KR20120135843A - Continuously variable transmission of hub type - Google Patents

Abstract

PURPOSE: A nonstep variable transmission of hub type is provided to eccentricity-arrange a variable pin in the magnetoelectricity center of an input link by link-coupling the input link and a coupler link. CONSTITUTION: A case(50) is steadily inscribed in a hub of a driving wheel. A fixing central axis(21) has a central axis line same as the rotation center of the driving wheel. The fixing central axis is circumscribed with a variable pin guide unit(21a) by being placed on a one way clutch bearing(21b). One variable pin(P1) link-unites an input link(60) and multiple coupler links(90). A final output axis(85) is steadily inscribed in an output gear(82).

Description

Continuously variable transmission of hub type

The present invention relates to a hub type CVT.

More specifically, the present invention uses a lever crank mechanism for link coupling the input link, the plurality of coupler links and the same number of output links as the number of the coupler links, but the input link is rotated, A variable pin for linking the input link and the plurality of coupler links is elastically fixed in the radial direction of the rotation of the input link according to the load while preventing the rotation and the rotating movement in the state eccentrically arranged at the rotation center of the input link. And a plurality of clutch gears externally connected to the output shafts of the plurality of output links through link pins for coupling the plurality of coupler links and the plurality of output links and one-way clutch bearings. Hub type continuously variable transmissions with a structure that allows them to revolve with the same center of revolution It relates.

In general, the reducer is divided into a constant speed reducer that outputs power at a constant reduction ratio by combining gears of different sizes with each other, and a continuously variable transmission that can change the reduction ratio by applying a conical reduction gear.

The rotational force generated from a power generator such as a motor or an engine is output with high rotational power, but the force (torque) is small. Therefore, in most industrial machines, the torque is increased by using a reduction gear.

Here, the reducer increases torque instead of slowing down the number of revolutions transmitted from the power generator. However, the speed reducer reduces the rotation speed supplied from the power generator and increases the torque and outputs the torque. However, when the load applied to the output shaft is greater than the output torque of the output shaft, the load is reversed to the motor or engine that is the power source. By acting, there is a problem of shortening the life of a motor or engine.

In addition, a load larger than the output torque of the output shaft acts in a reverse direction to the motor or the engine, thereby preventing a target output from being supplied to the output shaft.

A continuously variable transmission device for solving this problem is disclosed in Korean Patent No. 10-2007-0064349 filed by the inventor.

In the continuously variable transmission disclosed by the patent application, a lever crank mechanism is interposed between an input shaft that is rotated in one direction by an external force (such as a motor or an engine) and an output shaft that receives the driving force of the input shaft and transmits the driving force to the outside. .

The lever crank mechanism is a known mechanism for causing the one-way rotational movement of the input shaft to make the output shaft reciprocate within a certain angle range. By using such a known mechanism, the device may be, for example, a wiper drive device.

However, the conventional continuously variable transmission using the lever crank mechanism adopts a system in which the power transmission system is biased to one side, and thus there is a problem that vibration or noise is generated during operation.

A continuously variable transmission that solves this problem is disclosed in Patent Application No. 10-2008-0092992 filed by the present inventors.

The continuously disclosed variable speed apparatus includes an input shaft (1) rotatably mounted on a frame (not shown) to receive a rotational force input from the outside, as shown in FIGS. 1 and 2; A pair of driven shafts 2 and 2 arranged parallel to the input shaft 1 with the input shaft 1 interposed therebetween to receive power from the input shaft 1 while being rotatably mounted to the frame. '); The radially outward direction of the pair of variable pins (P1, P2) is coupled to the input shaft (1) so as to receive a rotational force of the input shaft (1), the rotation radius is variable by an external load A pair of variable input links 3 and 4 respectively accommodating a pair of reaction force devices 3a and 4a respectively pressed together with the pair of variable pins P1 and P2; One-way clutch bearings 5 and 6 which receive two-way rotational force transmitted to each of the pair of driven shafts 2 and 2 'in one direction and rotate each of the pair of driven shafts 2 and 2' in one direction; Two pairs of output links 7, 8; 7 ', 8' having one end circumscribed and coupled via 5 ', 6'); And one end rotatably coupled to each of the pair of variable pins P1 and P2, and the other end rotatably coupled to each of the two pairs of output links 7, 8; 7 ', 8'. Two pairs of coupler links 9, 10; 9 '10' are included.

