JP2003120775A - Speed change gear - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a speed change gear having a large speed changing range, and securing a large torque for the whole range. SOLUTION: An input wheel 12 is rotatably provided on the outside of a pair of sun wheel 6 and 6 provided on a fixed shaft. A planetary wheel unit 20 is provided on the inner side of the input wheel 12 to be energized in an eccentric direction by a pressurizing unit 24. A rotatable planetary wheel 23 on the innermost circumference is thus pressed to the sun wheels 6 and 6. As the input wheel 12 is rotated following rotation of an input shaft 4, the planetary wheel 23 revolves, while turning inversely by rolling friction to the sun wheels 6 and 6. The three planetary wheels 23 are connected to each other through a torque transmission arm 32 and torque transmission wheels 35a and 53b, and their rotation is transmitted through a large gear 38 and a small gear 39 provided on the torque transmission wheel 35c to an output shaft 5. As a handle 9 is operated, separation distance between the paired sun wheels 6 and 6 is adjusted, and circumferential length of a part where the sun wheels 6 and 6 get in contact with the planetary wheel 23 is changed, thereby ratio between the rotational speed of the input shaft 4 and the rotational speed of the output shaft 5 is continuously varied.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a transmission that is composed of members that make planetary movements and that can change the gear ratio steplessly.

[0002]

2. Description of the Related Art Conventionally provided continuously variable transmissions include those based on the basic principle shown in FIG. 14, for example. That is, the conical input wheel 102 connected to the power 101 is rotated, the output wheel 103 is pressed against the outer periphery of the input wheel 102 to transmit the rotation, and the output wheel 103 is pressed by various mechanisms while maintaining the state in which both are pressed. It is known that any one of the input wheel 103 and the input wheel 102 is moved in the axial direction and the axis-perpendicular direction to thereby arbitrarily change the rotation of the output wheel. This is based on the shift principle that rolling friction between the input wheel 102 and the output wheel 103 is used to transmit rotation and torque, and the difference in circumferential length between the two wheels is used to shift gears. Is.

[0003]

However, in the continuously variable transmission having the above-described basic structure, the contact position of the output wheel 103 with respect to the input wheel 102 moves to the right (the direction B) in the figure. Gear ratio is large, but both wheels 1
The rolling friction for transmitting power between 02 and 103 gradually becomes smaller, and eventually power cannot be transmitted. That is, as the gear ratio increases, only a small torque can be transmitted.

Therefore, the gear ratio that can be generally obtained is about 4: 1 to 1: 1/4, and the gear range is narrow.
Moreover, there is a problem that a large torque cannot be secured over the entire shift range, and the transmission efficiency is extremely reduced if a gear ratio of 4: 1/4 is exceeded.
For this reason, for example, when a conventional type transmission is attached to a lathe and a speed change rotation of about 1/10 of the rotation of the power is to be used, the speed is changed between the power and the transmission or directly by connecting the power and the transmission. It was necessary to incorporate a gear reduction device between the machine and the lathe. Further, in order to obtain the rotation speed in the range of 1: 1 to 1: 1/16, it was necessary to use the transmissions connected in series.

The present invention has been made in view of the above-mentioned conventional problems, and an object of the present invention is to provide a speed change device having a wide speed change range and capable of securing a large torque over the entire range.

[0006]

In order to solve the above-mentioned problems, according to the invention of claim 1, the rotary support which is rotated by the input power and the rotary support are arranged such that their rotation centers coincide with each other. In the rotating body, a friction surface whose longitudinal section along the center of rotation is inclined is provided on the peripheral surface, and the fixed ring is allowed to move in the extending direction of the center of rotation and is prohibited from rotating. An adjusting mechanism that adjusts the position of the rotation center of the fixed wheel in the extending direction, and a ring body that is rotatably assembled to the rotation support body in a direction opposite to the rotation support body, the crossing being orthogonal to the rotation center. A rotary wheel having a circular friction surface provided on the peripheral surface, and the rotary wheel is pressed in a predetermined direction so as to be eccentric with the rotary support, and the peripheral surface of the rotary wheel is pressed against the peripheral surface of the fixed wheel. Rotation of the rotating wheel is transmitted to the pressing mechanism It is was assumed that an output shaft.

In such a structure, when the rotary support body is rotated by the input power, the rotary wheel, which is an annulus, revolves around the rotation center of the fixed wheel and the friction surface of the rotary wheel. Due to the rolling friction between the fixed wheel and the friction surface, the rotation of the fixed wheel is delayed by the rotation of the rotation support body, and the rotation is transmitted to the output shaft. That is, the rotation from the power is transmitted to the output shaft by utilizing the rolling friction between the fixed wheel and the rotating wheel. Further, when the moving position of the fixed wheel is adjusted by the adjusting mechanism, the rotation speed of the rotating wheel changes due to the difference in the circumferential length (diameter) of the two wheels at the position where the fixed wheel and the rotating wheel are in contact with each other. That is, the gear ratio changes.

Here, when the difference between the diameters of the two wheels at the position where the fixed wheel and the rotating wheel are in contact with each other becomes smaller, the gear ratio increases, but as the difference between the diameters decreases, the rolling friction increases, so the gear ratio increases. The greater the torque can be transmitted.

Further, in the invention of claim 2, the fixed wheels are provided as a pair in the extending direction of the rotation center, and the adjustment mechanism is a mechanism for adjusting the distance between the pair of fixed wheels. It was supposed to be

In such a structure, the revolving rotary wheel and the fixed wheel are in a two-point contact state, and the rolling friction between them is doubled.

Further, in the invention of claim 3, the pressing mechanism presses the rotating wheel in a predetermined direction at a plurality of positions on the same circumference.

In such a structure, since the rotating wheel is pressed in a predetermined direction at a plurality of locations on the same circumference, the processing accuracy of the friction surfaces of both wheels at the position where the fixed wheel and the rotating wheel are in contact with each other, The rotating wheel and the fixed wheel can be brought into stable contact with each other without increasing the assembly accuracy of each member.

Further, in the invention of claim 4, the pressing mechanism includes a guide mechanism for restricting a pressing direction of the rotary wheel to a constant direction.

Also in this structure, since the pressing direction of the rotary wheel is regulated to a fixed direction by the guide mechanism, the processing accuracy of the friction surfaces of both wheels at the position where the fixed wheel and the rotary wheel are in contact with each other, and the assembly of each member The rotating wheel and the fixed wheel can be brought into stable contact with each other without increasing the attaching accuracy.

Further, in the invention of claim 5, the shape of the longitudinal cross section along the center of rotation between the friction surface of the fixed wheel and the friction surface of the rotary wheel is curved in opposite directions. did.

In such a structure, when the position of the fixed wheel changes, that is, when the gear ratio is changed, the positions of the contact points of both the fixed wheel and the rotating wheel change, so that the friction surfaces of both wheels during the use period are changed. Wear degree is reduced.

Further, in the invention of claim 6, a plurality of the fixed wheels sharing the rotary support and the rotary wheels are arranged in parallel along the center of rotation, and the rotation of each rotary wheel is prevented. A transmission mechanism for transmitting to the output shaft is provided.

