JP2002039308A - Friction type transmission - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a friction type transmission suitably applicable to high-speed vehicles. SOLUTION: The friction type transmission includes a planet wheel 5 made to rotate about its own axis by the rotation of a sun wheel 4 which rotates concentrically and together with a first shaft 2; a first drive wheel 6 which rotates while abutting the planet wheel 5; a second drive wheel 9 which rotates together with the first shaft 2; a rotor which abuts and rotates about the first and second drive wheels 6 and 9 while rotating about its own axis; a transmission wheel 10 which rotates about the first shaft 2 with the inner peripheral surface of the transmission wheel abutting the surface of the rotor 7; a transmission means for transmitting the rotation of the transmission wheel 10 to a second shaft 3; and an abutting position changing means 12 for changing the abutting position of the transmission wheel 10 relative to the rotor 7 in the radial direction of the rotor 7, with all of these members being provided within a predetermined casing 14. The planet wheel 5 is journaled in position in a manner allowing its free rotation about a roller support shaft 53 fixed within the easing 14, and the first and second drive wheels 6 and 9 have their respective peripheral speeds set so that a neutral position where the transmission wheel 10 is not rotated is located near the center of the rotor 7.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a friction type transmission which is improved so as to be suitably applied to a high-speed vehicle such as an automobile.

[0002]

2. Description of the Related Art Conventionally, a friction type transmission as disclosed in Japanese Patent Application Laid-Open No. 61-218864 has been known. This transmission changes the speed of rotation input about the axis of the input shaft and transmits it to the output shaft concentric with the input shaft by frictional force. A plurality of conical rotators arranged obliquely around the transmission wheel, a large-diameter transmission wheel that rotates around the input shaft by friction transmission by abutting against the back side of this conical rotator, A speed change ring that rotates around the input shaft in contact with the conical surface of the conical trochanter, and a plurality of planetary gears that revolve around the sun gear fixed to the input shaft by rotation of the large-diameter transmission wheel while revolving around the sun gear. An input shaft and an output shaft concentric with the carrier supporting the planetary gear.

The speed change ring can be moved forward and reverse in parallel with the input shaft while operating on the operating lever while abutting on the conical surface of the conical trochanter. By changing the contact position of the speed change ring with respect to, the contact position moves away from or near the center of the conical surface, so that the rotation speed and revolving speed of the conical rotator increases and decreases, thereby causing large diameter transmission The number of revolutions of the car can be changed.

[0004]

In the above-mentioned conventional friction type transmission, the output shaft is directly connected to the carrier of the planetary gear, and the conical rotation is performed with the transmission ring not rotating. By changing the contact position of the speed change ring with respect to the conical surface of the child, both the rotation speed and the revolving speed of the conical trochanter are changed, and the rotation speed of the output shaft changes accordingly. And, since the revolving speed increases as the speed change ring shifts the contact position to the large diameter side of the conical trochanter, the centrifugal force generated by the revolving increases at an accelerating rate with the increase of the revolving speed, and However, the contact position of the transmission ring is greatly deviated from the center of gravity of the conical trochanter, and it becomes difficult to maintain the balance of the conical trochanter.
There is a problem that the rotational speed ratio cannot be secured. That is, if a rotation speed suitable for friction transmission cannot be secured, the transmission of rotational force becomes unstable, and it is difficult to always obtain a stable rotational output with high transmission efficiency.

Further, the rotation of the input shaft causes the plurality of planetary gears and conical rotators to revolve around the sun gear and the small-diameter transmission vehicle, so that the lubricating oil loaded in the casing is agitated. Since the revolution of the planetary gear and the conical rotator becomes unstable due to the generated stirring resistance, there is also a problem that it is difficult to obtain high transmission efficiency.

In particular, this problem becomes conspicuous when the output shaft is set in a low speed range. That is, the so-called neutral position on the generatrix of the conical trochanter, at which the transmission ring does not rotate, is set at a position away from the center position of the conical trochanter.
The triangle connecting the contact points of the large-diameter transmission and the transmission ring is distorted, and the center of gravity of this triangle and the center of gravity of the conical trochanter deviate greatly. As a result, the rotational force of the input shaft cannot be reliably transmitted in the low-speed range of the output shaft.

[0007] As described above, the conventional friction type transmission has been applied to low-speed vehicles such as wheelchairs in which running and stopping are repeated at a relatively low speed due to many problems. It could not be applied to high-speed vehicles such as cars.

SUMMARY OF THE INVENTION The present invention has been made to solve the above problems, and has high rotational transmission efficiency, can obtain a more stable rotational output, and can perform high-speed input. It is another object of the present invention to provide a friction type transmission suitable for application to a high-speed vehicle.

[0009]

According to the first aspect of the present invention,
A friction transmission in which a rotation input about an axis of a first shaft is shifted and transmitted to a second shaft concentric with the first shaft by frictional force,
The first drive wheel and the second drive wheel, one of which rotates concentrically with the first shaft and the other rotates in the reverse direction, and the back surface of which contacts the outer peripheral surfaces of the first drive wheel and the second drive wheel, thereby performing both drive. A conical rotor that revolves around its first axis while revolving around a first axis due to a peripheral speed difference between the wheels, and an inner peripheral surface that abuts on a generatrix of a conical surface of the rotor and rotates around the first axis. A transmission wheel movable in the axial direction of the shaft; and transmission means for transmitting rotation of the transmission wheel to a second shaft, wherein the first and second drive wheels are arranged so that the mother wheel does not rotate the transmission wheel. The peripheral speeds are set so that the neutral position on the line is set to a position near the center of the rotor.

According to the present invention, the rotation of the first shaft around the axis is such that one of the first shafts rotates forward and the other rotates reversely.
The driving force is transmitted to the driving wheel and the second driving wheel, and the back side is transmitted to the rotor that is in contact with the outer peripheral surfaces of the first and second driving wheels. Revolves while revolving around. The speed change wheel whose inner peripheral surface is in contact with the generatrix of the conical surface of the rotor rotates around the first axis in any direction depending on the balance between the revolution of the rotor and the rotation.

In the first and second drive wheels, the neutral position on the generating line that does not rotate the transmission wheels is set to a position near the center of the rotor (the vertex of a cone forming the rotor). In the state where the speed change wheel is located at the neutral position, the first speed with respect to the rotor is
And a triangle formed by connecting the respective contact positions of the second drive wheel and the transmission wheel has a shape close to a substantially isosceles triangle,
The force is applied to the rotor in a very good balance, so that the transmission efficiency of the rotational force of the second shaft in the low speed range is stabilized.

