JPS63285359A - Non-step speed change gear - Google Patents

Abstract

PURPOSE:To provide the extremely high efficiency of slipless transmission by adjusting eccentrically a driven friction wheel in pressure contact with a drive friction wheel rotating together with an input shaft respectively to an output shaft to interconnect directly both friction wheels through wedge engagement. CONSTITUTION:When an eccentric cam 12 is pivoted by a lever 16 to align a drive friction wheel 67 with a driven friction wheel 19, both wheels contact each other on the whole peripheries and integrally rotate by a coiled spring 66 with the wedge action of disks 62, 65b causing few slippage. Under such condition, the rotation of an input shaft 30 rotates a planet carrier 29 and a drive rotor 48 and further a driven rotor 18 and a gear 22 through a key 60, shaft tube 61, ring 63 key 64, shaft tube 65 and both friction wheels 67, 19. Also a transmission gear 32 is rotated through an internal transmission gear 26, each planet gear 56 rotates approximately integrally with the input shaft 30 so that the rotational speed ratio of output shaft 41 is 1:1 representing the low condition. Next, when the lever 16 is pivoted in the reverse direction, the output shaft 41 is rotated with aceleration. Thus, extremely high transmission efficiency can be obtained.

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.

- For example, there is 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 continuously changing the rotation radius of the friction transmission contacts of the conical wheel. be.

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 one side of the contact trajectory has a positive slip and the other has a negative slip on the large diameter side and the small diameter side. As a result, there is a problem in that this causes internal friction loss and reduces transmission efficiency. Furthermore, when the gear ratio is the 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 above-mentioned positive and negative slips occur. However, there was a problem in that the transmission efficiency was significantly reduced during so-called top and low transmission.

(Means for Solving the Problems) In order to solve the above-mentioned problems, in the present invention, the planetary carrier formed integrally with the human power shaft is integrally coupled with the drive rotating body, and the planetary carrier is integrally formed with the human power shaft. A driven rotating body whose eccentricity can be freely adjusted with respect to the provided output shaft is provided, and a driving friction wheel is configured to rotate integrally with the driving rotating body, and a driven rotating body is configured to rotate integrally with the driven rotating body. The external gear integrally formed on the driven rotating body is meshed with an internal transmission gear rotatably provided with respect to the case. A planetary gear pivotally supported on the planetary carrier is meshed with an internal gear of a transmission gear which is meshed through a gear, and the planetary gear is meshed with a sun gear formed integrally with the output shaft. This constitutes a continuously variable transmission.

(Function) As described above, the device of the present invention does not use a conical wheel for friction transmission, but instead uses a driven friction wheel that presses into engagement with a driving friction wheel that rotates together with the input shaft and connects it to the output shaft, which is concentric with the input shaft. The eccentricity of the drive friction wheel and the driven friction wheel can be adjusted freely, and the driving friction wheel and the driven friction wheel are brought into direct contact through mock engagement, so that the driving friction wheel and the driven friction wheel are concentrically connected, especially in the low gear shifting state. Therefore, in this case, both friction wheels are pressure-welded around the entire circumference, and as a result, extremely high transmission efficiency of nearly 10 oz without slippage can be obtained.

Furthermore, even if the driving friction wheel is eccentric with respect to the driven friction wheel and the two friction wheels are in a shifting state other than low where they are partially connected, the ratio of the pitch line diameters of the friction transmission contacts of both friction wheels is 1:
2, the friction transmission contact line is formed considerably longer 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, resulting in a low Considerably high transmission efficiency can be obtained even in other speed ranges.

(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 this 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 an output of the case body 1. A hollow cylindrical output side case is connected to the side by a bolt 6, 7 is an output side case lid connected to the output side case 5 by a bolt 8, and 9 is a boss portion 7 of this case lid 7.
A is a bearing housing connected by a bolt 10, and 11 is an oil cap screwed onto the input side case lid 3.

In this embodiment, as shown in FIG. 1.6.7, the outer circumferential surface 12a is formed in a cylindrical shape, and the inner circumferential surface 12b, which is also cylindrical, is stepped with eccentricity with respect to the outer circumferential surface 12a. A hollow cylindrical eccentric cam 12 is integrally formed. 12c (
1) is a stepped cylindrical portion of the eccentric cam 12, and this cylindrical portion 12c is formed concentrically with the inner peripheral surface 12b of the eccentric cam 12.

This eccentric cam 12 is connected to the case body 1 and the output side case 5.
A long hole 5a (
The lever 16 inserted from the outside via the lever (see FIG. 1) is screwed onto the eccentric cam 12, and the lever 16 is connected to the
, as shown in B, so that it can be rotated approximately 90 degrees.