In such a structure, the structure is relatively simple, and the size of the device is not so large.
It is possible to obtain a large output torque according to the number of sets of fixed wheels and rotating wheels.

Further, in the invention of claim 7, the transmission mechanism includes a connecting mechanism for connecting the rotating wheels adjacent to each other while permitting relative movement in the eccentric direction.

In such a structure, the rotation is transmitted to the output shaft by the rotation of the plurality of rotating wheels in cooperation with each other.

Further, in the invention of claim 8, the rotary support is hollow, the rotary wheel is assembled inside the rotary support, and the fixed wheel is arranged inside the rotary wheel. The friction surface is provided on the inner peripheral side of the rotating wheel, and the friction surface is provided on the outer peripheral side of the fixed wheel.

In such a structure, when the rotary support rotates, the rotary wheel revolves around the fixed ring, and rolling friction occurs between the friction surface of the rotary wheel and the friction surface of the fixed ring. After that, the rotation is transmitted to the output shaft. Even in this case, the rotation from the power is transmitted to the output shaft by utilizing the rolling friction between the fixed wheel and the rotating wheel, and the gear ratio can be changed by the adjusting mechanism, and the gear ratio becomes large. Accordingly, due to the increase in rolling friction, a large torque can be transmitted even when the gear ratio is large.

Further, in the invention of claim 9, the adjusting mechanism is a tubular member which is fitted on the fixed ring while the fixed ring is slidable in the position adjusting direction and is prohibited from rotating. ,
A fixed shaft having a key hole extending in the position adjusting direction opened on the peripheral surface and a fixed shaft are rotatably fitted in the fixed shaft in both forward and reverse directions. A moving shaft having a threaded portion provided in a predetermined region of the peripheral surface corresponding to the key hole of the shaft, and a threaded portion of the moving shaft that meshes with the threaded portion of the moving shaft from the outside of the fixed shaft through the key hole. A moving key inserted from one side in the position adjusting direction is included in the central portion side.

In such a structure, in the structure in which the fixed ring is arranged inside the rotary wheel, the position of the fixed ring can be accurately adjusted. In addition, when there are a plurality of pairs of fixed wheels or a plurality of fixed wheels and rotating wheels, the positions of the plurality of fixed wheels can be adjusted collectively and accurately.

Further, in the invention of claim 10, the rotary wheel is assembled on the outer side of the rotary support, the fixed wheel is disposed as an annular body on the outer side of the rotary wheel, and the outer peripheral side of the rotary wheel is provided. The friction surface is provided, and the friction surface is provided on the inner peripheral side of the fixed ring.

In such a structure, since the rotary ring and the fixed ring are located outside the rotary support without increasing the outer dimensions, the friction surface of both the fixed ring and the rotary ring pressed against each other is larger. A radius of curvature can be secured. In addition, the input shaft for inputting power can be used as a rotary support, the number of members for revolving the rotating wheel is reduced, and the input shaft and output shaft are coaxial without complicating the overall structure. Can be placed on top.

[0027]

BEST MODE FOR CARRYING OUT THE INVENTION An embodiment of the present invention will be described below with reference to the drawings. (First Embodiment) Configuration FIG. 1 is a sectional view showing a transmission 1 according to a first embodiment of the present invention. First, an outline will be described. The transmission 1 includes a housing 2 forming a main body of the apparatus, a fixed shaft 3 penetrating the housing 2 and fixed by a nut, an input shaft 4 protruding to one side portion (left side in the drawing) of the housing 2 and the other. It has an output shaft 5 projecting to the side (right side in the figure), and the rotation input from the power to the input shaft 4 is used as a plurality of sun wheels 6, an input wheel 12, a plurality of planet wheels 23 and The first to third torque transmission wheels 35a, 35b, 35c and the like are used to change the speed and transmit it to the output shaft 5 to take out rotational torque from the output shaft 5.

The details of each unit will be described below. On the fixed shaft 3 penetrating the housing 2, sun wheels 6 and 6 which are fixed wheels according to the present invention and which are made of the same member and which are paired with each other, that is, have a symmetrical shape are arranged at predetermined intervals in the axial direction. Three pairs are arranged side by side. Each sun wheel 6 has a substantially frustoconical shape, and a friction surface 6a is formed on the outer periphery of the sun wheel 6 so that the longitudinal section (section shown in FIG. 1) along the center of rotation is curved in a concave shape and is inclined. The sun wheels 6 and 6 forming a pair are externally fitted to the fixed shaft 3 in a state where the right and left are reversed. Also,
The pair of sun wheels 6 and 6 are prevented from rotating in the state of being assembled to the fixed shaft 3 by a mechanism described below, and at the same time, position adjustment in a direction in which they approach or separate from each other is possible.

FIG. 2 is a diagram showing a main part of the adjusting mechanism D in the present embodiment for adjusting the positions of the pair of sun wheels 6, 6. As shown in FIG. 2, the fixed shaft 3 is a hollow member, and the circumferential surface of the fixed shaft 3 is located at a position corresponding to each sun ring 6 in the axial direction, that is, in the position adjustment direction of the sun ring 6 (extension of the rotation center). Key hole 3a extending in the present direction) and reaching the inside of the fixed shaft 3, and the engagement groove 3 also extending in the axial direction.
b and are provided. An engagement pin 7 is inserted into the sun wheel 6 from the peripheral surface outside the friction surface 6a toward the center, and the tip end of the engagement pin 7 engages with the engagement groove 3b. . As a result, the sun wheel 6 is prohibited from rotating and at the same time is allowed to move in the axial direction. Alternatively, instead of using the engagement pin 7, for example, a slip key may be used, or the fixed shaft 3 may be a spline shaft and the sun wheel 6 may be meshed with the sun wheel 6 to prohibit only the rotation of the sun wheel 6. Good.

Further, three movable shafts 8 having a predetermined length are loosely inserted inside the fixed shaft 3. As shown in the drawing, an engaging concave portion 8a is formed at one end (left side in the figure) of each moving shaft 8 and an engaging convex portion 8b is formed at the other end (right side in the figure). The engaging projection 8b of the other moving shaft 8 is engaged with the engaging recess 8a of the one moving shaft 8 that is adjacent to the inside. Further, one end side of the moving shaft 8 located on the input shaft 4 side among the three moving shafts 8 is a crank type that is loosely inserted into the fixed shaft 3 from the outside of the housing 2 by the engaging structure similar to the above. When the operation handle 9 is engaged and the operation handle 9 is rotationally operated, the three moving shafts 8 are integrally rotated in the fixed shaft 3 in both forward and reverse directions.

Further, as shown in FIG. 3, the key holes 3 corresponding to the pair of sun wheels 6 and 6 are provided on the peripheral surface of each moving shaft 8.
The 1st screw part 8c and the 2nd screw part 8d are provided in the predetermined area | region corresponding to a. Both first screw portions 8c,
8d has a right-hand thread on one side and a left-hand thread on the other side. On the other hand, a pair of sun wheels 6, 6
As shown in FIG. 2, the central portion of each of the first and second screw portions 8 is provided from the outside of the fixed shaft 3 through the key hole 3a.
A moving key 10 that meshes with c and 8d is fitted from one side in the position adjusting direction, and is prevented from coming off from each sun wheel 6 by a donut plate-like retaining member 11. Thus, when the operation handle 9 is rotated to one side or the other, the pair of sun wheels 6 and 6 collectively,
In the state where the rotation is prohibited, the movement keys 10 are used to accurately move in the directions in which they approach or separate from each other.