[0012] Further, since the neutral position of the rotor on the generatrix is located in the vicinity of the center of the rotor, the first and second positions can be set.
The difference in peripheral speed between the drive wheels is reduced, and the rotor is suppressed from revolving.The rotating wheels are rotated by the rotation, so that the lubricating oil filled in the casing revolves around the rotor. Thus, the stirring resistance caused by the stirring can be significantly reduced as compared with the related art, thereby also improving the transmission efficiency of the rotational force.

According to a second aspect of the present invention, in the first aspect of the present invention, the first drive wheel has a first outer peripheral surface and a second outer peripheral surface having a diameter larger than the first outer peripheral surface. The outer peripheral surface is the first
Around the center of the sun roller concentrically rotating with the axis, the sun roller rotates around the first axis by abutting on the outer peripheral surface of the planetary roller that rotates only by rotation of the sun roller, and the second outer peripheral surface is The second drive wheel is configured to be in contact with a rotor, the second drive wheel is fixed to a first shaft concentrically and corotatably, and a contact position of the transmission wheel with respect to the rotor is changed in a radial direction of the rotor. It is characterized in that contact position changing means is provided.

According to the present invention, the rotational force applied to the first shaft is a sun roller integrated with the first shaft, a planetary roller arranged around the center of the sun roller, and a planetary roller having the first outer peripheral surface. Is transmitted to the rotor via the first drive wheel which is in contact with the first shaft, and is also transmitted by rotation of the second drive wheel integrated with the first shaft, whereby the rotor is always rotated around the center of rotation by the first shaft. And revolve at the same speed ratio. When the effective diameter of the rotor (the distance from the center position of the rotor to the position where the transmission wheel is in contact) changes due to the change in the contact position of the transmission wheel with respect to the rotor, the transmission wheel is brought into the contact position. Will rotate at a predetermined rotational speed ratio with respect to the first shaft.

The planetary roller rotates by the rotation of the sun roller but does not revolve. Therefore, the lubricating oil filled in the casing is agitated by the revolution of the planetary roller, and imparts agitating resistance to the planetary roller. Second
It is possible to reliably suppress the occurrence of inconvenience such as unstable rotation of the shaft.

Further, the planetary rollers are not revolved,
By not increasing the difference in peripheral speed between the first drive wheel and the second drive wheel, the revolution speed of the rotor becomes low, so that problems such as instability of the contact state due to centrifugal force and stirring resistance are caused. As a result, the transmission of the rotational force with high transmission efficiency that is always stable between the first and second shafts is achieved.

Since the first drive wheel has, on its outer peripheral surface, a first outer peripheral surface corresponding to a planetary roller and a second outer peripheral surface corresponding to a rotor, the diameter of each of these outer peripheral surfaces is adjusted appropriately. , The peripheral speed can be made substantially the same as the peripheral speed of the second drive wheel. When the peripheral speeds of the driving wheels become substantially the same, the rotor mainly rotates in a stable state with the revolution suppressed as much as possible, so that the transmission can withstand high-speed rotation of the first shaft and the second shaft. become.

According to a third aspect of the present invention, in the first aspect of the present invention, the first drive wheel has a gear concentric with the first shaft, and the gear rotates concentrically with the first shaft. The gear is configured to rotate around a first axis by meshing with a planetary gear that performs only rotation through an idle gear through rotation of an idle gear, and an outer peripheral surface of the gear is in contact with the rotor. A contact position changing means fixed concentrically and corotatably to the first shaft and changing a contact position of the transmission wheel with respect to the rotor in a radial direction of the rotor is provided. .

According to the present invention, the sun roller and the planetary roller according to claim 2 are replaced with a sun gear and a planetary gear, respectively, and the rotation of the sun gear is transmitted to the planetary gear via the idle gear. This point is different from the second aspect of the invention only, and has the same effect as the second aspect of the invention. However, as a function unique to the invention of claim 3, no slip occurs between the gears, and the transmission efficiency of the rotational force is improved.

According to a fourth aspect of the present invention, in the first aspect of the present invention, the first shaft and the second shaft are connected to each other.
Between the shafts, there is a clutch mechanism that joins the first shaft and the second shaft at the same rotation speed while separating the first shaft and the second shaft at different rotation speeds. It is characterized by being interposed.

According to the present invention, the first shaft and the second shaft are joined by the clutch mechanism so that they can rotate together in a high-speed shift state in which the first shaft and the second shaft have reached the same rotational speed. The rotational force transmission efficiency between the first shaft and the second shaft becomes 100%.

[0022]

FIG. 1 is an exploded perspective view, partially cut away, showing an embodiment of a friction type transmission according to the present invention, and FIG. 2 is an assembled perspective view thereof. FIG. 3 is a sectional view taken along line AA of FIG. In the present specification, the rotation axis itself serving as the rotation center is the first axis 2 or the second axis 3.
Rotating around is called revolution, and other rotations are called rotation. The term “rotation” simply refers to one or both of revolution and rotation.

As shown in FIGS. 1 to 3, the friction type transmission 1 of this embodiment functions as an input shaft when used as a speed reducer and as an output shaft when used as a speed increaser. A first shaft 2 that carries the light, a second shaft 3 that operates in the opposite direction to the first shaft 2, a sun wheel (sun roller) 4 that is concentric with and coaxial with the first shaft 2, and is arranged around the center of the sun wheel 4. A planetary wheel (planetary roller) 5 that rotates by its rotation about its axis, a first drive wheel 6 that rotates around the first shaft 2 with a part of the outer peripheral surface contacting the planetary wheel 5, A plurality of rotors 7 to which the rotation of the drive wheels 6 is transmitted by frictional force, a rotor support member 8 that supports each of the rotors 7, and the rotation of the rotor 7 in cooperation with the first drive wheels 6 described above. The second drive wheel 9 revolves together with the inner peripheral surface, which can slide in the axial direction of the first shaft 2 while being in contact with the surface of the rotor 7. A transmission wheel 10, a transmission means 11 for transmitting the rotation of the transmission wheel 10 to the second shaft 3, and a contact member for sliding the transmission wheel 10 to change the contact position between its inner peripheral surface and the surface of the rotor 7. The contact position changing means 12 and the clutch mechanism 13 interposed between the first shaft 2 and the second shaft 3 are formed by being provided inside or outside the casing 14.

The casing 14 has a tubular casing 141 having a bottom and a tubular shape, and the tubular casing 141.
And a circular lid 145 that closes the opening. The cylindrical casing 141 includes an annular wall 142 and a side plate 143 having one side of the annular wall 142 closed. The annular wall 142 has a bulging portion 142a whose upper portion bulges upward, and the contact position changing means 12 is provided inside the bulging portion 142a.

