JPH1061739A - Continuously variable transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a continuously variable transmission capable of smoothly performing a shift change even during operation, increase shift change ratio larger than in the past, increase power transmission ability, improve power transmission efficiency and use a ball roller with good accuracy and productivity capable of using the two or more ball rollers. SOLUTION: In both sides of a casing 3, a prime mover shaft 1 provided with a prime mover wheel 1a in an inside end and a driven shaft 2 provided with a driven wheel 2a similarly in the inside are provided on the same axial line by opposing the prime mover wheel 1a to the driven wheel 2a. Between the prime mover wheel 1a and the driven wheel 2a, a rotating-around impeding frame 4, provided vertically respectively swivelably with a first swivel member 7, 7 meshed with a sector gear part 6, 6, is arranged. In an opposite side to a side provided with the sector gear part 6, 6 of the first swivel member 7, 7, a recessed groove is provided, in this recessed groove, two power transmitting ball rollers 9, 9 engaging a bearing-shaped outer ring 10 are provided. A second swivel member, swiveling the outer ring 10 by interposing its both sides of the ball roller 9 provided in the above, is provided.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a continuously variable transmission for transmitting a rotational force through a plurality of ball rolling elements.

[0002]

2. Description of the Related Art Japanese Patent Publication No. 38-25315 and Japanese Utility Model Publication No. 39-18631 show a continuously variable transmission which transmits a rotational force through a ball rolling element.
An object of the present invention is to improve the former problem using a plurality of ball rolling elements and to provide a device capable of manufacturing a device having a higher power transmission efficiency.

[0003] In order to facilitate understanding,
The continuously variable transmission disclosed in Japanese Patent No. 25315 will be described.

FIG. 1 shows the structure, in which a dish-shaped driving wheel 103 and a driven wheel 104 are provided at ends of a driving shaft 101 and a driven shaft 102 provided on the same axis, respectively.
Between the driving wheel 103 and the driven wheel 104, each of the driving wheel 103 and the driven wheel 104 is brought into pressure contact engagement with one point on the spherical surface, and a pair of ball rolling members which are brought into pressure contact engagement with each other at a line or point. A means for providing the rotors 105 and 106 and for inclining the rotation axis of the ball rolling elements 105 and 106, and a means for generating a pressing force between the ball rolling element and the driving wheel 103 and the driven wheel 104 are provided. It is a thing.

[0005] As means for inclining the ball rolling elements disclosed in the publication, the ball rolling elements 105 and 10 are used.
6 is provided with a supporting member 108 provided with an engaging tooth profile 107, respectively, and an annular gear 110 provided with racks 109, 109 meshing with the engaging tooth shapes 107, 107 is provided outside the supporting members 108, 108. The ring gear 110 is shifted by the speed change operation rod 113 via the U-shaped engaging portion 112 to tilt the ball rolling elements 105 and 106.

As a means for generating a pressure contact force, two ball transmission elements having a round head rivet shape are combined, and a spring 114 is provided inside, and a pressure contact force is generated by the spring 114. ing.

In a free state in which no load is applied to the driven shaft 102, the shift operation rod 113 is shifted to the left to engage the ring gear 110 with the detent 115.
The effective rotation diameter at the point where the ball rolling element and the prime mover contact each other is decelerated because the left side is larger than the right side, deceleration, constant velocity in the illustrated neutral position, and conversely when shifting to the right, Therefore, the rotation of the driven shaft 102 is accelerated.

However, during an actual operation in which a load is applied to the driven shaft 102, a torsional moment acts on the ball rolling element, so that there is no backlash between the rack 109 and the engaging tooth form 107, and a close contact state is established. As a result, there is a disadvantage that the shift operation rod 113 cannot be shifted and the shift cannot be performed during driving.

Also, the width of the support member 108 of the ball rolling element must be wide because of the necessity of providing the engaging tooth form 107, so that the prime mover 10 which can be used for transmitting power is used.
There is a disadvantage in that the contact spherical surface with 3,104 is reduced, and the speed ratio is reduced only in that portion.

In addition, with this structure, it is difficult to increase the number of ball rolling elements in order to improve the power transmission capacity when implementing means for inclining the ball rolling elements.

Further, since the structure of the ball rolling element is a split-shaped special structure, production and accuracy are difficult.

[0012]

SUMMARY OF THE INVENTION An object of the present invention is to enable a smooth shift even during operation. The gear ratio can be made larger than conventional gear ratios. It is another object of the present invention to provide a continuously variable transmission using a ball rolling element with high accuracy and high productivity that can use the ball bearing manufacturing technology as it is.