Further, as shown in FIG. 4A, gaps L1 and L2 are provided between the moving shafts 8 adjacent to each other inside the fixed shaft 3 (the moving shaft 8 and the operating handle not shown). The same applies to the engaging portion with 9.). As a result, the pair of sun wheels 6 and 6 can move in the extending direction of the fixed shaft 3 (directions a and b) while maintaining the state in which the positions thereof are adjusted and the distance between them is determined. Has become.

On the other hand, as shown in FIG.
A hollow input wheel 12 is housed inside. The input wheel 12 is a rotary support of the present invention, and is provided inside the housing 2 and has a first boss portion 2a located on the side of the operation handle 9 and a second boss portion located on the other side. Two
b, and is rotatably supported via first and second bearings 13 and 14. An input-side large gear 15 that is loosely fitted to the outside of the first boss 2a is attached to an end of the input wheel 12 on the side of the operation handle 9. The input-side large gear 15 meshes with the input-side small gear 16 provided on the input shaft 4, and the input wheel 12 is rotated via the input-side large gear 15.

Inside the input wheel 12, three planetary wheel units 20, 20, 20 corresponding to the above-mentioned respective pairs of sun wheels 6, 6 and independent from each other are mounted side by side in the axial direction of the fixed shaft 3. Has been. Each of the planetary wheel units 20, 20, 20 has a holding ring 21 supported by the input wheel 12, which is an annular body, a third bearing 22 fitted in the holding ring 21, and a third bearing 22. It is comprised of a planet wheel 23 which is a rotating wheel of the present invention.

FIG. 5 is a sectional view taken along line I--I of FIG. 1, showing the assembly structure of the planetary wheel unit 20 to the input wheel 12. The input wheel 12 has a ring-shaped planetary wheel unit 2
A pair of pressing units 24, 24, which urge 0 in a predetermined direction so that its rotation center P (see FIG. 5) is eccentric with the rotation center O of the input wheel 12, are provided close to each other on the same circumference. There is. Each pressing unit 24, 24 constitutes the pressing mechanism of the present invention, and is a sleeve 25 embedded in the input wheel 12, and is slidably fitted into the sleeve 25 and screwed to the outer circumference of the holding ring 21. And a spring 27 that is externally inserted into the support pin 26 and has one end thereof housed in the sleeve 25 and is contracted between the sleeve 25 and the holding ring 21. Then, the planet wheel unit 20 is biased in a certain direction by the spring force of each spring 27, 27 of the pair of pressing units 24, 24, and the planet wheel 23 of the innermost circumference corresponds to the pair of sun wheels 6, 6. 6, both friction surfaces 6a,
6a is pressed.

Further, on the outer peripheral portion of the holding ring 21,
On the same circumference as the pair of support pins 26, 26,
The intermediate point between the pair of support pins 26, 26 and the planetary wheel unit 2
A direction regulating block 29 is screwed by a bolt 28 at a position where a straight line passing through the rotation center P of 0 (see FIG. 5) intersects. The direction regulation block 29 is inserted into the hole formed in the input wheel 12 from the outside of the input wheel 12 in correspondence therewith, and is slidably supported. As a result, the biasing direction of the planetary wheel unit 20 by the spring force of the springs 27, 27 described above is regulated to a fixed direction. That is, in the present embodiment, the pair of pressing units 24,
The guide mechanism of the present invention is realized by the direction of 24 being restricted by each sleeve 25, each support pin 26, and block 29. The types of the springs 27, 27 can be appropriately changed as long as the above-mentioned functions can be ensured, and for example, hydraulic pressure, pneumatic cylinders or the like can be used.

FIGS. 6 (a) to 6 (c) show three planetary wheel units 20 by a pressing mechanism composed of the above-mentioned respective parts.
It is a schematic diagram corresponding to FIG. 5 which showed the urging | biasing direction of 20,20. The planetary wheel units 20, 20, 20 are arranged in a fixed manner as indicated by arrows in the figure because the pair of pressing units 24, 24 corresponding to each planetary wheel unit and the direction restriction block 29 are arranged differently on the input wheel 12. Angular spacing of (120
°) and are urged in different directions.

Further, as shown in FIG. 7, the inner peripheral side of the planetary wheel 23 constituting the planetary wheel unit 20 has a trapezoidal shape with rounded corners in a longitudinal section along the center of rotation, and is curved. Both corners 23b, 23b are in contact with and pressed against the friction surfaces 6a, 6a of the pair of sun wheels 6, 6 at one point on the circumference. Both corners 23b and 23b are friction surfaces on the planetary wheel 23 side in the present invention, and the curvature in the illustrated vertical cross section is smaller than that of the friction surfaces 6a and 6a of the pair of sun wheels 6 and 6.

On the other hand, each planet wheel unit 20, 20,
A pair of four torque transmission arms 32, each having a roller 31 provided at the tip of a shaft 30, are provided on the side surface of the planet wheel 23 of 20. The torque transmission arm 32
Is provided only on the right side surface of the planet wheel 23 (FIG. 7) of the planet wheel unit 20 located on the input shaft 4 side, and is provided on both side surfaces of the other planet wheels 23 respectively. There is.

Further, the fixed shaft 3 supporting the sun wheel 6 has first to third torque transfer wheels 35a, 35a, 3a which together with the plurality of torque transfer arms 32 constitute a connecting mechanism of the present invention.
5b and 35c are rotatably supported via a fourth bearing 36, respectively. As shown in FIGS. 7 and 8, the first to third torque transmission wheels 35a, 35b, 35c.
Four notches 37 that are open to the peripheral surface and the side surface are radially provided in the. In each notch 37, the roller 31 of each torque transmission arm 32 protruding from the adjacent planet wheel 23 is loosely fitted with a proper clearance,
Each roller 31 is rollable in the notch 37 and is also movable in the radial direction of the first to third torque transmission wheels 35a, 35b, 35c. As a result, as described above with reference to FIG. 6, each planet wheel unit 20, 20, 20
The first to third torque transmission wheels 35a, 35b, 35c can rotate together with the planet wheel units 20, 20, 20 even if the rotation centers of the two are eccentric in different directions.

Further, in the third torque transmission wheel 35c located on the rightmost side in FIG. 1, the third boss portion 2 provided inside the second boss portion 2b of the housing 2 described above.
An output-side large gear 38 that is loosely fitted to the outside of c is attached. The output-side large gear 38 meshes with the output-side small gear 39 provided on the output shaft 5, and the third torque-transmitting wheel 35
The rotation of c is transmitted to the output shaft 5 via the large output gear 38 and the small output gear 39.