Here, the driving coupling method between the input shaft (1) and the pair of variable input links (3, 4), as shown in Figure 1, a pair of variable input links on both ends of the input shaft (1) (3, 4) A manner in which each end is fixedly circumscribed may be taken, or as shown in FIGS. 3 and 4, an input gear G1 fixedly circumscribed on the outer circumferential surface of the input shaft 1 is provided. And engaging the G1 and G2 with each other in a state where a primary driven gear G2 fixedly circumscribed is provided in a cylindrical housing 11 in which the pair of variable input links 3 and 4 are integrated. The way may be taken.

In addition, the pair of variable pins P1 and P2 are disposed with a phase difference of 180 degrees with respect to each other, and the output links 7 and 7 'of the two pairs of output links are the one output link 7. ) May be arranged in such a manner as to have a leading phase difference greater than 0 degrees and less than 180 degrees in the rotational direction than the other output link 7 ', and the other output links 8 and 8' are also output in the one output. The link 8 can be arranged in such a way that it has a leading phase difference greater than 0 degrees and less than 180 degrees in the direction of rotation than the other output link 8 '.

In addition, the driving coupling between the two pairs of output links (7, 8; 7 ', 8') and the pair of driven shafts (2, 2 '), as shown in Figures 1 and 2, One end of the output link 7, 8, 7 ′ 8 ′ with one-way clutch bearings 5, 6; 5 ′, 6 ′ interposed at each end of each of the pair of driven shafts 2, 2 ′. This fixed circumscribed manner can be taken, or as shown in FIGS. 3 and 4, each of the pair of driven shafts 2, 2 ′ is tubular and the pair of driven shafts 2, 2 ′. ) One end of the output link 7, 8; 7 ′ 8 ′ may be fixedly inscribed with the one-way clutch bearings 5, 6; 5 ′ 6 ′ interposed therebetween.

In addition, a pair of output gears G3 and G3 'are fixedly circumscribed to the pair of driven shafts 2 and 2', respectively, and between the pair of output gears G3 and G3 '. And final output gear (G4) is arranged to mate with.

The final output gear G4 is fixedly inscribed with a final output shaft 15 to be coupled with a driven shaft (not shown) of an external device to which power is to be transmitted.

In the conventional continuously variable transmission configured as described above, the coupler link, the output link, and the driven shaft are symmetrically arranged on the left and right sides of the variable input link, so that no vibration occurs during operation, so that noise is generated. In addition, a pair of output gears fixedly circumscribed between two driven shafts are engaged with each other via a final output gear, such that the pair of output gears rotate in one direction in cooperation with each other. In this case, the output gear can be rotated with great force, and the external device can be driven with great force.

However, such a continuously variable transmission device is provided between the first link portions 3, 9, 9 ′, 7, 7 ′ and the second link portions 4, 10, 10 ′, 8, 8 ′, which link with each other with a phase difference. There is a problem in that the stepless transmission is enlarged by being spaced at a predetermined interval in the longitudinal direction of the input shaft 1, and the first link portion and the second link portion have a phase difference with each other, which is a pivoting movement, that is, a pivoting movement in opposite directions. This imparts a torsional load doubled to the input shaft 1, making the input shaft 1 vulnerable to durability, and even at a precise time, the counterclockwise or counterclockwise clockwise rotation of the clockwise motion. There is a problem that the first link portion or the second link portion does not switch the swing motion.

Furthermore, when the conventional continuously variable transmission, in which the overall size is enlarged as described above, is loaded into the hub of the driving wheel such as a bicycle, an electric bicycle, an electric wheel chair, or an electric car, it protrudes prominently, and thus, a bike, an electric bike, an electric wheel chair, an electric car. The conventional continuously variable transmission has the problem of spoiling the appearance of the back and the like.

A continuously variable transmission device for overcoming these problems is disclosed in Korean Patent Laid-Open Publication Nos. 10-2010-0076365 and 10-2010-0090090.

The continuously variable transmission described above has an input shaft rotatably mounted to one side of a case 211 fixedly inscribed to a hub of a driving wheel (not shown) via a bearing B1, as shown in FIG. 5. 110 and an idle shaft S2 rotatably mounted through the bearing B2 on the other side of the case 211.

One side of the input shaft 110 protruding from one side of the case 211 has a driven sprocket (D) is fixedly circumscribed, the driven sprocket (D) is not shown mounted on a pedal shaft (not shown) In a state of being wound on a chain (not shown) wound on a drive sprocket, the shaft is rotated together with the input shaft 110.