At the center of the side plate 143, the second shaft support cylinder 1 supporting the second shaft 3 via two bearings B
Reference numeral 44 projects outward. In addition, the annular wall 14
An annular edge 142 having the same width dimension and protruding radially inward is provided on an edge of the second shaft support cylinder 144 opposite to the second shaft support cylinder 144.
b is provided.

The lid 145 is formed on a shallow cylindrical lid body 146 whose diameter is set slightly smaller than the diameter of the cylindrical casing 141, and is formed on the opening edge of the lid body 146. Flange 147 and first shaft support tube 14
It consists of eight. On the inner surface side of the flange portion 147,
An annular projection 147a is provided concentrically and protruding into the cylindrical casing 141. This annular projection 147a
The outer diameter is set slightly smaller than the inner diameter of the annular edge 142b, and the flange 147 is bolted to the annular edge 142b with the annular projection 147a fitted into the annular edge 142b. The lid 14
5 is fixed to the cylindrical casing 141.

An insertion hole through which the first shaft 2 is inserted is formed in a bottom plate portion of the first shaft support cylinder 148.
An annular oil seal 148a is mounted. The first shaft 2 is supported via a bearing B housed in the first shaft support tube 148 in a state penetrating the oil seal 148a, and has a distal end projecting outward as shown in FIG.

The first shaft 2 includes a shaft main body 21 at a central portion,
The shaft main body 21 includes a small-diameter portion 22 extending concentrically rightward from the right end in FIG. Small diameter part 2
A first annular groove 23 is recessed at an appropriate position on the outer peripheral surface of the shaft 2, and a second annular groove 24 is recessed at the left end of the shaft body 21. The annular grooves 23 and 24 are for feeding hydraulic oil to the clutch mechanism 13 described in detail later, and are slidably contacted with the small diameter portion 22 of the first shaft 2.
3. Coupling 2 for feeding hydraulic oil so as to surround 3
9 (FIG. 2) is attached, and through this coupling 29,
The first annular groove 23 of the rotating first shaft 2 and the shaft passage 2
6 (FIG. 3) and the hydraulic oil are fed into the clutch mechanism 13 through the second annular groove 24.

In the present embodiment, the first driving wheel 6 has a circumferential speed of the large-diameter cylindrical body 62 that is equal to the circumferential speed of the second driving wheel body 91, which will be described later. 0.0 times ~
It is set to a value within the range of 3.0 times. Such a peripheral speed of the large-diameter cylinder 62 is set when the peripheral speed of the large-diameter cylinder 62 is lower than the peripheral speed of the second driving wheel main body 91 (that is, when the peripheral speed is lower than 1.0 times). The revolving direction of the rotor 7 is the same as the direction of rotation of the first shaft 2, whereby the second shaft 3 does not rotate despite the rotation of the first shaft 2. When it is larger than 3.0 times, the revolution speed of the rotor 7 becomes too high,
This is because the resistance between the lubricating oil loaded in the casing 14 and the revolving rotor 7 increases, and the transmission efficiency of the rotational force decreases.

The second shaft 3 is a shaft main body 2 of the first shaft 2.
1 and a shaft body 31 having a slightly larger diameter than FIG.
And a small-diameter portion 32 protruding concentrically from the left end surface of the diaper. The second shaft 3 is connected to the second shaft 3 in a state where the bearing B is fitted around the substantially central position of the small diameter portion 32 and the left position in FIG.
By passing through the shaft support tube 144, the second shaft 3 is supported by the second shaft support tube 144 of the cylindrical casing 141 via the two bearings B, whereby the second shaft 3 and the lid 145 are connected to each other. The mounted first shaft 2 can rotate relative to each other around the axis.

The end surface of the shaft body 31 of the second shaft 3 has
A fitting hole 34 for fitting a cylindrical slide bearing 33 is formed in a concave shape, and clutch teeth 35 formed in a sawtooth shape at an equal pitch over the entire periphery are provided at the edge. The clutch teeth 35 constitute a part of the clutch mechanism 13.

The sun ring 4 includes a sun ring main body 41 fitted around the shaft main body 21 of the first shaft 2 so as to be corotatable therewith, a sun disk 42 formed concentrically with the sun ring main body 41 and integrally therewith, An annular ring 43 is provided to protrude from the outer periphery of the solar disk 42 to the left in FIG. 3. The inner peripheral surface of the annular ring 43 is formed with an annular contact surface 43 a that is inclined to widen and contacts the outer peripheral surface of the planetary wheel 5. The diameter of the sun ring 4 and the length in the axial direction are set so that the sun ring 4 can be housed in the lid main body 146.

The outer peripheral surface of the planetary wheel 5 is the annular ring 43.
Is formed by a roller so that the rotation of the sun wheel 4 can be transmitted by contacting the contact surface 43 a formed on the inner peripheral surface of the sun wheel 4.
A first annular contact surface 51 is formed so as to be inclined so as to contact the annular contact surface 43a, and a second annular contact surface 52 inclined in the opposite direction is formed on the opposite surface. Is formed.

The planet wheel 5 is fitted via a sliding bearing onto a press-fit shaft (roller support shaft) 53 which is press-fitted and fixed at equal pitches on the same circular locus about the center of the hole of the annular support disk 54, It is rotatably supported around the press-fit shaft 53.
The support disk 54 has a small-diameter cylindrical body 61 whose inner diameter is described later.
Are set so that they can be inserted in a sliding contact state, and the outer diameter is set slightly smaller than the inner diameter of the annular projection 147a of the lid 145.
7a, the first annular contact surface 51 of the planetary wheel 5 is connected to the annular contact surface 43 of the sun wheel 4 by screwing.
a in the state of being abutted on the cover main body 146. In the present embodiment, three planet wheels 5 are provided on the support disk 54.

According to such a configuration of the planetary wheel 5, since the sun wheel 4 rotates together with the first shaft 2 around the axis, the rotational force is applied to the annular contact surface 43a of the sun wheel 4 and the annular surface. The rotation is transmitted to the planetary wheel 5 via the first annular contact surface 51 that is in contact with the contact surface 43a as rotation in the same direction.

The first drive wheel 6 contacts each second annular contact surface 52 of the three planet wheels 5 and rotates around the first shaft 2, and transmits this rotation to the rotor 7. Rotor 7
The second annular contact surface 52 of the planetary wheel 5
, And a large-diameter cylinder 62 integrally connected to the small-diameter cylinder 61. Small diameter cylinder 6
Numeral 1 is for transmitting the rotation of the planetary wheel 5 to the first drive wheel 6, and the large-diameter cylinder 62 abuts on the periphery of the rotor 7 to apply the rotation of the large-diameter cylinder 62 to the frictional force. For transmitting to the rotor 7. The first drive wheel 6 is connected to the first shaft 2
, And rotates in a direction opposite to the first shaft 2 in a speed increasing state.