Operation Next, the operation of the transmission 1 configured as described above will be described. When the input shaft 4 is rotated by power, the input wheel 12 is rotated via the input small gear 16 and the input large gear 15. At this time, each planet wheel unit 20, 20, 20
Are urged by the pressing units 24 in a direction eccentric to the input wheel 12, and the inner peripheral side of each planet wheel 23 is pressed against the pair of sun wheels 6, 6. For this reason,
Each planet wheel unit 20, 20, 20 revolves around the input shaft 4 so as to wind around the pair of sun wheels 6, 6, and at the same time, the planet wheel 23 of each planet wheel unit 20, 20, 20 The peripheral corner portion 23b and the friction surface 6 of the pair of sun wheels 6 and 6
Due to the rolling friction with a, it rotates behind the input wheel 12 and rotates.

At this time, the planet wheels 23, 23, 23
Are connected to each other via a plurality of torque transmission arms 32 via first and second torque transmission wheels 35a and 35b, and each transmission arm 32 is movably in the radial direction to provide first to third torque. It is connected to the transmission wheels 35a to 35c. Therefore, the rotations of the planet wheels 23, 23, 23 that are eccentric in different directions are transmitted to the first to third torque transmission wheels 35a to 35c almost as they are, and they are transmitted to the planet wheels 23. , 23, 23 rotate at almost the same speed. That is, each planet wheel 23, 2
3, 23 rotate in cooperation with each other and are transmitted to the first to third torque transmission wheels 35a to 35c. Then, the rotation is transmitted to the output shaft 5 via the output-side large gear 38 and the output-side small gear 39 of the third torque transmission wheel 35c. That is, the rotation from the power is transmitted to the output shaft 5.

On the other hand, the pair of sun wheels 6, 6 against which the planet wheels 23, 23, 23 are pressed against each other are rotated by operating the operating handle 9 so that the adjusting mechanism D (FIG. 2) described above makes them move to each other. It is possible to collectively and accurately adjust the amount of separation. Here, the sun wheel 6 passing through the contact point between each sun wheel 6 and each planet wheel 23
Side circumference is A. Planetary wheel 2 passing through the contact point between each sun wheel 6 and each planet wheel 23.
Assuming that the circumference on the 3 side is B, the rotation speed N of each planet wheel 23 is: N = (A−B) / B × rotation speed of the input wheel 12 (revolution speed of each planet wheel 23) By adjusting the distance between the pair of sun wheels 6 and 6, the circumferential length A on the sun wheel 6 side can be increased or decreased. That is, if the distance between the pair of sun wheels 6, 6 is increased, the circumference A is reduced, and if the distance between the pair of sun wheels 6, 6 is decreased, the circumference A is increased. Therefore, by adjusting the distance between the pair of sun wheels 6 and 6 to change the difference between the circumference A on the sun wheel 6 side and the circumference B on the planetary wheel 23 side, the rotation speed of the input shaft 4 and The ratio to the rotation speed of the output shaft 5 can be continuously changed. Moreover, for example, when the gear ratio between the input side small gear 16 and the input side large gear 15 and the gear ratio between the output side small gear 39 and the output side large gear 38 are the same, the output shaft 5 has "0". It is possible to obtain the same number of rotations as the input shaft 4 from the number of rotations “or near”.

In addition to this, the planet wheel 23 is an annulus, and as the difference between the circumference A on the sun wheel 6 side and the circumference B on the planet wheel 23 side becomes smaller, the pair of sun wheels 6, 6 and the planet wheel The rolling friction with the wheel 23 is increased. Therefore, the larger the gear ratio, the larger the torque that can be transmitted, and unlike the one described in the prior art, the gear ratio exceeding 1: 1/4 can be obtained while maintaining the high transmission efficiency. . In other words, it is possible to secure a wide torque range and a large torque over the entire range.

Further, in the present embodiment, the sun wheel 6 is provided as a pair with respect to the planet wheel 23, and the pair of sun wheels 6 and 6 are provided at both corners 23b on the inner peripheral side of the planet wheel 23. 23b
It is a two-point contact system in which (see FIG. 7) is pressed.
Therefore, the rolling friction acting on the orbiting planet wheel 23 is 2
It is doubled and a larger rotation torque can be obtained.

Further, the planet wheel 23 (the planet wheel unit 2
0) and a pair of transmission units (3 sets) each including a pair of sun wheels 6 and 6, and the rotation of each planet wheel 23 is transmitted to the output shaft 5, the transmission units are Compared with the case of one set, a large output torque can be obtained which is directly proportional to the number of units. For example, assuming that the transmission efficiency of the torque of the conventional transmission is 90%, the transmission efficiency when two transmissions are connected in series to obtain a rotation speed of 1/16 of the power is 9/10 × 9 / 10 = 81%. On the other hand, in the present embodiment, since the output torque is directly proportional to the number of transmission units, if the transmission efficiency of one transmission unit is 90%, the torque extracted to the output shaft 5 with respect to the input side shaft torque. 90% transmission efficiency
It is possible to

That is, 1 kg per transmission unit
Assuming that a torque of −m is applied and the speed is reduced to ½: output torque = input torque × reciprocal of reduction ratio × transmission efficiency, so in the above example, output torque = 1 × 2/1 × 0.9 = 1.8 kg-m. If five transmission units are arranged in parallel, the total output torque is 1.8 × 5 = 9 kg-m. The total torque applied to each transmission unit is 1
kg-m × 5 = 5 kg-m, but since the reduction ratio is 1/2, multiplying it by 2/1 of this reciprocal gives 5 × 2/1 = 10.
It becomes kg-m. Since the transmission efficiency is the total output torque / the total input torque, 9/10 = 0.9, which is 90%.

Further, since three sets of transmission units are coaxially arranged side by side and share the input wheels 12, when the number of transmission units is increased, the fixed shaft 3 and the housing 2 are arranged in the same arrangement. It is only necessary to increase the length, and most of the input shaft 4, the output shaft 5 and the peripheral parts thereof can be shared. Therefore, it is possible to obtain a large output torque without increasing the size of the main body of the apparatus with a relatively simple structure, which is convenient. Further, as described above, each planet wheel 23, 23, 23 rotates (rotates) in cooperation with each other, and the rotation is transmitted from the third torque transmission wheel 35c to the output shaft 5. Compared with the case where the rotations of the wheels 23, 23, 23 are individually transmitted to the output shaft 5, the rotations of the plurality of planet wheels 23, 23, 23 are efficiently rotated without complicating the rotation transmission mechanism. Can be transmitted to.

Further, in the present embodiment, the planetary wheel units 20 are pressed in different directions at a constant angular interval (see FIG. 6), so that the tires of an automobile can be seen when the above-mentioned operation is performed. Vibrations caused by imbalance during high-speed rotation can be suppressed.