In the case 211, a standing frame F is embedded, and the variable input link 130 is connected to the frame (B) through a bearing B3 in a hole O formed at the center of the frame F. It is rotatably inserted with respect to F).

On one side of the variable input link 130, the front end of the input shaft 110 is rotatably inserted in the state through the one-way clutch (C).

6 and 7, the variable input link 130 is disposed radially outward with respect to the variable input link 130, and has a phase difference of 90 degrees to the frame F. Four output links 171, 172, 173, 174 are rotatably mounted.

The other side of the variable input link 130 has a built-in reaction force (S) for pressing the variable cam (P), the rotation radius is variable by an external load elastically in the radial outward direction.

The variable input link 130 together with the variable cam P is revolved about the center of rotation of the variable input link 130 according to the rotational movement of the variable input link 130 at the front end of the variable cam P. Disc disk 140, which rotates orbitally about the center of rotation is coupled rotatably.

Each of the four output links 171, 172, 173, and 174 is externally provided with four driven gears 121, 122, 123, and 124 via one-way clutch bearings 151, 152, 153, and 154. It receives two-way rotational force transmitted to each of the four output links 171, 172, 173, and 174 in one direction to rotate each of the four driven gears 121, 122, 123, and 124 in one direction.

One end of four coupler links 191, 192, 193, and 194 having the same length is rotatably linked to each of the four holes 181, 182, 183, and 184 formed with the phase difference of 90 degrees in the disk plate 140. The other end of the four coupler links (191, 192, 193, 194) is rotatably linked to each of the four output links (171, 172, 173, 174).

The one-way clutch bearings 151, 152; 153, 154 are all walked in the same direction, that is, clockwise or counterclockwise, with respect to the four driven gears 121, 122; 123, 124, respectively. 121, 122; 123, 124 are rotated clockwise or counterclockwise.

In addition, at the base end of the input shaft 110, one output gear G3 rotated in engagement with all of the four driven gears 121, 122, 123, and 124 is rotatably circumscribed, and the one output The gear G3 is integrally formed with an annular output shaft G4 protruding toward the proximal end of the input shaft 110 and having a rotation center and a concentric rotation axis of the input shaft 110.

In addition, the annular output shaft G4 is fixedly inscribed on one side of the case 211.

One side of the frame F is fixed to the other end of the first support piece 220, one end of which is supported by the idle shaft S2, of the case 211 fixedly circumscribed to the annular output shaft G4. The other end is fixed to the front-end | tip of the 2nd support piece 230 in which the base end is standing up via the bearing B4 in the boss 212.

A continuously variable transmission with this configuration is powered and shifted as follows.

The input shaft 110 that rotates in one direction by receiving power from the chain (not shown) through the sprocket D rotates the variable input link 130, and thus the variable cam is arranged to be eccentrically accommodated in the variable input link 130 ( P) and the variable cam (P) rotational force rotates the disk plate (140) rotatably coupled to the variable cam (P) about the center of rotation of the variable input link (130).

The disk plate 140 rotated in an orbital manner is four coupler links 191, 192, 193, which are linked to the disk plate 140 by an orbital motion of 0 to 90 degrees of the disk plate 140. For example, one output link 171 of the four output links 171, 172, 173, and 174 linked to each of the four coupler links 191, 192, 193, and 194 through 194 is provided. In the case of pivoting at a predetermined angle for driving the real body, the other output link 174 having a phase difference within -180 degrees with respect to the one output link 171 is moved forward and backward in the forward direction, and the one The other output link 172 has a phase difference of +180 degrees with respect to the output link 171 in the forward turning direction, and the other one having a phase difference of 180 degrees or more with respect to the one output link 171. Pivoting the output link 173 in the reverse direction;

Subsequently, the disk plate 140 has a 91-180 degree orbital motion, which has a +90 degree phase difference with respect to one of the four output links 171, 172, 173, and 174. The output link 172 is pivoted at a predetermined angle for driving the actual material, and the output link 171 is rotated forward and backward in a forward direction with respect to the output link 172 with a phase difference within -180 degrees. Entering and pivoting the output link 173 having a phase difference within +180 degrees with respect to the link 172 in a forward direction, and the other output link 174 having a phase difference of 180 degrees or more with respect to the output link 172. Pivoting in the reverse direction;