On the outer peripheral surface of the large-diameter cylindrical body 62,
An annular recess 63 is formed in a portion facing the edge of the rotor 7, and the first drive wheel 6 is extended by extending the contact length between the two by fitting the edge of the rotor 7 into the annular recess 63. The transmission efficiency of the rotational force to the rotor 7 is improved.

The rotor 7 has a conical body 71 having a conical shape, a friction disk 72 integrally formed on the bottom surface of the cone 71, and a vertical projection from the center of the friction disk 72. It consists of a top axis 73. Friction disk 72
Has an arc edge 72a whose outer peripheral edge is formed in an arc shape in a side view as shown in FIG. This arc edge 72
“a” is formed in order to increase the contact length of the friction disk 72 with the first drive wheel 6 to obtain a reliable frictional force. In the present embodiment, four rotors 7 are provided.

The rotor support member 8 supports the rotor 7 so as to be rotatable around the top axis 73, and has an annular disk 81 and a radial dimension from the periphery of the annular disk 81 to the left. And an annular flapper cylinder 82 extending so as to gradually increase. The wrapper cylinder 82 is provided with four mounting holes 83 at equal pitches in the circumferential direction, and the top shaft 73 is inserted into the mounting holes 83 in a slidable state, so that the rotor 7 rotates around the top shaft 73. It is rotatably mounted on the rotor support member 8. In addition, a center hole 84 is provided at the center of the annular disk 81 to insert a part of the second drive wheel 9 in a sliding contact state.

Then, as shown in FIG.
Of the cone 71 with respect to the friction disk 72 is set to the same angle as the inclination angle β of the cone 71 with respect to the first shaft 2 so that the rotor 7 is mounted on the rotor support member 8 so that the cone 71 Are parallel to the first axis 2.

The second driving wheel 9 drives the rotor 7 to rotate around the top axis 73 in cooperation with the first driving wheel 6 by contacting the peripheral surface of the second driving wheel 9 with the bottom surface of the friction disk 72. The rotor 7 is rotated by the difference between the rotation speed of the first drive wheel 6 and the rotation speed of the first drive wheel 6 due to the co-rotation of the rotor 7 with the first shaft 2.
Play a role to rotate around. Therefore, as long as the rotation speed of the first shaft 2 does not change, the rotor 7 always revolves while rotating at the same rotation speed.

The second drive wheel 9 is composed of a second drive wheel main body 91 fitted around the first shaft 2 so as to be rotatable around the first shaft 2 and a cylindrical body 92 formed on the right side of the second drive wheel main body 91. Has become. The cylindrical body 92 has an outer diameter dimension of the rotor support member 8.
Is set slightly smaller than the inner diameter of the center hole 84 so that the cylindrical body 92 can be fitted into the center hole 84 in a sliding contact state.

Further, on the periphery of the second drive wheel main body 91,
A contact surface 93 is provided on the back surface of the rotor 7 so as to be in close contact with the back surface of the rotor 7. The contact surface 93 is pressed against the back surface of the rotor 7, so that the rotation of the second drive wheel 9 is reliably performed on the rotor 7. It is made to be transmitted to.

The speed change wheel 10 changes the rotational speed around the first shaft 2 by changing the contact position with respect to the cone 71 and transmits the change to the second shaft 3. The transmission wheel 10 includes an annular transmission wheel main body 101 and a drive wheel housing cylinder 102 for accommodating a second driving wheel main body 91 protruding leftward concentrically from the left surface of the transmission wheel main body 101 in FIG. And a female spline cylinder 103 projecting leftward from the drive wheel storage cylinder 102.

The speed change wheel main body 101 is dimensioned so as to abut against the generatrix of the cone 71 of the rotor 7 having the inner diameter of four. The rotor 7 has its surface in contact with the first drive wheel 6 and the second drive wheel 9, and by this contact, the number of rotations around the top axis 73 and the revolution around the first axis 2 is set to be constant. Have been. On the other hand, the speed change wheel 10
The contact position with respect to the rotor 7 can be changed by operating the contact position changing means 12. When the contact position with respect to the rotor 7 changes, the distance between the center of the rotor 7 and the contact position, that is, the speed of the rotor 7
Are different, the speed of the transmission wheel 10 changes.

The driving wheel housing cylinder 102 has a length in the axial direction substantially equal to the diameter of the conical body 71 of the rotor 7.
1 can move forward and backward in the axial direction between a position in contact with the approximate center position of the cone 71 and a position in contact with the peripheral edge position. In addition, the female spline cylinder 103
Are provided with a plurality of spline ridges 104 extending in the axial direction protruding at equal pitches in the circumferential direction.

FIG. 4 is an explanatory diagram for explaining the relationship between the set position of the transmission wheel main body 101 and the rotation speed.
Is a plan view, and a graph showing the relationship between the displacement (L) of the transmission wheel body 101 from the center point O of the rotor 7 and the rotation speed (N) of the transmission wheel body 101 with respect to the rotor 7. Also described. (B) is a partially enlarged sectional view of the transmission 1 in a side view, in which the rotation direction of each component is indicated by an arrow.

First, as shown in FIG. 4B, when the first shaft 2 rotates clockwise as viewed by X-ray as indicated by an arrow, the rotation is caused by the sun wheel 4 and the planet wheel 5. Is transmitted to the first drive wheel 6 in a speed-up state via the first drive wheel 6, and the first drive wheel 6 turns counterclockwise in the opposite direction to the first shaft 2. The rotation of the first drive wheel 6 in the counterclockwise direction is transmitted to the rotor 7 via the first drive wheel 6 so as to rotate rightward as viewed in the Y-line.

On the other hand, the second drive wheel 9 which rotates together with the first shaft 2 at the same rotation speed also comes into contact with the rotor 7 to rotate the rotor 7 rightward (clockwise) when viewed from the Y line. Since the peripheral speed is lower than the peripheral speed of the first drive wheel 6, this difference causes the rotor 7 to revolve clockwise around the first shaft 2 in the X-ray view, while the rotor 7 rotates in the Y direction. The transmission wheel main body 101 abutting on the rotor 7 by this rotation is rotated clockwise in the line view, and the transmission wheel body 101 is rotated leftward in the X-ray view depending on the contact position with respect to the rotor 7. Rotate to the right or to the right.