Further, each planet wheel unit 20 is constituted so as to be urged in a predetermined direction at two locations on the same circumference by a pair of pressing units 24, 24, and the pair of sun wheels 6, 6 are desired. The structure is in a state (free state) in which the fixed shaft 3 is allowed to move in the extending direction while maintaining the state in which the position adjustment for obtaining the gear ratio is accurately performed. The processing accuracy of the friction surfaces of both wheels at the position where the wheels 6, 6 and the planetary wheel 23 contact, that is, the former friction surface 6a and the inner corners 23b, 23b of the latter, and the processing accuracy of other members, and The pair of sun wheels 6, 6 and the planet wheel 23 can be stably brought into contact with each other without assuring the assembling accuracy of each member so much, and the two-point contact state between them can be reliably ensured. it can.

That is, as shown in FIG. 4B, an axial deviation occurs between the pair of sun wheels 6 and 6 and the planet wheel 23 due to a manufacturing error or an assembly error of each component. Even if both of them are in a one-point contact state, the pair of sun wheels 6, 6 are moved within the fixed shaft 3 by the pressing force F of the pair of pressing units 24, 24. By moving together with the shaft 8 in the axial direction (arrow direction B in the illustrated example), the pair of sun wheels 6 and 6 and the planet wheel 23 are moved.
The two-point contact with and is always secured. Therefore, more stable output can be obtained, and at the same time, the cost of the device can be reduced.

That is, when the processing accuracy and the assembly accuracy are low, the contact points between the pair of sun wheels 6 and 6 and the planet wheel 23 change subtly during rotation, resulting in uneven transmission torque and rotational speed. However, a pair of pressing units 24, 2
Since the planetary wheel unit 20 can be stably pressed against the pair of sun wheels 6 and 6 by means of 4, the assembly and adjustment of the device can be made relatively easy, and at the same time, depending on the location, the processing accuracy of parts can be improved. This is because you don't have to worry too much.

Further, in the present embodiment, the pressing direction of each planet wheel unit 20 is regulated in a fixed direction by each sleeve 25 and each block 29 of the pair of pressing units 24, 24. Therefore, for example, even when the pressing forces of the pair of pressing units 24, 24 have variations in pressing force due to differences in conditions such as manufacturing error and quenching, the pressing direction of the planetary wheel unit 20 is changed. The direction can always be fixed. Therefore,
A more stable output can be obtained, and at the same time, the cost of the device can be reduced. Further, in cooperation with the configuration in which the planetary wheel unit 20 is biased in the predetermined direction at two locations on the same circumference, it is possible to effectively suppress the occurrence of the following bouncing phenomenon phenomenon.

For example, a pair of sun wheels 6, 6 and a planet wheel 23
If there is a slight circularity error or unevenness on both surfaces (the friction surface 6a of the sun wheel 6 and the inner peripheral corners 23b, 23b of the planet wheel 23) at the contact point with The pressing function of the units 24, 24 cannot follow.
Then, the planet wheel 23 momentarily separates from the pair of sun wheels 6 and 6 (bounds) and loses its original function. However, if this occurs continuously, the bound is amplified and the pressing force is increased. A phenomenon such as not working at all will occur. That is the bounce phenomenon.

Further, in the present embodiment, the friction surface 6a of the sun wheel 6 is curved and inclined in a concave shape, while the inner peripheral corners 23b and 23b of the planet wheel 23 have a pair of curvatures in the longitudinal section. The sun wheels 6 and 6 are curved with a smaller curvature than the friction surfaces 6a and 6a, and both are curved in opposite directions. For this reason, if the adjustment mechanism D (FIG. 2) is used to adjust the distance between the pair of sun wheels 6, 6 to change the gear ratio,
Not only the contact on the side of the sun wheel 6 but also the position of the contact on the side of the planet wheel 23 changes. In other words, as the pair of sun wheels 6, 6 move apart, the two contacts between them approach each other, and conversely, as the pair of sun wheels 6, 6 move closer, the two contacts move apart.
The position of one contact changes.

Therefore, the friction surfaces 6a, 6a of the pair of sun wheels 6, 6 and the corners 23b, 23b on the inner peripheral side of the planetary wheel 23.
The degree of wear during the period of use of and is low, and stable shifting performance can be maintained for a long period of time. Further, the usable period of the sun wheel 6 and the planet wheel 23 is long, and the maintenance cost of the device can be kept low. Regarding this point, contrary to the present embodiment, the pair of sun rings 6, 6
The same applies to the case where the friction surfaces 6a, 6a are convex and the inner peripheral surface of the planetary wheel 23 pressed against the friction surfaces is concave.

(Second Embodiment) Configuration FIG. 9 shows a transmission device 51 according to a second embodiment of the present invention.
FIG. The transmission 51 has a basic configuration corresponding to the planetary wheel 23 of the transmission 1 according to the first embodiment arranged inside the pair of sun wheels 6 and 6.

In outline, the transmission 51 of the present embodiment has a housing 52 forming the main body of the device, a housing 52 having one side portion (left side in the figure) and the other side portion (right side in the figure). Input shaft 53 and output shaft 54 protruding respectively
The rotation input from the power source to the input shaft 53 is transmitted to the output shaft 54 after being rotated by a plurality of sun wheels 59, a plurality of planet wheels 64, etc., which will be described later, and the rotation torque from the output shaft 54. To take out.

The details of each unit will be described below. The input shaft 53 and the output shaft 54 share the axis Q, and the output shaft 54 is supported by the housing 52 via the first and second bearings 55 and 56, while the input shaft 53 has one end thereof. The side is supported by the housing 52 via a third bearing 57, and the other end side is supported by the output shaft 54 via a fourth bearing 58.

On the inner peripheral wall of the housing 52, sun rings 59, 59, which are made of the same member as a ring (rotating body) and are paired with each other, that is, have a symmetrical shape, are arranged at a predetermined interval in the axial center Q direction. Three pairs are arranged side by side. Each sun wheel 59 is a fixed wheel according to the present invention, and a friction surface 59a is formed on the inner peripheral side of which a longitudinal section (section shown in FIG. 9) along the axis Q is curved and inclined in a concave shape. , Its friction surface 5
9a are assembled to the housing 52 in a state where the left and right sides face each other. Further, the center of rotation of each sun wheel 59 coincides with the axis Q and is connected to the adjusting mechanism E provided on the outer peripheral portion of the housing 52.

The adjusting mechanism E includes an operating handle 60, and a mechanism (not shown) moves the pair of sun wheels 59, 59 in the direction of approaching or separating from each other in accordance with the operation of the operating handle 60, and the pair of sun wheels 59. , 59 has a structure for adjusting the amount of separation. Note that any specific structure may be used as long as the rotation of each sun wheel 59 after position adjustment (after movement) can be prohibited. For example, a pair of "H" -shaped slits are provided on the housing 52 side so as to separate the pair of sun rings 59, 59, and pins protruding outward from each slit are provided on the outer peripheral portions of each sun ring 59, 59. Provided,
The pins of the pair of sun wheels 59, 59 may be reciprocally moved in the circumferential direction by operating the operation handle 60.