Subsequently, the disk plate 140 has a retardation motion of 181 degrees to 270 degrees, which has a +90 degree phase difference with respect to one of the four output links 171, 172, 173, and 174. The output link 173 is pivoted at a predetermined angle for driving the actual material, and the output link 172 is pivoted forward and backward in a forward direction with respect to the output link 173 with a phase difference within -180 degrees. Entering orbiting the output link 174 having a phase difference within +180 degrees with respect to the link 173 in a forward direction, and the other output link 171 having a phase difference of 180 degrees or more with respect to the output link 173. Pivoting in the reverse direction; And

Subsequently, the disk plate 140 has a +90 degree phase difference with respect to one of the output links 173 of the four output links 171, 172, 173, and 174 by 271 degrees to 360 degrees of revolving motion. The output link 174 is pivoted at a predetermined angle for driving the actual material, and the output link 173 is pivoted forward and backward in the forward direction with respect to the output link 174 with a phase difference within -180 degrees. Entering orbiting the output link 174 having a phase difference within +180 degrees with respect to the link 173 in a forward direction, and the other output link 171 having a phase difference of 180 degrees or more with respect to the output link 173. Rotate in the reverse direction.

Between the output link (171, 172, 173, 174) and the driven gear (121, 122, 123, 124) only the forward turning movement of the output link (171, 172, 173, 174) the driven gear One-way clutch bearings 151 and 152 which transmit to 121, 122, 123 and 124, respectively, are interposed, resulting in an output gear that meshes with the four driven gears 121, 122, 123 and 124 simultaneously. G3) always rotates in the forward direction when the input shaft 110 is driven.

As a result, the output gear G3 transmits the forward motion to the annular output shaft G4 to rotate the case 211 fixed to the annular output shaft G in the forward direction to rotate the driving wheel of the bicycle in the forward direction.

 Here, a large load transmitted from the annular output shaft G4 via the driving wheel and the case 211 is transmitted to the reaction force device S through the driven gear, the output link, the coupler link disk plate, and the variable cam P, When the variable cam P approaches the center axis of the variable input link 130, the revolving radius of the variable cam P becomes small, so that the reciprocating turning of the output links 171, 172, 173, 174 is performed. As the angle of the movement becomes smaller, the driven gears 121, 122, 123, and 124 become a low speed mode, and on the contrary, a small load transmitted from the annular output shaft G4 is transmitted to the reaction force device S in the same manner as described above. When the variable cam P moves away from the center axis of the variable input link 130, the revolving radius of the variable cam P becomes large, so that the angle of the turning reciprocating motion of the output links increases. The driven gears are in high speed mode.

And when the load transmitted from the annular output shaft compresses the reaction device (S) so that the variable cam (P) is located on the center axis of the variable input link 130, the revolving radius of the variable cam (P) is In the state of zero, only rotating, the angle of the turning reciprocating motion of the output link is zero, the speed of the driven gear is "0", at this time, since the minimum speed as the reference of the gear ratio is "0", in theory, Since the transmission ratio is 0 to ∞, the conventional hub type continuously variable transmission can be continuously controlled.

As described above, the hub type continuously variable transmission may be fixedly inscribed to a hub such as a bicycle by reducing its volume.

Nowadays, the vehicle is being improved to an electric vehicle driven by an electric motor in order to prevent environmental pollution, and in addition, the bicycle driven by a manpower is being improved by an electric bicycle driven by an electric motor.

In line with this situation, a method of incorporating a hub type continuously variable transmission in which a motor, which is an electric motor, is combined as one modular small unit, has been considered.

However, the conventional continuously variable transmissions use a lever crank mechanism for linking an input link, a plurality of coupler links, and an output link equal to the number of coupler links to each other, thereby allowing the input link to rotate. A variable pin for link coupling the input link and the plurality of coupler links is to be resiliently moved in the radial direction of the rotation of the input link according to the load while the idle movement in the state eccentrically arranged in the rotation center of the input link Rotating the link pins for linking the plurality of coupler links and the plurality of output links is not idle and the plurality of clutch gears external to the output shaft of the output link via the one-way clutch bearing is not idle It is structured to exercise, the input link and a plurality of Although the variable pin that couples the coupler link is eccentric in the center of the rotational motion of the input link is the most important component for continuously variable speed, but the input link is rotated through the bearing through the bearing, The variable pin, which is orbitally moved by the input link according to a variable such as wear, has a different amount of eccentricity from the center of the rotational motion of the input link. As the unit is compact, it has a problem that it is structurally difficult to eccentrically position the variable pin.