The number of rotations of the transmission wheel main body 101 in the clockwise direction (indicated by the dashed-dotted arrow in FIG. 4A) is as shown in the graph of FIG. It differs depending on the contact position with the child 7, and the center point O
(The vertex of the conical body 71). That is, the relational expression of “N = aL” holds.
Note that N is the number of revolutions of the transmission wheel main body 101 with respect to the rotor 7, and L is the displacement amount of the transmission wheel main body 101 from the center point O. A is a proportional constant.

On the other hand, as described above, due to the difference between the number of rotations of the first drive wheel 6 and the number of rotations of the second drive wheel 9, the rotor 7 is deflected around the first axis 2 in X-rays. Since it revolves clockwise (indicated by a dotted arrow in (a) of FIG. 4), the effect of this revolving is written in the graph of FIG.
1 ". Therefore, the neutral position L, which is the position of the intersection of the straight line “N = N1” and the straight line “N = aL”
Reference numeral 1 denotes a position where the clockwise rotation and the counterclockwise rotation around the first shaft 2 of the transmission wheel main body 101 are offset with each other. Therefore, the transmission wheel main body 101 does not substantially rotate with respect to the casing 14 at this position. is there.

Then, when the transmission wheel body 101 is in the neutral position L1
To the left, the value of N on the straight line of N = aL becomes N1
Is larger than the center point O of the rotor 7
Since the rotation in the clockwise direction (peripheral speed) overcomes the rotation in the counterclockwise direction around the first shaft 2 due to the revolution of the rotor 7 (peripheral speed), the transmission wheel main body 101 moves rightward in X-ray view ( (Clockwise).

On the other hand, when the transmission wheel body 101 moves to the right from the neutral position L1, the value of N becomes smaller than the value of N1, so that the counterclockwise rotation speed of the transmission wheel body 101 due to the revolution of the rotor 7 is reduced. Transmission wheel body 1 by rotation of rotor 7
Thus, the speed change wheel body 101 is rotated leftward (counterclockwise) as shown by the downward dashed-dotted line in FIG.

In summary, by changing the position of the transmission wheel main body 101, it is possible to change the rotation speed and the rotation direction, and the change in the rotation speed follows the straight line of "N = aL". Since it is performed gradually or gradually, a stable stop state at the neutral position L1 can be realized.

The neutral position L1 can be arbitrarily set in advance by variously changing the effective diameters of the sun wheel 4, the planet wheel 5 and the first drive wheel 6 at the design stage. The most suitable one can be obtained according to the use of the machine 1. Further, in the present invention, when the transmission wheel main body 101 is located at a predetermined position (edge position L2) near the peripheral edge of the rotor 7, the first shaft 2 and the second shaft 3 are rotated at the same rotational speed. The effective diameters of the sun wheel 4, the planet wheel 5, etc. are set so as to rotate.

The transmission means 11 has a male spline cylinder 111 having an outer diameter slightly smaller than the inner diameter of the female spline cylinder 103 of the transmission wheel 10, and a transmission co-rotating with the male spline cylinder 111. And a wheel 115. The male spline cylinder 111 has a center hole 112a having a larger diameter than the second shaft 3 at a center position of the side wall 112 on the speed change wheel 10 side. Male spline cylinder 1
11 has a plurality of spline grooves 113 corresponding to the spline ridges 104 of the female spline cylinder 103.
Is recessed.

Then, the spline groove 113 is fitted into the spline ridge 104 so that the second hole is formed in the center hole 112a.
By inserting the male spline cylinder 111 in which the shaft 3 is fitted into the female spline cylinder 103, relative rotation is prevented,
In addition, the male spline cylinder 111 and the transmission wheel 10 are connected to each other in a state where relative movement within a predetermined range in the axial direction is allowed. Male spline cylinder 1
A radiation groove 114 having a predetermined length extending radially from a peripheral portion of the center hole 112 a
(FIG. 3) are provided at the same pitch in the circumferential direction.

The transmission wheel 115 has an inner diameter of the second shaft 3.
Cylindrical transmission wheel main body 116 slightly larger than the shaft main body 31
And a protruding cylindrical body 117 protruding from the transmission wheel main body 116 concentrically to the left and having an outer diameter set to abut only on the inner cylinder of the bearing B.
The transmission wheel main body 116 is provided with a radiation groove 118 on the transmission wheel 115 side corresponding to the radiation groove 114 provided on the side wall 112 of the male spline cylinder 111, and a retainer 109 is provided between the radiation grooves 114. , And the rotation of the male spline cylinder 111 is transmitted to the transmission wheel 115 via these steel balls S. Each of the radiation grooves 114 and 118 has an arc shape or a V shape so that the cross-sectional shape matches the spherical surface of the steel ball S.
It is formed in a character shape.

Therefore, when the male spline cylinder 111 rotates, this rotational force causes the steel ball S to ride on the inclined surface of the V-groove, and is thereby divided into a force (thrust force) for pressing in the axial direction. The male spline cylinder 111 is pressed to the right by this thrust force, so that the second drive wheel 9 more securely adheres to the rotor 7 and the frictional force proportional to the rotational force therebetween. This greatly improves transmission efficiency.

The side wall 112 of the male spline cylinder 111
As shown in FIG. 1, an annular groove 112b is formed concentrically with the center of the center hole 112a, and an annular surface having the same diameter dimension is formed on a surface of the second drive wheel body 91 facing the side wall 112. With the groove 91a (FIG. 3) recessed and the male spline cylinder 111 penetrated into the transmission wheel 10, as shown in FIG. 3, a plurality of steel balls S are interposed between the annular grooves 91a and 112b. The male spline cylinder 111 and the second drive wheel 9 can rotate around the axis at different rotational speeds by the rolling of the steel ball S in each of the annular grooves 91a and 112b. Each of these annular grooves 91a, 112b
And the steel ball S form a thrust bearing.

The contact position changing means 12 includes an operating rod 12 inserted into a rod insertion hole 142c formed in an axially opposed wall of a bulging portion 142a of a cylindrical casing 141.
0, a spiral rod 121 externally fitted to the operation rod 120 and fixed by screws or the like, and a spiral wheel 121 screwed to the spiral rod 121 and
The operation member 123 includes a U-shaped member 122 that is slidably connected to the operation rod 01 and an operation handle 123 that is fixed to an end of the operation rod 120 by screws or the like.

The U-shaped member 122 has a screw hole 122a screwed to the spiral rod 121, and has an external fitting groove 122b orthogonal to the screw hole 122a. The outer fitting groove 122b is dimensioned so that the groove width dimension can be fitted into the outer peripheral edge of the transmission wheel main body 101 in a sliding contact state. The outer fitting groove 12 of the U-shaped member 122
As shown in FIG. 3, as shown in FIG. 3, the contact position changing means 12 is linked to the transmission wheel 10 by being slidably fitted on the outer peripheral edge of the transmission wheel main body 101.