[0013]

SUMMARY OF THE INVENTION The present invention has been made in order to solve the above-mentioned problems, and has a driving shaft provided with a driving wheel at both inner ends of a casing, and a driven wheel also provided at the inner end. A driven shaft is provided on the same axis with the driven vehicle and the driven vehicle facing each other, and a first swing member in which a sector gear is meshed between the driven vehicle and the driven vehicle is slidably provided vertically. A suitable number of power transmissions in which a revolution prevention frame is arranged and a bearing-shaped outer ring is engaged with each groove provided on the side opposite to the side provided with the sector gear portion of each of the first swing members. A continuously variable transmission, wherein a ball rolling element is provided, and second swing driving means for swinging while holding an outer ring of the ball rolling element provided above or below is provided.

[0014]

FIG. 2 is a longitudinal sectional front view of a first embodiment using two ball rolling elements, FIG. 3 is a sectional view taken along line AA, and FIG. 4 is a component incorporated therein. FIG. 3 is an exploded perspective view of FIG.

2 to 4, reference numeral 1 denotes a driving shaft provided with a dish-shaped driving wheel 1a at the inner end, and 2 denotes a driven shaft provided with a dish-shaped driven wheel 2a at the inner end. Placed,
The casing 3 is rotatably attached to the housing portions 3a and 3b.

Numeral 4 denotes a revolution preventing frame having a shape as shown in FIG. 4. The projections 4a, 4a provided on both sides are engaged with the concave grooves 3c, 3c of the casing 3, and are fixed in place by screws 5, 5. ing. Upper and lower arc-shaped slide portions 4b, 4b are provided, and the slide portions 4b, 4b are provided with gutter-shaped first swing members 7, 7 in which sector gears 6, 6 provided at a central portion are meshed with each other. Has been abutted.

A groove 8 is provided on each of the first rocking members 7, 7 on the side opposite to the side on which the sector gear 6 is provided. Outer ring 10 is engaged.

In the first embodiment, as shown in FIG. 3, a bearing-shaped outer ring 10 rotatably mounted on a ball rolling element 9 connects the outer ring 10 with a ball via a ball similarly to a ball bearing. FIG. 5 (a) shows a ball roller in which a raceway groove 121 is provided in the outer race 10 and a cylindrical roller 122 is engaged with the raceway groove 121, as shown in FIG. As shown in FIG. 5 (b), a ball rolling element is provided with a raceway groove 123 in the ball rolling element main body and a cylindrical roller 122 is engaged with the raceway groove 123, as shown in FIG. A die roller 104 is provided between the outer race 10 and the ball rolling element main body, or a type in which a ball bearing 125 is used for the outer ring and the ball rolling element main body is a hemisphere united type as shown in FIG. 5D. You can do it. These ball rolling elements can be manufactured with high manufacturing accuracy using the conventional ball bearing manufacturing technology.

The thus configured ball rolling elements 9, 9
Is arranged so that both sides are narrowed by the rims of the driving wheel 1a and the driven wheel 2a, like the conventional continuously variable transmission, and the contact pressure is applied via the washers 13 by the initial pressure nuts 11, 12. It has become.

Reference numerals 14 and 14 denote a second swinging member,
a, 14a are pivotally mounted on the bearing portion of the casing 3, and the respective slit grooves 14b, 14b are connected to the outer race 10 of the upper ball rolling element 9.
The fan gear 14d is provided with an engaging portion on both sides of the shaft and having a swing limiting hole 14c. Reference numeral 15 denotes a stud that is engaged with the swing limiting hole 14c and is implanted in the casing 3.

Each sector gear 14 of the second swinging members 14, 14
d, 14d are pinions 17, 17 provided on the transmission shaft 16.
The transmission shaft 16 is configured to be driven via a differential gear mechanism 19 by rotating a handle 18.

The differential gear mechanism 19 includes a fixed crown gear 191 having _one tooth fixed to the casing 3 and a transmission shaft 16.
A flexible crown gear 192 having _two teeth and fixed to the fixed crown gear 191 and having the handle 18;
It comprises a driving disk 194 for moving the balls 193 and 193 while pressing the balls 193 against the flexible crown gear 192. The operation of the driving disk 194 will be described below.

FIG. 6 is an exploded view for explaining the operation of the differential gear mechanism 19.
When the ball 193 is rotated in the direction of arrow P1, the ball 193 revolves while rotating in the direction P2, and generates a wavy motion in the flexible crown gear 192. Therefore, the flexible crown gear 192 is differentially decelerated by the difference in the number of teeth from the fixed crown gear 191, and the reduction ratio R is

[0024]

(Equation 1)

## EQU1 ## For example, Z ₁ = 100 sheets, Z ₂ =
Assuming 102 sheets, R = 1/10.

Since the steering wheel 1 is constructed as described above,
8, the transmission shaft 16 rotates, and the pinion 17,
17, the upper ball rolling element 9 is swung through the fan-shaped gear portions 14d, 14d meshing therewith and the second swinging members 14, 14.