17 is the case 5 and the eccentric cam 1 on both sides of the elongated hole 5a.
This is an O-ring provided to seal the gap between the case and the case to prevent the lubricating oil from leaking out.

Further, reference numeral 18 denotes a driven rotary body formed in a stepped hollow cylindrical shape so that it can be rotatably fitted into the eccentric cam 12.The driven rotary body 18 has a hollow cylindrical shape in the middle part on its inner periphery as shown in FIG. A driven friction wheel 19 having a ring-like cross-sectional shape is integrally formed. 20 and 21 are bearings for rotatably supporting the driven rotating body 18 with respect to the eccentric cam 12.

Further, 22 is a ring-shaped gear integrally connected to the input side of the driven rotating body 18 by a screw 23, 24 is a collar ring, and 25 is a snap ring.

Reference numeral 26 denotes a ring-shaped internal tooth transmission gear, which is rotatably provided in the case body 1 via a bearing 27. As shown in FIG. 4.5, even when the eccentric cam 12 rotates, the gear 26
are formed so that they interlock internally. 28 is coloring.

Further, an input shaft 30 integrally formed with a disk-shaped planetary carrier 29 is rotatably provided in the boss portion a of the input side case lid 3 via a bearing 31, and a ring-shaped transmission shaft is provided on the outer periphery of the planetary carrier 29. A gear 32 is rotatably provided via a bearing 33. The transmission gear 32 is provided with an external gear 32a having the same diameter as the gear 22, and is also integrally formed with an internal gear 32b, so that the external gear 32a is internally meshed with the internal transmission gear 26. 34 and 35 are coloring,
36: 37, 38, 39 are snap rings, 4
0 is an oil seal.

Further, one end 41a of an output shaft 41 which is coaxial with the input shaft 30 is supported via a bearing 42 in a hole 30a provided at the opposite end of the input shaft 30, and the other end of this output shaft 41 is mounted on the output side case. It penetrates the boss portion 7a of the lid 7 and the bearing housing 9 and is rotatably supported via a bearing 43. 4
4 and 45 are snap rings, and 46 is an oil seal. Further, a sun gear 47 is integrally formed at the input end of the output shaft 41.

In addition, a hollow cylindrical drive rotating body 48 is connected to the output shaft 4 in the case.
1 through bearings 49 and 50 so as to be freely rotatable.

51 is a bearing housing fixed to the output side of the drive rotary body 48 with a screw, 52 is a snap ring, 53 is a collar ring, and 54 is a collar ring provided on the bearing 49 side.

A flange portion 48a is formed on the input side of the drive rotary body 48, and a plurality of (four in this embodiment) bolts 55 are provided to span between the flange portion 48a and the planetary carrier 29. A planetary gear 56 is provided with each bolt 55 as a shaft, and each planetary gear 56 meshes with the internal gear 32b and also meshes with the sun gear 47. Furthermore, 57
is a disc ring inserted on the input side of the flange 48a,
58 is a bearing roller of each planetary gear 56, and 59 is a washer provided on both sides of this bearing roller 5B.

Further, a sliding key 60 is provided on the outer periphery of the driving rotary body 48, and a shaft cylinder 61 that is slidable on the key 60 and the driving rotary body 48 is provided.
is fitted into the driving rotary body 48, and a disk 62 integral with the shaft cylinder 61 is provided on the input side of the driven friction wheel 19. Further, a ring 63 is screwed and fixed to the outer periphery of the output side end of the shaft cylinder 61, and a sliding key 64 is provided on the outer periphery of this ring 63, and a stepped shaft cylinder that can freely slide on the key 64 and the shaft cylinder 61. 65 is fitted onto the outer periphery of the shaft cylinder 61 and the ring 63,
A coil spring 66 is inserted between the input side end plate 65a of the shaft cylinder 65 and the ring 63, and a disc 65b integral with the shaft cylinder 65 is provided on the output side of the driven friction wheel 19.
5b and the disk 62 constitute a driving friction wheel 67 that constantly presses the driven friction wheel 19 by the action of the coil spring 66.

FIG. 9 shows a modified example of the present invention, and the same reference numerals as in the embodiment described above indicate equivalent parts.

In FIG. 9(a), the driving friction wheel and the driven friction wheel are reversed from those of the previous embodiment.

That is, in this case, a disk-shaped drive friction wheel 67 with both sides formed into conical surfaces is formed integrally with the drive rotary body 48,
The driven friction wheel 19 is made up of two rings that are slidably provided in the axial direction of the output shaft 41 on the inner circumference of the hollow cylindrical driven rotating body 18 that encloses the driving friction wheel 67. The drive friction wheel 67 is configured to be compressed by the drive friction wheel 67. 68 is a coil spring for pressing the driven ring against the driving friction wheel 67.