The operating handle 123 includes a handle disk 124 and a handle lever 125 attached to the handle disk 124. Handle disk 1
A mounting hole 124a into which the distal end of the operation rod 120 is fitted is formed at the center position of the
The operation handle 123 is attached to the casing 14 by fixing the handle disk 124 to the operation rod 120 by screwing or the like with the mounting hole 124a externally fitted to the tip of the operation rod 120 led out from the rod insertion hole 142c. It is supposed to be.

The handle lever 125 is protruded near the edge of the surface of the handle disk 124 opposite to the surface on which the operation rod 120 is mounted so as to be orthogonal to the disk surface. Therefore, by operating the handle lever 125 forward and backward around the operation rod 120, the spiral rod 121 integrated with the operation rod 120 rotates together with the handle lever 125, and the spiral rod 12
The transmission wheel main body 101 whose edge is fitted into the outer fitting groove 122b moves forward and reverse by the forward and reverse movement of the U-shaped member 122 screwed into the first member 122, and the inner peripheral surface of the transmission wheel body 101 abuts on the rotor 7. Is changed, the rotation of the first shaft 2 is reduced at a predetermined reduction ratio, and
It will be transmitted to the shaft 3.

The clutch mechanism 13 will be described below with reference to FIG. 5 and to FIGS. 1 and 3 as necessary. FIG. 5 is an enlarged cross-sectional view showing one embodiment of the clutch mechanism 13, wherein FIG.
Indicates a clutch-on state. As shown in these figures, the clutch mechanism 13 is connected to the second drive wheel 9.
Cylinder 131 concentrically recessed at the distal end side of cylindrical body 92
And a clutch cylinder 132 provided inside the cylinder 131 so as to be able to move forward and backward in the axial direction.
A hydraulic passage 133 for feeding hydraulic oil into the inside 31 and pressing the clutch cylinder 132 in the direction of the second shaft 3;
In addition, it has a basic configuration including an installation shaft 134 that is installed concentrically between opposed end surfaces of the second shaft 3, and a coil spring 135 that presses the clutch cylinder 132 in the direction of the first shaft 2.

The inner diameter of the cylinder 131 is set to be larger than the inner diameter of the cylinder 92 of the second drive wheel 9. The cylinder 131 is concentrically recessed from the front side (the left side in FIG. 5) of the second drive wheel main body 91 toward the cylinder 92, thereby forming an annular wall 131 a at the right end of the cylinder 131. It is in a state of being left. On the inner peripheral surface of such a cylinder 131, there are provided a plurality of protrusions 131b projecting at equal pitches in the circumferential direction and extending in the axial direction. The first shaft 2 is in a state in which its tip portion penetrates through the cylinder 92 and slightly projects into the cylinder 131.

The clutch cylinder 132 is formed with a bottom having an opening at the left end face, has a bottom plate 132a at the right end, and extends on the outer peripheral face in the axial direction corresponding to the ridge 131b. A plurality of grooves 132c are recessed,
By fitting the concave groove 132c into the ridge 131b, the clutch cylinder 132 can rotate with the second drive wheel 9 while moving forward and backward.

On the other hand, the bridging shaft 134 has a large-diameter shaft 134a which is fitted in a sliding contact with the slide bearing 33 press-fitted into the fitting hole 34 of the second shaft 3, and a large-diameter shaft 134a which is concentric with the end face of the large-diameter shaft 134a. And a small-diameter shaft 134b protruding toward one shaft 2. A press-fitting hole 25 is formed in the end surface of the first shaft 2 for fitting the small-diameter shaft 134b in a state of sliding contact with the axial center position. The second shaft 3 and the second shaft 3 can rotate without being out of order.

The bottom plate 132a of the clutch cylinder 132
At the center position, an insertion hole 132b through which the small-diameter shaft 134b is slidably inserted is formed. The small-diameter shaft 134b is inserted into the press-fit hole 2 of the first shaft 2 while passing through the insertion hole 132b.
5. An annular thrust bearing plate 136 is externally fitted to the small-diameter shaft 134b inside the clutch cylinder 132, and the coil spring 135 is externally fitted in a compressed state between the thrust bearing plate 136 and the bottom plate 132a. Usually, the clutch cylinder 132 is the first shaft 2
And is brought into contact with the tip of the first shaft 2.

The clutch cylinder 132 has a first clutch claw 137 radially protruding from the end face thereof over the entire circumference, while the first clutch claw 1 is provided on the end face of the second shaft 3.
The second clutch pawl 138 faces the second clutch claw 138. Then, in a state where the hydraulic oil from the hydraulic passage 133 has not reached the predetermined hydraulic pressure, the clutch cylinder 132 is moved to the state shown in FIG.
As shown in FIG. 5, the urging force of the coil spring 135 pushes the first clutch claw 137 into the clutch off state in which the first clutch claw 137 is separated from the second clutch claw 138, while a predetermined pressure is applied from the hydraulic passage 133. Is supplied to the cylinder 131, the clutch cylinder 132 moves leftward against the urging force of the coil spring 135, and as shown in FIG. The clutch is engaged so as to be engaged with the clutch pawl 138.

The hydraulic passage 133 includes an axial passage 26 formed at an axial position of the first shaft 2, the second annular groove 24 communicating with the axial passage 26, and a second drive wheel 9. Cylinder 92
And a tubular passage 94 formed therein corresponding to the second annular groove 24. The cylindrical passage 94 has one opening provided on the inner peripheral surface of the cylindrical body 92 so as to face the second annular groove 24, and the other opening has an annular wall 1.
31a, whereby the hydraulic oil from the axial passage 26 is introduced into the cylinder 131 via the passage 94 in the cylinder, regardless of the rotational phase of the second drive wheel 9. I have.

The clutch mechanism 13 is automatically turned on by operating the operation handle 123 with the first shaft 2 and the second shaft 3 set to the same rotation speed, while the first shaft 2 and the second shaft 2 The clutch is turned off in a state where the handle is operated so that the number of rotations with the shaft 3 is different.

More specifically, a position sensor (not shown) for detecting whether or not the contact position of the transmission wheel body 101 with the rotor 7 is the edge position L2 in FIG. 4 is provided at an appropriate position of the operation handle 123. . When the position sensor detects that the transmission wheel main body 101 is located at the edge position L2, a detection signal indicating the fact is output to a hydraulic mechanism (not shown) via a predetermined control means (control means). In general, the detection signal is converted into a control signal for giving a command to the hydraulic mechanism through the control of the hydraulic mechanism. The clutch is turned on by the projection of the cylinder 132 from the cylinder 131.