When the upper ball rolling element 9 is swung, the lower ball rolling element 9 is interlocked via the first swing members 7, 7 engaged with the sector gears 6, 6. Rocked in the opposite direction.

FIG. 7 shows the contact state of the prime mover and the driven vehicle when the ball rolling elements 9 and 9 swing. In the state [1], the rotation of the prime mover contacting the ball rolling element is shown. Since the effective diameter is larger than that of the driven vehicle side, the driven vehicle turns at high speed, and at the neutral position in the state (II), the driven vehicle has the same speed as the driving vehicle, and in the state of (III), the driven vehicle has the same speed. Since the effective rotation diameter of the driven vehicle is smaller than that of the driven vehicle, the speed of the driven vehicle is reduced.

In the continuously variable transmission described above, the revolution preventing frame 4 is provided with the first swing members 7 and 7 linked by the sector gears 6 and 6, and the ball rolling elements 9 are provided in the concave grooves 8 and 8. , 9 are engaged with each other,
Outer ring 10 of one (upper in the embodiment) ball rolling element 9
The ball rolling elements 9, 9 are configured to be rocked in conjunction with each other by the second rocking driving means for pinching and rocking both sides of the ball rolling elements. However, the bite phenomenon does not occur unlike the conventional continuously variable transmission, so that the continuously variable transmission can be smoothly performed.

Moreover, as can be seen from FIG.
a and the ball rolling element 9 are in engagement with each other, so that the so-called hertz area is large, and the difference in the rotation ratio between the motor 1a and the diameter passing through the inner and outer ends of the hertz area of the ball rolling element 9 is small. Equipped with efficient contact conditions for transmission capacity.

Further, since the outer race 10 is for supporting and swinging the ball rolling element main body, it does not require a wider width than the conventional one shown in FIG. Since it is wide, there is an advantage that the gear ratio can be made larger than in the conventional device.

Further, since the ball rolling element 9 can use the ball bearing manufacturing technology as it is because of its structure, a high-precision ball rolling element can be provided at low cost.

Since the ball rolling elements 9, 9 and the first swing members 7, 7 are in a floating state at the time of assembly, they follow the shapes of the rims of the driving wheel 1a and the driven wheel 2a. The rolling elements 9 and 9 come into contact with the rims of the driving wheel 1a and the driven wheel 2a with uniform pressure, and can cover the manufacturing accuracy error of each part.

8 to 10 show a second embodiment using four ball rolling elements. FIG. 8 is a longitudinal sectional front view, FIG. 9 is a sectional view taken along the line BB, and FIG. FIG. 3 is an exploded perspective view of components incorporated in the device.

8 to 10, reference numeral 201 denotes a driving shaft provided with a dish-shaped driving wheel 201a at the inner end, and reference numeral 202 denotes a driven shaft provided with a dish-shaped driven wheel 202a at the inner end. The housing part 2 of the casing 203
Numerals 03a and 203b are attached rotatably.

Numeral 204 denotes a revolving block having a shape as shown in FIG. 10. The projections 204 a, 204 a provided on both sides are engaged with the concave grooves 203 c, 203 c of the casing 203, and are fixed in place by screws 205, 205. ing. Upper and lower arc-shaped slide portions 204b, 204b are provided, and first swing members 207, 207 in which sector gears 206, 206 provided at a central portion are engaged with each other, are brought into contact with the slide portions 204b, 204b. Have been.

The first swinging members 207, 207 have grooves 208, 207 on the side opposite to the side where the sector gear 206 is provided.
By forming a mountain-shaped portion provided with a groove 208,
The ball-shaped outer races 210 provided on the ball rolling elements 209 are engaged with the ball rolling elements 208, respectively.

Thus, the upper and lower first swing members 20
Four ball rolling elements 209,2 engaged with 7,207
09, 209, and 209 are the same as in the first embodiment.
Both sides are arranged so as to be sandwiched between the rim portions of the driving wheel 201a and the driven wheel 202a.
The contact pressure is applied via the washer 213.

Reference numerals 14 and 14 denote second swing members having the same structure as that of the first embodiment. The ear shafts 14a and 14a are pivotally mounted on the bearing portion of the casing 203, and the respective slit grooves 14b and 14b are provided.
To the outer races 210, 2 of the upper ball rolling elements 209, 209.
A fan-shaped gear portion 14d which is engaged with the outside of the motor 10 and has a swing limiting hole 14c is provided. Reference numeral 15 denotes a stud that is engaged with the swing restriction hole 14c and is implanted in the casing 203.

Numeral 19 denotes a differential gear mechanism, the construction and operation of which are the same as in the first embodiment, and a description thereof will be omitted.

The handle 1 is constructed as described above.
8, the transmission shaft 16 rotates, and the pinion 17,
17, the upper ball rolling element 20 via the sector gears 14d, 14d meshing therewith and the second swing members 14,
9 and 209 are rocked.