FIG. 9(b) shows that the driving friction wheel 67 is formed into a V-pulley shape, and the two ring members 19a constituting the driven friction wheel 19 are attached to the inner surface of the groove of the V-pulley-shaped driving friction wheel 67. It is designed so that it comes into pressure contact with the 69 is a coil spring inserted between these two ring members 19a.

Further, FIG. 9(C) has a configuration opposite to that shown in FIG. 9 (with). That is, the driven friction wheel 19 is formed into a pulley shape, and the driving friction wheel 67 is constituted by two ring members 67a that are slidable in the axial direction with respect to the driving rotating body 48. The coil spring 70 is pressed against the inner surface of the groove of the driven friction wheel 19.

In FIG. 10, in contrast to the embodiments shown in FIGS. 1 to 9, in which the eccentricity of the driven friction wheel 19 with respect to the output shaft 41 can be freely adjusted, the drive friction wheel 67 is connected to the output shaft 41. The amount of eccentricity can be adjusted freely with respect to the shaft, and in this case as well, the operation and effect are substantially the same as those shown in FIGS. 1 to 9.

In the figure, the same reference numerals as those mentioned above indicate equivalent parts.

FIG. 10(a) shows the driving friction wheel 67 and the driven friction wheel 1.
The relationship with 9 is the same as that shown in FIG. 1, and in the figure, 71 is an inner eccentric cam, 72 is an outer eccentric cam, and 73 is a driving rotor.

10(b), (C), and (d) show that the relationship between the driving friction wheel 67 and the driven friction wheel 19 is shown in FIG.
a) This corresponds to (b) and (C).

Next, the operation of the apparatus of the present invention constructed as described above will be explained first with reference to the embodiments shown in FIGS. 1 to 8. When the lever 16 is rotated approximately 90 degrees in the direction of arrow A in FIG. 2, the eccentric cam 12 becomes as shown in FIG. 6. In this state, the driving friction wheel 67 and the driven friction wheel 19 are concentric, so both friction wheels 67 and 19 are in contact with each other around the entire circumference, and the discs 62 +' 65b on both sides of the driving friction wheel 67 are connected to the coil spring 66. As a result of this action, the driven friction wheel 19 having a patterned cross-sectional shape is compressed from both sides, so that when the driving friction wheel 67 rotates, the driven friction wheel 19 also rotates integrally with almost no slipping.

Therefore, if the input shaft 30 rotates in the direction of arrow C in FIG. 2 in this state, the planetary carrier 29 integrated with the input shaft 30
, the drive rotating body 48 rotates in the direction of the arrow in FIG.
3. Drive friction wheel 67 via key 64 and stepped shaft cylinder 65
is the same (rotates in the direction of the arrow, and as a result, the driven friction wheel 1
9. The driven rotary body 18 and the gear 22 also rotate substantially integrally with the drive friction wheel 67 in the direction of the arrow.

When the gear 22 rotates, the transmission gear 32 rotates integrally with the gear 22 via the internal transmission gear 26 as shown in FIGS. It rotates almost integrally with the carrier 29. When the planetary carrier 29 rotates, each planetary gear 5
6 also revolves integrally with the input shaft 30, and as a result, the sun gear 47 that meshes with these planetary gears 56 also rotates along with the output shaft 41.
It rotates almost integrally with the input shaft 30.

That is, in this case, the rotation ratio of the input shaft 30 and the output shaft 41 is 1:1. This state is the so-called low shift state of the present continuously variable transmission.

Next, when the lever 16 is rotated approximately 90 degrees in the direction of arrow B in FIG. 2 from this low gear shift state, the eccentric cam 12 will be in the state shown in FIG.
7 is also eccentric with respect to the driven friction wheel 19 as shown in FIG. 3.7. Therefore, the contact portion between the driving friction wheel 67 and the driven friction wheel 19 is only near point E shown in FIGS. 3 and 7. In this state, the drive friction wheel 6 is rotated in conjunction with the rotation of the input shaft 30.
7 rotates in the direction of arrow F in FIG.
9 also rotates in the direction of arrow G, but in this case both friction wheels 67
, 19, there is a difference in the radius of rotation up to the friction transmission point E.

That is, in FIG. 7, the center of the drive friction wheel 67 is set to 0. If the center of the driven friction wheel 19 is 02, the radius from OI to point E is R, and the radius from 0□ to point E is R2, then R1<R2. Therefore, in this case, the driven friction wheel 19 rotates at a reduced speed with respect to the driving friction wheel 67. In this example, the reduction ratio is 1:0.7
It is about 9. In other words, 0 for 1 rotation of the input shaft 30
．． The speed will be reduced by 21.