On the other hand, in the present embodiment, the input shaft 53 is the rotary support of the present invention, and the input shaft 53 corresponds to each pair of sun wheels 59, 59 and is independent of each other. One planet wheel unit 61, 61,
61 are assembled side by side in the axial direction. Figure 10
FIG. 10 is a partial enlarged view showing the planetary wheel unit 61 located on the rightmost side in FIG. 9. Note that the cross-sectional position in the figure is on the front side of the input shaft 53 (upper side of the drawing) unlike FIG. As shown in the figure, each planet wheel unit 61, 61, 61 includes a holding ring 62, which is a ring body loosely inserted outside the input shaft 53,
It is composed of a fifth bearing 63 fitted on the holding ring 62, and a planetary wheel 64 which is a rotating wheel of the invention fitted on the fifth bearing 63.

FIG. 11 shows, together with FIG. 10, the assembly structure of the planetary wheel unit 61 with respect to the input shaft 53, III in FIG.
FIG. 3 is a cross-sectional view taken along the line -III, in which the ring-shaped planetary wheel unit 61 is supported by the input shaft 53 by a pressing mechanism as described below, and at the same time, its rotation center P (see FIG. 12) is the shaft of the input shaft 53. It is pressed in a predetermined direction so as to be eccentric with the center Q.

That is, pressing units 65, 65 paired with each other are provided on both sides in the axial direction of the planetary wheel unit 61. Each of the pair of pressing units 65, 65 has a fixed block 66 fitted onto the input shaft 53, and the holding ring 6 of the planetary wheel unit 61 with the fixed block 66 interposed therebetween.
The first movable block 67 (FIG.
Lower side) and the second movable block 68 (upper side in FIG. 11).
And a pair of support rods 69 and 69 which form a pair with the input shaft 53 interposed therebetween, penetrate the second movable block 68 and the fixed block 66, and have their tips screwed and fixed to the first movable block 67. , Springs 70, 70 which are externally inserted to the respective support rods 69 and are contracted between the first movable block 67 and the fixed block 66 in a state where one end side thereof is accommodated in the first movable block 67. It consists of

The fixed block 66 is slidably fitted on the input shaft 53, and a key 72 fitted in a key groove 71 extending in the axial direction provided on the peripheral surface of the input shaft 53 is axially provided therein. Is fitted in from one end side. As a result, the planetary wheel unit 61 is connected to the input shaft 5 via the fixed block 66.
It is supported in a state where rotation is prohibited by 3. Alternatively, the input shaft 53 may be a spline shaft, and the fixed block 66 may be meshed with the spline shaft to prohibit the rotation of the fixed block 66 while allowing the axial movement of the fixed block 66. Further, each support rod 69 of the pair of pressing units 65 is slidable between the fixed block 66 and the second movable block 68, and the planet wheel unit 61 is
The movement direction with respect to the input shaft 53 is restricted to a predetermined direction (the diametrical direction of the input shaft 53) by the four support rods 69 on both sides of the input shaft 53 and both sides in the axial direction.

The planet wheel unit 61 is biased in the predetermined direction by each spring 70 of the pair of pressing units 65, and the planet wheel 64 at the outermost periphery thereof corresponds to the pair of sun wheels 59, 59 described above. Both friction surfaces 5
It is pressed by 9a and 59a. That is, in the present embodiment, the pressing mechanism and the guide mechanism of the present invention are realized by the pair of pressing units 65, 65.
It should be noted that the type of the spring 70 can be appropriately changed in the present embodiment as long as the above-mentioned function can be secured, and for example, a hydraulic pressure, a pneumatic cylinder or the like can be used. 12A to 12C show three planetary wheel units 6 by a pair of pressing units 65, 65.
It is a schematic diagram corresponding to FIG. 11 which showed the urging | biasing direction of 1,61,61. Each planet wheel unit 61, 61, 61
Is different from each other in the rotational direction with respect to the input shaft 53 because the positions where the above-mentioned keys 72 are fitted in the fixing blocks 66, 66 of the three pairs of pressing units 65, 65 are different.
They are urged in different directions at regular angular intervals of 0 °. In this way, by arranging the plurality of planetary wheel units 61 at equal angles, it is possible to suppress vibration caused by imbalance during high speed rotation.

Further, the shape of the outer peripheral side of the planet wheel 64 in each planet wheel unit 61 is similar to that of the first embodiment, and as shown in FIG. 10, the shape in the vertical cross section along the center of rotation is It has a trapezoidal shape with rounded corners, and both curved corner portions 64b, 64b are pressed against the friction surfaces 59a, 59a of the pair of sun rings 59, 59 at one point on the circumference. Both corners 64b, 64b are friction surfaces on the planetary wheel 64 side in the present invention, and the curvature in the illustrated vertical cross section is smaller than the frictional surfaces 59a, 59a of the pair of sun wheels 59, 59.

On the other hand, each planet wheel unit 61, 61, 61
9 and 10, each planet wheel 64 has a plurality of (six) torque transmission arms 75 provided with a roller 74 at the tip of a shaft 73 in the circumferential direction on one side surface located on the right side in FIGS.
It is projected at equal intervals on the same circumference. Further, torque transmission wheels 76 are fixed to the other side portions of the second and third planet wheels 64 from the left in FIG. 9 and are located outside the pressing unit 65 described above. The torque transmission wheel 76 is
A member in which a flange portion 76b is provided at an opening edge of a cylindrical mounting portion 76a that is bolted to the planet wheel 64,
As shown in FIG. 13, the flange portion 76b is provided with six notches 76c radially.

A roller 74 of each torque transmission arm 75 protruding from the adjacent planet wheel 64 is loosely fitted in each notch 76c, 76c, ... And each roller 74 is movable in the notch 76c. And is movable in the radial direction of the torque transmission wheel 76. As a result, FIG.
As already explained in the above, each planet wheel unit 61, 61,
Even if the rotation center P of 61 is eccentric in different directions, one of the plurality of torque transmission arms 75 of the adjacent planet wheel unit 61 and the torque transmission wheel 76 of the other planet wheel unit 61. Are always connected in the rotational direction, so that the adjacent one planet wheel unit 61 can rotate together.

Further, in the housing 52, the above-mentioned 3
The above-mentioned output shaft 5 close to the th planet wheel unit 61
A torque transmitting portion 77 having substantially the same structure as the torque transmitting wheel 76 is integrally formed on the outer periphery of the boss portion of No. 4. A plurality of notches 77c, 77c ... Are radially provided in the flange portion 77b of the torque transmitting portion 77, and the rollers 74 of the torque transmitting wheels 76 protruding from the third planetary wheel 64 are provided therein. By being housed, the third planetary wheel 64 and the output shaft 54 are connected in the rotational direction. That is, in the present embodiment, the torque transmission arm 75, the torque transmission wheel 76, and the torque transmission portion 77 of the output shaft 54 described above constitute the coupling mechanism of the present invention. motion

Next, the operation of the transmission 51 having the above structure will be described. When the input shaft 53 is rotated by power, each planet wheel unit 61, 61, 61
Rotates. At this time, each planet wheel unit 61, 61,
61 is urged by a pair of pressing units 65, 65 in different directions eccentric to the input shaft 53, and the corners 64b, 64b of the outer peripheral surface of each planet wheel 64 are separated by a pair of sun wheels 59, 59. It is pressed against the friction surfaces 59a, 59a. Therefore, each planet wheel unit 61, 61, 61 revolves together with the input shaft 53, and at the same time, each planet wheel 64, 6
4 and 64 rotate behind the input shaft 53 due to rolling friction between the corresponding sun wheels 59 and 59.