When the upper ball rolling elements 209, 209 swing, the lower ball rolling elements 209, 209 interlock via the first swinging members 207, 207 engaged with the sector gears 206, 206. And rocked in the opposite direction.

The ball rolling elements 209, 209, 20
The stepless speed change is performed by the swinging motions 9 and 209 as in the case of the first embodiment. However, since four ball rolling elements are used, the ball rolling elements, the prime mover and the driven vehicle are used. Since the rim portion is inscribed engagement, the hertz area is doubled as compared with the case of the first embodiment, so that a larger transmission capacity can be obtained.

The other effects and advantages are the same as in the first embodiment, and will not be described.

[0045]

According to the present invention, the speed can be changed smoothly even during driving. Since the width of the outer ring can be made narrower than that of the conventional structure, the gear ratio can be made larger than that of the conventional structure. In addition, since the structure is such that the number of ball rolling elements can be increased, it is possible to provide a continuously variable transmission having a large power transmission capacity and a high power transmission efficiency.

Further, the ball bearing manufacturing technology can be used as it is, and a continuously variable transmission using a ball rolling element with high accuracy and high productivity can be provided.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a configuration of a conventional continuously variable transmission.

FIG. 2 is a vertical sectional front view of the first embodiment of the present invention.

FIG. 3 is a sectional view taken along line AA of FIG. 2;

FIG. 4 is an exploded perspective view of components incorporated inside the first embodiment of the present invention.

FIG. 5 is a view showing an example of the structure of various ball rolling elements that can be used in the present invention.

FIG. 6 is a development view for explaining the operation of the fine movement gear mechanism.

FIG. 7 is an explanatory diagram of a shift operation according to the first embodiment of the present invention.

FIG. 8 is a vertical sectional front view of the second embodiment of the present invention.

FIG. 9 is a sectional view taken along line BB of FIG. 8;

FIG. 10 is an exploded perspective view of components incorporated inside the second embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Driving shaft 1a Driving wheel 2 Driving shaft 2a Driving shaft 3 Casing 3a, 3b Housing part 3c Concave groove 4 Revolution prevention frame 4a Projection 4b Slide part 5 Screw 6 Sector gear part 7 First swing member 8 Concave groove 9 Ball rolling Element 10 Outer ring 11, 12 Initial pressure nut 13 Washer 14 Second swing member 14a Ear shaft 14b Slit groove 14c Swing limiting hole 14d Sector gear section 15 Stud 16 Shift shaft 17 Pinion 18 Differential gear mechanism 191 Fixed crown gear 192 Possible Flexible crown gear 193 Ball 194 Driving disk

────────────────────────────────────────────────── ───

[Procedure amendment]

[Submission date] October 30, 1996

[Procedure amendment 1]

[Document name to be amended] Statement

[Correction target item name] 0024

[Correction method] Change

[Correction contents]

[0024]

[ Equation 1 ]

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0025

[Correction method] Change

[Correction contents]

## EQU1 ## For example, Z ₁ = 100 sheets, Z ₂ =
If 102, then R = 101 .

[Procedure amendment 2]

[Document name to be amended] Statement

[Correction target item name] 0028

[Correction method] Change

[Correction contents]

FIG. 7 shows the state of contact between the prime mover and the driven vehicle when the ball rolling elements 9 and 9 swing. In the state [I] , the rotation of the prime mover that comes into contact with the ball motor is effective. Since the diameter of the driven vehicle is larger than that of the driven vehicle, the driven vehicle rotates at a high speed. At the neutral position in the state [II], the driven vehicle has the same speed as the driving vehicle. Since the rotation effective diameter on the side is smaller than that on the side of the driven vehicle, the driven vehicle becomes slow.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0030

[Correction method] Change

[Correction contents]

Moreover, as can be seen from FIG.
Because a the ball rolling elements 9 is engaged inscribed engagement, large-called Hertz area and rotation ratio difference diameter through the Hertz area inside and outside end of the driving wheel 1a and the ball rolling members 9 are small, transmission With efficient and efficient contact conditions.

Claims (1)

[Claims] 1. A driving shaft provided with a driving wheel at an inner end on both sides of a casing, and a driven shaft provided with a driven wheel also at the inner end are provided on the same axis with the driving vehicle and the driven vehicle facing each other. And, between the prime mover and the driven vehicle, a revolving-prevention frame in which a first swing member meshed with a sector gear portion is provided so as to freely swing up and down, and a sector gear of each of the first swing members is provided. A suitable number of power transmitting ball rolling elements in which a bearing-shaped outer ring is engaged with a concave groove provided on the side opposite to the side provided with the portion, and the ball rolling elements provided above or below are provided. A continuously variable transmission, comprising a second swing drive means for sandwiching and swinging an outer ring.