When the driven friction wheel 19 decelerates and rotates, the driven rotating body 1
8. Gear 22 rotates via screw 23 as shown by arrow H in FIG. 4, and as a result, transmission gear 32 rotates via internal transmission gear 26 in the direction of arrow I in FIG. In this case, the planetary carrier 29 is rotating together with the input shaft 30 at a faster speed than the transmission gear 32. Therefore, each planetary gear 56 is
Since it revolves in the direction of arrow J and rotates on its own axis in the direction of arrow J in FIG. 8, the sun gear 47 meshing with these planetary gears 56 rotates at a higher speed than the input shaft 30. That is, this planetary differential device increases the rotation speed of the output shaft 41 in proportion to the deceleration of the driven Fj friction wheel 19.
In this embodiment, when the number of teeth of the internal gear 32b is 60 and the number of teeth of the sun gear 47 is 12, the rotation of the output shaft 41 at the maximum eccentricity of the driven friction wheel 19 is equal to the rotation of the input shaft 30 by 1. The case is as follows.

1+ (-(0,79-1) X-) = 1+
(-(-0, 21)

If the lever 16 is set to any intermediate position in FIG. 2, a stepless gear ratio can be obtained from the low to the top.

Also, in the case of the modified examples shown in FIGS. 9 and 10, the operation is similar to that of the above embodiment, so the explanation will be omitted.

(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 driven friction wheel 19 that presses into engagement with the driving friction wheel 67 that rotates together with the input shaft 30. The amount of eccentricity can be freely adjusted with respect to the output shaft 41, which is concentric with Since the dynamic friction wheels 19 are joined concentrically, in this case both friction wheels 67, 19 are pressure-welded around the entire circumference, and as a result, an extremely high transmission efficiency of nearly 100% without slipping can be obtained.

Furthermore, even if the driving friction wheel 67 is eccentric with respect to the driven friction wheel 19 and the both friction wheels 67 and 19 are in a gear change state other than low where they are partially connected, the friction transmission contact E of both friction wheels
Since the ratio of the pitch line diameters is closer than 1:2, the friction transmission contact line is formed quite long on the pitch line, and the positive and negative slip bands existing on both sides of the pitch line are also As a result of being narrower than the conventional one, considerably high transmission efficiency can be obtained even in shift ranges other than low.

Therefore, according to the present invention, it is possible to provide a continuously variable transmission device having a relatively simple structure, a wide shift width, and extremely high transmission efficiency, especially in the low state, at a relatively low cost.

[Brief explanation of the drawing]

Fig. 1 is a longitudinal sectional side view of the device of the present invention, Fig. 2 is a front view of the device as seen from the input shaft side, and Fig. 3 is a partial cross-sectional view taken along the line ■-■ in Fig. 1 when the top gear is in a shifting state. FIG. 4 is a partial sectional view taken along line IV-It/ in FIG. 1, FIG. 5 is a sectional view of FIG. Partial sectional view taken along the VI line, No. 7
The figure is a partial sectional view taken along the line ■-■ in Figure 3, and Figure 8 is a partial cross-sectional view taken along the
Partial sectional view taken along the line ■-■ in the figure, Figures 9(a)(b)(
C) is a side view partially showing a modified example of the device of the present invention, and FIGS. 10(a), (b), (C), and (d) are side views showing partially cross-sectionally another modified example. 1... Case body 2... Base 3... Input side case lid 5... Output side case 7... Output side case lid 12... Eccentric cam 16... Lever
18... Driven rotating body 19... Driven friction wheel
22... Gear 26... Internal tooth transmission gear 29.
・・Planetary carrier 30・・Input shaft 32・
...Transmission gear 41...Output shaft 47...
Sun gear 48... Drive rotating body 55... Bolt (shaft) 56... Planetary gear 60... Sliding key 61... Shaft cylinder 63... Ring 64... Sliding key 65... Shaft cylinder 66...
・Coil spring 67... Drive friction wheel 68...
coil spring

Claims (1)

[Claims] 1. A planetary carrier formed integrally with the input shaft is integrally coupled with the driving rotary body, and a driven rotary body is provided whose eccentricity can be freely adjusted with respect to the output shaft provided concentrically with the input shaft,
A driving friction wheel configured to rotate integrally with the driving rotating body and a driven friction wheel configured to rotate integrally with the driven rotating body are pressed into engagement, and the driving friction wheel configured to rotate integrally with the driven rotating body is press-fitted. The external gear formed in the above-mentioned manner is meshed with an internal transmission gear provided rotatably with respect to the case, and the internal transmission gear is meshed with the internal transmission gear via the external gear. A continuously variable transmission characterized in that a planetary gear pivotally supported by a planetary carrier is meshed with the planetary gear and a sun gear formed integrally with the output shaft is meshed with each other to extract an output.