On the other hand, it is detected that the transmission wheel main body 101 has deviated from the edge position L2 by the operation of the operation handle 123, and the pressure in the cylinder 131 is reduced by the reverse drive of the hydraulic mechanism. When the pressure in the cylinder 131 is reduced, the clutch cylinder 132 is immersed in the cylinder 131 by the urging force of the coil spring 135,
The engagement of the first and second clutch claws 137 and 138 is released, and the second shaft 3 rotates at a lower speed than the first shaft 2.

The present invention is not limited to the case where the first clutch pawl 137 and the second clutch pawl 138 are provided on the opposing surfaces of the clutch cylinder 132 and the second shaft 3, respectively. A so-called wet clutch which presses and abuts each other via lubricating oil may be employed.

Hereinafter, the operation of the present invention will be described mainly with reference to FIGS. First, when the first shaft 2 is rotated in the state shown in FIG.
And the rotation of the planet wheels 5 is transmitted to the first drive wheels 6. The rotation of the first drive wheel 6 is transmitted to the rotor 7 by the contact between the annular concave portion 63 and the arc edge 72a of the rotor 7, and the rotor 7 rotates at a predetermined rotation speed in a predetermined direction. While the force is applied, the second drive wheel 9 is
The friction disk 72
The rotor 7 with which the rotor 7 is in contact is also provided with a rotational force from the second drive wheel 9 in the same direction, and rotates due to a difference in the number of rotations provided from the second drive wheel 9 and the first drive wheel 6. While revolving around the first axis 2.

The rotation of the rotor 7 is controlled by the speed change wheel main body 10.
Transmission wheel 1 whose inner peripheral surface is in contact with the surface of cone 71
0, the rotation of the transmission wheel 10 is transmitted to the second shaft 3 via the male spline cylinder 111, the steel ball S and the transmission wheel 115, and the second shaft 3 is moved in the same direction with respect to the first shaft 2. Decelerated rotation will be performed.

Since the planet wheel 5 is configured to rotate around the press-fit shaft 53 fixed to the casing 14 via the support disk 54, the planet wheel 5 does not revolve around the sun wheel 4. Therefore, when the planetary wheel 5 revolves, the lubricating oil filled in the casing 14 is stirred up, and the rotational movement of the planetary wheel 5 and other interior parts is not performed smoothly due to the resistance fluctuation, and the stable rotation is not achieved. The conventional inconvenience that it becomes difficult to apply the obtained rotation output to the second shaft 3 is solved, and a stable rotation output can always be taken out from the second shaft 3.

Further, since the planet wheel 5 does not revolve,
Irrespective of the contact position of the transmission wheel 10 with the rotor 7, the revolution speed of the rotor 7 can be reduced and the rotation speed of the rotation can always be set to be constant. It is possible to design in advance so as to be a value most suitable for the force transmission, so that the rotation of the first shaft 2 can always be performed at a high transmission efficiency and stably at any speed ratio within the operation range. It can be output to two axes 3.

FIGS. 6A and 6B are views showing another embodiment of the friction type transmission according to the present invention. FIG. 6A is a sectional view, and FIG. 6B is a front view explanatory view showing an arrangement state of each gear. is there. The transmission 1a of this embodiment employs gears (sun gear 4a and planetary gear 5a) as the sun wheel 4 and the planet wheel 5, and drives the outer peripheral surface of the small-diameter cylinder 61 of the first drive wheel 6a. The point where the gear 61a is formed, the point where the rotation of the sun gear 4a is transmitted to the planetary gear 5a via the idle gear 40, and the press-fit shaft that supports the planetary wheel 5 (the planetary gear 5a). The point that 53 is fixed to the inner surface of the lid 145, that is, the point that the support disk 54 for supporting the press-fitting shaft 53 adopted in the previous embodiment is not provided is the same as the transmission 1 of the previous embodiment. Are different.

Also, by adopting gears for each wheel,
It is necessary to provide a structure for applying a thrust force to the rotor 7 between the first drive wheel 6a and the second drive wheel 9. For this purpose, in the present embodiment, the large diameter portion 2a is formed on the right side of the substantially central portion of the first shaft 2 as a boundary, and the small diameter portion 2b is formed on the left side.

A bearing insertion hole 2c is formed concentrically on the large-diameter cylindrical body 62 side of the first drive wheel 6a, and the first drive wheel 6a is inserted with the bearing B into the first drive wheel 6a. The wheel 6a is rotatably supported around the small diameter portion 2b. The bearing B has a large diameter portion 2 at the right end.
a and a small-diameter portion 2b, and a C-ring 2d is mounted on the entrance side of the bearing insertion hole 2c, whereby the bearing B comes out of the bearing insertion hole 2c. It has been stopped.
Other configurations of the transmission 1a are the same as those of the previous embodiment.

The planetary gear 5a includes a small-diameter gear 56 meshed with the idle gear 40 and a large-diameter gear 57 formed concentrically and integrally with the small-diameter gear 56. The large-diameter gear 57 meshes with the drive gear 61a. ing.

According to the transmission 1a of this embodiment, the sun wheel 4, the planetary gear 5a and the drive gear 61a are replaced with rollers for the sun wheel 4, the planetary wheel 5, and the first drive wheel 6 instead of the rollers.
, The transmission efficiency of the rotational force of the first shaft 2 is improved as compared with the case where these are rollers.

Since the first driving wheel 6a is supported by the small diameter portion 2b of the first shaft 2 via the bearing B, the first driving wheel 6a is generated by the steel ball S supported by the retainer 109,
The thrust force transmitted to the first drive wheel 6a via the drive wheel 9 and the rotor 7 is applied to the large-diameter portion 2a via the bearing B.
Therefore, the rotor 7 is reliably pressed and sandwiched by the first drive wheel 6a and the second drive wheel 9 by the thrust force.

[0086]

According to the first aspect of the present invention, the first and second drive wheels are respectively rotated so that the neutral position on the generating line that does not rotate the transmission wheels is set to a position near the center of the rotor. Since the speed is set, the triangle formed by connecting the first and second drive wheels and the respective contact positions of the transmission wheel with the rotor is substantially an isosceles triangle when the transmission wheel is located at the neutral position. , And a force is applied to the rotor in a very good balance state, so that the transmission efficiency of the rotational force of the second shaft in a low speed range can be stabilized.

Further, since the neutral position of the rotor on the generatrix is located near the center of the rotor, the first and the second
The difference in peripheral speed between the drive wheels is reduced, and the rotor is suppressed from revolving.The rotating wheels are rotated by the rotation, so that the lubricating oil filled in the casing revolves around the rotor. Thus, the stirring resistance caused by the stirring can be greatly reduced as compared with the related art, and the transmission efficiency of the rotational force can also be improved.