At this time, each planet wheel 64, 64, 64
Are connected to each other via a plurality of torque transmission arms 75 and torque transmission wheels 76, and each transmission arm 7
5 is connected to the torque transmission wheel 76 so as to be movable in the radial direction. Therefore, the planet wheels 64, 64, 64 cooperate with each other in an eccentric state in different directions and rotate at substantially the same speed. Then, the rotation is transmitted to the output shaft 54 via the torque transmitting portion 77. That is, the rotation from the power is transmitted to the output shaft 54. Here, each planet wheel 64,6
Assuming that the torque produced by each of the motors 4 and 64 is 1 kg-m, the torque transmitted to each of the torque transmission wheels 76, 76, 76 is also 1 kg-m, and finally, the total of 3 kg-m of them. The torque is transmitted to the output shaft 54.

On the other hand, the pair of sun wheels 59, 59 to which the planet wheels 64, 64, 64 are pressed are rotated by operating the operation handle 60 to adjust the above-mentioned adjustment mechanism section E.
With this, it is possible to collectively and accurately adjust the amount of separation from each other. Therefore, the pair of sun wheels 59, 59
By adjusting the amount of separation between the two, and changing the difference between the circumference of the sun wheel 59 side and the circumference of the planet wheel 64 side that are in pressure contact with each other, the same principle as that described in the first embodiment is used. ,
The ratio between the rotation speed of the input shaft 53 and the rotation speed of the output shaft 54 can be continuously changed.

That is, the transmission 5 in the present embodiment
1 has the same basic configuration as that of the first embodiment except that the pair of sun wheels 59, 59 are arranged outside the planet wheel 64, and transmits rotation by the same principle. Gear shifting can be performed. Therefore, also in the present embodiment, it is possible to obtain a wide shift range and obtain a large torque over the entire shift range. In addition, the planetary wheel 64 is a ring, and it is a two-point contact system in which it is pressed against both the pair of sun wheels 59, 59, and the corners 64b, 64b of the outer peripheral surface of the planetary wheel 64.
Since the shape and the relationship between the pair of sun wheels 59, 59 and the friction surfaces 59a, 59a are the same as those in the first embodiment, the effects by them can be similarly obtained.

Further, in the present embodiment, the planet wheel unit 61 has the input shaft 5 by the pair of pressing units 65, 65.
Both sides of A3 and both sides in the axial direction are urged, and at the same time, the urging direction is restricted to a fixed direction. Further, the planet wheel unit 61 is connected to the input shaft 5 via the fixed block 66.
3 is supported in a state in which rotation is prohibited, is slidable on the input shaft 53, and is allowed to move in the axial center Q direction when the position adjustment of the pair of sun wheels 59, 59 is accurately performed. In the opened state (free state), that is, similarly to the above-described first embodiment, the pair of fixed wheels and rotating wheels in the present invention are allowed to move relative to each other in the axial direction. It has a structure.

Therefore, similarly to the first embodiment, the pair of sun wheels 59, 59 and the planet wheel 64 can be stabilized without making the machining accuracy of parts and the assembly accuracy of each member very high. Can be brought into contact with each other, and a two-point contact state between them can be reliably ensured. Therefore, more stable output can be obtained, and at the same time, the cost of the device can be reduced. At the same time, the pair of pressing units 65, 65
Even if the pressing force varies among the plurality of springs 70, 70, ... That constitute the pressing force due to differences in conditions such as manufacturing error and quenching, the pressing direction of the planet wheel unit 61 should always be a constant direction. You can Therefore, more stable output can be obtained, and at the same time, the cost of the device can be reduced. Further, it is possible to effectively suppress the occurrence of the above-mentioned bounce phenomenon.

Further, the transmission 5 in the present embodiment
In the first embodiment, since the pair of sun wheels 59, 59 are arranged outside the planetary wheels 64 as described above, the following advantages are obtained when compared with the transmission 1 in the first embodiment. There is.

That is, considering the case where the external dimensions of the device are the same, the outer peripheral surface of the planet wheels 64 that are pressed against each other,
Also, the circumferential length of the inner circumferential surface of the pair of sun wheels 59, 59 can be increased. That is, it is possible to increase the radius of curvature of the both in the press contact portion and increase the rolling friction generated between the two. Therefore, it is possible to secure a larger output torque without increasing the size of the device.

Further, as described above, by using the input shaft 53 as the rotary support of the present invention, the planet wheel 64 is
It is possible to arrange the input shaft and the output shaft coaxially without reducing the number of members for revolving the shaft and complicating the entire structure. Therefore, the cost reduction of the device and the convenience during use can be secured at the same time. Moreover,
Since the adjusting mechanism portion E for adjusting the distance between the pair of sun wheels 59, 59 can be provided on the outer peripheral portion of the housing 52, the design is easy and the degree of freedom in design is wide. This also makes it possible to reduce the cost of the device.

In the present embodiment, the adjustment mechanism E described above moves the pair of sun wheels 59, 59 in the direction of moving toward or away from each other.
Since each planet wheel unit 61, 61, 61 is movable in the axial direction and is always urged outward,
The configuration may be such that only one side of the pair of sun wheels 59, 59 is moved. Even in that case, the two-point contact state between each planet wheel 64 and the pair of sun wheels 59, 59 can be maintained. In this respect, the same applies to the transmission 1 described in the first embodiment.

In the first embodiment, the first to third torque transmission wheels 35a to 35c having independent structures are provided, but the first and second torque transmission wheels 3 are shown.
As for 5a and 35b, the torque transmission wheel 76 may be attached to one side of the planet wheel 23 as shown in the second embodiment. In that case, the torque transmission arm 3
The number of parts such as 2 can be reduced.

[0083]

As described above, in the invention of claim 1, the rotation from the power is transmitted to the output shaft by utilizing the rolling friction between the fixed wheel and the rotating wheel, and the gear ratio is adjusted by the adjusting mechanism. Can be changed, and further, as the gear ratio increases, the rolling friction increases, so that a large torque can be transmitted even when the gear ratio is large. Therefore, it is possible to have a wide shift range and to secure a large torque over the entire range.

Further, in the invention of claim 2, the revolving rotary wheel and the fixed wheel are in a two-point contact state, and the rolling friction between both is doubled. Therefore, a larger output torque can be obtained.

Further, in the inventions of claims 3 and 4, even if it is not necessary to secure a very high processing accuracy on the friction surfaces of both wheels at the position where the fixed wheel and the rotating wheel are in contact with each other and the fitting portions of the respective members, The rotating wheel and the fixed wheel can be brought into stable contact with each other. Therefore, it is possible to obtain a more stable output and to reduce the cost of the device.

Further, in the invention of claim 5, the degree of wear of the friction surfaces of both wheels during use is reduced. Therefore, stable shift performance can be maintained for a long period of time. At the same time, by improving the durability of the rotating wheel and the fixed wheel, the maintenance cost of the device can be kept low.

