driven friction wheels 54, 54 also rotate in the direction of arrow J, but in this case, the friction A difference occurs in the radius of rotation up to the transmission point H. That is, the fifth
In the figure, the center of the input shaft 15 and the driven friction wheel 56 is O ₁ , the center of the drive friction ring 39 is O ₃ , the radius from O ₃ to point H is R ₁ , and from O ₁ to H
If the radius to the point is R ₂ , then R ₁ <R ₂ . Therefore, in this case, the driven friction wheels 54 and 56 rotate at a reduced speed with respect to the driving friction ring 39. In this embodiment, the reduction ratio is approximately 1:0.67. In other words, for 1 rotation of the input shaft 15
This results in a deceleration of 0.33.

Then, when the driven friction wheels 54 and 56 decelerate and rotate, the driven rotary body 4
A planetary carrier 75, which is integral with 8, rotates at a reduced speed in the direction of arrow K in FIG. On the other hand, since the internal gear 21 on the outside of the planetary carrier 75 is fixed to the input shaft 15 via the key 25, it rotates in the same direction at a faster speed than the planetary carrier 75, as shown by arrow E in FIG. . Therefore, each planetary gear 77 revolves as shown by arrow K in FIG.
Since the sun gear 12 that meshes with these planetary gears 77 is further decelerated. That is, this planetary gear system further amplifies the deceleration of the driven friction wheels 54, 56. Since the amplification factor in this embodiment is approximately 3, the rotation of the output shaft 9 in the lowest speed change state (low) is 3 times the deceleration rate of 0.33 of the friction transmission section, that is, -0.33×3
≒-1, and since 1-1=0, it becomes approximately zero.

If the operating amount of the handle 35 in FIG. 2 is set to an arbitrary operating amount between the above-mentioned top and low, a stepless gear ratio can be obtained from low to top.

If necessary, this device can also rotate the output shaft in the opposite direction with respect to the input shaft by increasing the deceleration rate or amplification factor described above.

(Effects of the Invention) As described above, the device of the present invention does not use a conical wheel for friction transmission, but instead uses a driving friction ring 39 whose eccentricity can be freely adjusted with respect to the input shaft 15, and a driven friction ring 39 that rotates together with the driven rotating body 48. The dynamic friction wheels 54 and 56 are brought into direct contact through press-fit engagement, and the driving friction ring 39 and the driven friction wheels 54 and 56 are concentrically connected, especially in the top gear shifting state, so in this case. Drive friction ring 39 and driven friction wheel 5
4 and 56 are pressure-welded around the entire circumference, and as a result, extremely high transmission efficiency of nearly 100% with no slippage can be obtained.

Furthermore, even if the driving friction ring 39 is eccentric with respect to the driven friction wheels 54 and 56 and the speed change state is other than the top where both friction wheels are partially connected, the ratio of the pitch line diameters of the friction transmission contacts H of both friction wheels are closer than 1:2, so the friction transmission contact line is formed quite long on the pitch line, and the positive and negative slip zones on both sides of the pitch line are also narrower than in the conventional one. Considerably high transmission efficiency can be obtained in other speed ranges.

Further, in the present invention, the driving friction ring 39 spline-fitted to the driving friction wheel 38 is clamped by the driven friction wheels 54 and 56 provided on the driven rotary body 48 and the movable driven rotary body 57, respectively. When a slip occurs between the driven friction ring 54, 56 and the drive friction ring 39, a rotational phase difference occurs between the driven rotary body 48 and the movable driven rotary body 57.
As a result, due to the action of the cylindrical end cams 65 and 69, the driven friction wheels 54 and 56 are moved toward the drive friction ring 39.
The pressure will be stronger than before.

That is, the cylindrical end cams 65, 69 act as a boosting mechanism that increases the pressing force between the friction wheels when slip occurs between the friction wheels.

Particularly in the present invention, the cylindrical end cams 65, 6
Teeth 65c, 69c are provided on opposing cam surfaces of 9, respectively.
In addition, since the rotatable gear 73 is interposed between these tooth rows, the differential motion between the two opposing cams is not caused by slippage, but is reliably operated by meshing between the tooth row and the gear. Therefore, the device of the present invention can reduce the resistance associated with the action of the cylindrical end cams 65 and 69, and can ensure reliable operation.

Therefore, according to the present invention, even if the load increases and slip occurs, the pressure contact force between the friction wheels increases correspondingly to the slip, thereby significantly reducing the occurrence of slip due to increase in load. , the effect of increasing transmission efficiency can be obtained.

[Brief explanation of the drawing]

Fig. 1 is a vertical sectional side view of the device of the present invention, Fig. 2 is a front view of the device as seen from the input side, a part of which is shown in the - cross section of Fig. 1, and Fig. 3 is a state in which the eccentric cam shown in Fig. 1 is eccentric. FIG. 4 is a cross-sectional view of FIG. 1, FIG. 5 is a cross-sectional view of FIG. 3,
6 is a cross-sectional view taken from FIG. 1, FIG. 7 is a perspective view of the cylindrical end face cam portion, and FIG. 8 is an explanatory diagram of its operation. DESCRIPTION OF SYMBOLS 1... Case body, 2... Base, 3... Input side case lid, 5... Output side case lid, 9... Output shaft, 12... Sun gear, 15... Input shaft, 21,
22... Internal gear, 26... Inner eccentric cam, 29
...Outside eccentric cam, 30...Worm wheel,
32...Worm, 35...Handle, 36...
Drive rotating body, 38... Drive friction wheel, 39... Drive friction ring, 40... Internal gear, 44... Intermediate transmission gear, 48... Driven rotating body, 54, 56... Driven friction wheel, 57... ...Movable driven rotating body, 65, 69
...Cylindrical end cam, 65c, 69c...Teeth, 73
...gear, 75...planetary carrier, 77...planetary gear.

Claims (1)

[Claims] 1. In a friction wheel type continuously variable transmission in which a driving friction wheel and a driven friction wheel are eccentrically pressed into contact with each other for transmission, a driving friction ring is spline-fitted to the outer periphery of the driving friction wheel, and a hollow cylindrical A movable driven rotary body is rotatably provided on the inner periphery of the driven rotary body, a driven friction wheel that sandwiches the drive friction ring is provided on the driven rotary body and the movable driven rotary body, respectively, and this driven friction wheel is provided on the inner periphery of the driven rotary body. A cylindrical end face cam is provided which rotates together with the driven rotating body to apply thrust to the movable driven rotating body, teeth are provided on each of the opposing cam surfaces, and a rotatable gear is interposed between these tooth rows. A continuously variable transmission characterized in that the driven friction wheel is brought into pressure contact with the driving friction ring by the action of a cam.