According to the invention described in claim 2 (claim 3), the rotational force given to the first shaft is controlled by the sun roller (sun gear) integrated with the first shaft and the sun roller (sun gear). Planetary rollers (planetary gears) arranged around the center;
The outer peripheral surface (gear) is transmitted to the rotor via the first drive wheel that is in contact (engagement) with the planetary roller (planetary gear). The rotation is transmitted to the planetary gear via the idle gear), and is also transmitted by the rotation of the second drive wheel integrated with the first shaft, whereby the rotor is always rotated around the rotation center by the same rotation with respect to the first shaft. It can revolve and revolve at a ratio. Then, by changing the effective diameter of the rotor due to a change in the contact position of the transmission wheel with respect to the rotor, the transmission wheel can be rotated at a predetermined rotational speed ratio with respect to the first shaft corresponding to the contact position.

The planetary roller (planetary gear) rotates by the rotation of the sun roller (sun gear) but does not revolve. Therefore, the lubricating oil filled in the casing revolves around the planetary roller (planetary gear). By applying stirring resistance to the planetary rollers (planetary gears), it is possible to reliably prevent the occurrence of inconvenience such as unstable rotation of the second shaft.

Further, since the revolution speed of the rotor is reduced by not revolving the planetary rollers (planetary gears) and not increasing the peripheral speed difference between the first drive wheel and the second drive wheel, the centrifugal force is reduced. Problems such as instability of the contact state and stirring resistance due to the force are solved, and a stable and high transmission efficiency of the rotational force can be always achieved between the first and second shafts.

The first drive wheel has a first outer peripheral surface corresponding to a planetary roller (planetary gear) and a second outer peripheral surface corresponding to a rotor on the outer peripheral surface. By setting the diameter dimension appropriately, the peripheral speed can be made substantially the same as the peripheral speed of the second drive wheel. When the peripheral speed of each drive wheel becomes substantially the same, the rotor mainly rotates in a stable state with the revolution suppressed as much as possible, so that the transmission can withstand the high-speed rotation of the first shaft and the second shaft. Can be

In particular, according to the second aspect of the invention, since the rotation of the first shaft is smoothly transmitted to the first drive wheels via the rollers, the noise and vibration are reduced, and the transmission operates quietly. can do.

On the other hand, according to the third aspect of the present invention, since the sun gear, the idle gear and the planetary gear are employed, no slip occurs between the respective gears and the transmission efficiency of the rotational force is improved. Can be.

According to the fourth aspect of the present invention, the first shaft and the second shaft are jointly rotatable by the clutch mechanism in a high speed shift state in which the first shaft and the second shaft have reached the same rotational speed. The torque transmission efficiency between the first shaft and the second shaft
00%.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view, partly cut away, showing an embodiment of a friction type transmission according to the present invention.

FIG. 2 is an assembled perspective view of the friction type transmission shown in FIG.

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

FIGS. 4A and 4B are explanatory diagrams for explaining a relationship between a set position and a rotation speed of a transmission wheel main body.

FIGS. 5A and 5B are enlarged sectional views showing an embodiment of the clutch mechanism, wherein FIG. 5A shows a clutch-off state, and FIG. 5B shows a clutch-on state.

FIGS. 6A and 6B are diagrams showing another embodiment of the transmission according to the present invention, wherein FIG. 6A is a cross-sectional view, and FIG. 6B is a front view explanatory view showing an arrangement state of each gear.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1, 1a Transmission 2 1st shaft 21 Shaft main body 22 Small diameter part 23 1st annular groove 24 2nd annular groove 4 Sun wheel 4a Sun gear 41 Sun wheel body 42 Sun disk 43 Annular ring 5 Planetary wheel 5a Planetary gear 6 First Drive wheel 61 Small diameter cylinder 61a Drive gear 7 Rotor 71 Cone 72 Friction disk 8 Rotor support member 9 Second drive wheel 10 Transmission wheel 101 Transmission wheel body 102 Drive wheel storage cylinder 11 Transmission means 111 Male spline cylinder 112 Side wall 113 Spline groove 12 Contact position changing means 121 Spiral rod 122 U-shaped member 123 Operating handle 13 Clutch mechanism 131 Cylinder 132 Clutch cylinder 133 Hydraulic passage 14 Casing

Claims (4)

[Claims] 1. A friction type transmission for changing the rotation input about the axis of a first shaft and transmitting the rotation input to a second shaft concentric with the first shaft by frictional force, wherein any one of the transmissions is concentric with the first shaft. The first drive wheel and the second drive wheel, one of which rotates forward and the other reversely rotates, and the back side abuts the outer peripheral surfaces of the first drive wheel and the second drive wheel, and the first drive wheel and the second drive wheel are driven by the peripheral speed difference between the two drive wheels. A conical rotor that revolves around its axis while revolving around its axis, and its inner peripheral surface abuts on the generatrix of the conical surface of this rotor and rotates around the first axis. And a transmission means for transmitting the rotation of the transmission wheel to the second shaft. The first and second drive wheels are arranged such that a neutral position on the generating line that does not rotate the transmission wheel is a rotor. A friction type transmission, wherein peripheral speeds are set so as to be set at positions near the center. 2. The first driving wheel has a first outer peripheral surface and a second outer peripheral surface having a diameter larger than the first outer peripheral surface, and the first outer peripheral surface rotates concentrically with the first axis. Around the center of the roller, the outer peripheral surface of the planetary roller which rotates only by rotation of the sun roller and rotates only by rotating around the first axis, and the second outer peripheral surface comes into contact with the rotor. The second drive wheel is concentrically and rotatably fixed to the first shaft, and is provided with contact position changing means for changing the contact position of the transmission wheel with respect to the rotor in the radial direction of the rotor. The friction type transmission according to claim 1, wherein: 3. The planetary gear according to claim 1, wherein the first drive wheel has a gear that is concentric with the first shaft, and the gear only rotates through an idle gear by rotation of a sun gear that rotates concentrically with the first shaft. The gear is configured to rotate around the first shaft by meshing with the gear, and to have an outer peripheral surface in contact with the rotor. The second drive wheel is fixed to the first shaft concentrically and corotatably, and 2. The friction type transmission according to claim 1, further comprising contact position changing means for changing a contact position of the transmission wheel with respect to the rotor in a radial direction of the rotor. 4. The first shaft and the second shaft are joined between the first shaft and the second shaft in a state where the first shaft and the second shaft have the same number of revolutions, while the first shaft and the second shaft are connected to each other. The friction type transmission according to any one of claims 1 to 3, wherein a clutch mechanism that separates at different rotational speeds is provided.