Further, in the invention of claim 6, a large output torque corresponding to the number of fixed wheels and rotating wheels can be obtained with a relatively simple structure and without increasing the size of the apparatus. I was able to do it. Therefore, usability is improved.

Further, according to the invention of claim 7, the rotation is transmitted to the output shaft by the rotation of the plurality of rotating wheels in cooperation with each other. Therefore, the rotations of the plurality of rotary wheels can be efficiently transmitted to the output shaft without complicating the transmission mechanism.

Further, in the invention of claim 8, the above effect can be obtained in the structure in which the fixed wheel is arranged inside the rotary wheel.

In the ninth aspect of the invention, the position of the fixed ring can be accurately adjusted in the structure in which the fixed ring is arranged inside the rotary wheel. In addition, when there are a plurality of pairs of fixed wheels or a plurality of fixed wheels and rotating wheels, the positions of the plurality of fixed wheels can be adjusted collectively and accurately.

According to the tenth aspect of the invention, it is possible to secure a larger radius of curvature on both the friction surfaces of the fixed wheel and the rotating wheel that are in pressure contact with each other without increasing the outer dimensions. . Therefore, the rolling friction generated between the fixed wheel and the rotating wheel can be increased, and a larger output torque can be secured without increasing the size of the device. Further, the number of members for revolving the rotary wheel is reduced, and the input shaft and the output shaft can be arranged coaxially without complicating the entire structure. Therefore, the cost reduction of the device and the convenience during use can be secured at the same time.

[Brief description of drawings]

FIG. 1 is a vertical cross-sectional view showing a first embodiment of the present invention with simplified details.

FIG. 2 is an assembly cross-sectional view showing a main part of the adjusting mechanism in the same embodiment.

FIG. 3 is a perspective view showing a moving shaft and a moving key in the same embodiment.

FIG. 4 is a partial cross-sectional view showing a main part of the adjusting mechanism in the same embodiment, in which (A) shows a state in which there is no axial deviation between the pair of sun wheels and the planet wheels. Figure,
(B) is an explanatory view in the case where an axial deviation occurs between the pair of sun wheels and the planet wheels.

5 is a cross-sectional view taken along line I-I of FIG.

FIG. 6 is a schematic diagram corresponding to FIG. 5 showing the urging direction of each planet wheel unit.

FIG. 7 is a partially enlarged view of FIG.

8 is a cross-sectional view taken along the line II-II in FIG.

FIG. 9 is a vertical cross-sectional view showing a second embodiment of the present invention with simplified details.

FIG. 10 is a partially enlarged view of FIG.

11 is a cross-sectional view taken along the line III-III in FIG.

FIG. 12 is a view showing the urging direction of each planet wheel unit.
It is a schematic diagram corresponding to.

13 is a cross-sectional view taken along the line IV-IV in FIG.

FIG. 14 is a diagram showing the principle of a conventional transmission.

[Explanation of symbols]

1 transmission 3 fixed axis 3a key hole 4 input axes 5 output shafts 6 sun wheel 6a Friction surface 8 axis of movement 10 Move key 12 input wheels 20 Planetary wheel unit 23 Planetary wheels 23b Corner (inner side of planet wheel) 24 Pressing unit 28 direction control pin 32 torque transmission arm 35a-35c 1st-3rd torque transmission wheels 38 Output side large gear 39 Output small gear 51 transmission 53 Input axis 54 Output shaft 59 sun wheel 59a Friction surface 61 Planetary wheel unit 64 planet wheels 64b (outer peripheral side of planet wheel) 65 Pressing unit 75 Torque transmission arm 76 torque transmission wheel 77 Torque transmission section D adjustment mechanism E adjustment mechanism O (input wheel) center of rotation P (planetary wheel unit) center of rotation Q axis (of input shaft)

Claims (10)

[Claims] 1. A rotary support body that rotates by input power, and a rotary body that is arranged with its rotation center aligned with the rotation support body, wherein a friction surface whose longitudinal section along the rotation center is inclined is a peripheral surface. A fixed ring that is provided on the fixed ring, is allowed to move in the extending direction of the rotation center, and is prohibited from rotating; an adjusting mechanism that adjusts the position of the rotation center in the extending direction of the fixed ring; A rotary ring, which is rotatably assembled to the body in a direction opposite to that of the rotary support, and has a friction surface having a circular cross section orthogonal to the center of rotation on the peripheral surface, and the rotary ring. A pressing mechanism that presses the rotating support member in a predetermined direction to be eccentric and presses the peripheral surface of the rotating wheel against the peripheral surface of the fixed wheel; and an output shaft to which rotation of the rotating wheel is transmitted. Transmission characterized by. 2. The fixed wheels are provided as a pair in the extending direction of the center of rotation, and the adjusting mechanism is a mechanism for adjusting the distance between the pair of fixed wheels.
The described transmission. 3. The transmission according to claim 1, wherein the pressing mechanism presses the rotating wheel in a predetermined direction at a plurality of locations on the same circumference. 4. The transmission according to claim 1, wherein the pressing mechanism includes a guide mechanism that regulates a pressing direction of the rotary wheel in a constant direction. 5. A shape of a vertical cross section taken along the center of rotation between the friction surface of the fixed wheel and the friction surface of the rotating wheel,
The transmission according to any one of claims 1 to 4, wherein the transmission has a shape that curves in mutually opposite directions. 6. A plurality of fixed wheels that share the rotary support and the rotary wheel are arranged in parallel along a rotation center, and a transmission mechanism that transmits the rotation of each rotary wheel to the output shaft is provided. Any one of claims 1 to 5 characterized in that
The transmission according to paragraph. 7. The transmission according to claim 6, wherein the transmission mechanism includes a connecting mechanism that connects the rotating wheels adjacent to each other while allowing relative movement in the eccentric direction. 8. The rotary support is hollow, the rotary wheel is assembled inside the rotary support, the fixed wheel is arranged inside the rotary wheel, and the friction surface is provided on the inner peripheral side of the rotary wheel. 8. The transmission according to claim 1, wherein the friction surface is provided on the outer peripheral side of the fixed wheel. 9. The adjusting mechanism is a tubular member that is fitted onto the fixed ring while the fixed ring is slidable in the position adjusting direction and is prohibited from rotating, and is a key extending in the position adjusting direction. A fixed shaft having a hole opening on the peripheral surface, and a fixed shaft that is rotatably fitted in the fixed shaft in both forward and reverse directions, and is rotated when adjusting the position of the fixed ring, and the peripheral surface corresponding to the key hole of the fixed shaft. A moving shaft provided with a threaded portion in a predetermined region, meshes with the threaded portion of the moving shaft from the outside of the fixed shaft through the key hole, and moves in the position adjusting direction toward the center of the fixed ring. 9. The transmission according to claim 8, further comprising a moving key fitted from one side. 10. The fixed ring is mounted on the outer side of the rotary support, the fixed ring is arranged outside the rotary ring with the fixed ring as an annular body, and the friction surface is provided on the outer peripheral side of the fixed ring. The transmission according to any one of claims 1 to 7, wherein the friction surface is provided on an inner peripheral side of the.