A continuously variable transmission for solving such a problem is disclosed by the inventor in the patent application No. 10-2011-0031969 dated April 7, 2011.

However, the continuously variable transmission of the patent application has a problem in that, for example, the wheel to be driven by the electric motor can be driven in the forward rotation direction, but cannot be driven in the reverse rotation direction.

The present invention has a problem in solving the above problems.

The present invention, when the driving force in the positive rotational direction of the electric motor is applied, the rotational force in the forward rotational direction is applied to the output unit in a state where the stepless speed change is possible by the lever crank mechanism without rotating the variable pin and idle, and When the driving force in the reverse rotation direction of the electric motor is applied, the above problem can be solved by applying the rotation force in the reverse rotation direction to the output unit by rotating the bundle holding the lever crank mechanism in the reverse rotation direction while idling the variable pin. .

The present invention relates to: By the above problem solving means structurally facilitates the eccentric positioning of the variable pin, which is the most important component for the continuously variable, that is, the variable pin for link coupling the input link and the coupler link at the rotation center of the input link. In addition, it is possible to provide a continuously variable transmission in a small unit in a state where the electric motor is embedded, and at the same time, it is possible to transmit the reverse driving force to the output unit.

1 and 2 is a conceptual diagram showing a conventional continuously variable transmission,
3 and 4 are a cross-sectional view and a side view showing an improvement of the continuously variable transmission of FIG. 1 to a hub type.
5 is a conceptual diagram illustrating a conventional continuously variable transmission of the hub type;
6 and 7 show a conventional continuously variable transmission modified to a hub type based on the concept of FIG. 5; and
Fig. 8 is a view showing the hub type continuously variable transmission of this embodiment.

Hereinafter, an embodiment according to the present invention will be described with reference to FIG. 8, which is an accompanying drawing.

FIG. 8 is a cross-sectional view of an embodiment of a hub type continuously variable transmission that can be fixedly inscribed to a hub of a drive wheel, not shown.

Hub type continuously variable transmission of the embodiment, the fixed central axis (21); An electric motor (30) through which the fixed central axis (21) penetrates and is fixedly circumscribed to the fixed central axis (21); And a case 50 rotatably circumscribed to the electric motor 30 via a bearing 41 and fixedly inscribed to a hub of a driving wheel (not shown) and having the electric motor 30 embedded therein.

One end of the fixed central axis 21 extends to one side in the direction of the rotational center axis of the case 50, protrudes out of the case 50, and the other end of the fixed central axis 21 is the case 50. It is located in the case 50 extending to the other side in the direction of the center of rotation of the axis.

At the other end of the fixed center shaft 21, the variable pin guide portion 21a is circumscribed through the one-way clutch bearing 21b. The one-way clutch bearing 21b is in a stepped state with respect to the forward rotation of the variable pin guide portion 21a and a non-stepped state with respect to the reverse rotation.

The electric motor 30 is disposed radially inward with respect to the stator 32 and the stator 32 fixedly inscribed in the housing 31 of the electric motor 30, and rotates on the fixed central axis 21. An input gear coupled to the rotor 33, possibly rotatable, the rotor 33 rotatably circumscribed to the fixed central axis 21, and fixedly circumscribed to the variable pin guide portion 21a ( 34) and a reduction gear 35 engaged with the input gear 34 and rotating with the rotation center of the input gear 34 and the rotation center biased in the case 50.

The drum-type input link 60 is rotatably circumscribed with respect to the variable pin guide portion 21a in a state in which the variable pin guide portion 21a is interposed with a bearing 42. In addition, the drum-type input link 60 is rotatably circumscribed in a state in which a bearing 44 is interposed between a boss 51 formed on an inner surface of the case 50 facing the fixed central axis 21. .

The drum-type input link 60 may include a first token shape portion 61 and a second token shape portion 62 spaced apart from each other in an axial direction of the fixed central shaft 21, and the first and second token shapes. It includes a fastening member 63 for coupling in a state spaced apart from each other.

A ring-shaped rack gear is formed on an inner circumferential surface of the first token-shaped portion 61 of the variable input link 60 facing the reduction gear 35 so as to be engaged with the reduction gear 35. 64 is mounted to rotate with the input link 60 to have the same center of rotation as the center of rotation of the input link 60.

The variable pin guide portion 21a is formed with a long guide rail groove 65 in the radial direction of the rotational movement of the input link 60, and the guide rail groove 65 along the guide rail groove 65 A movable variable pin (P1) is mounted eccentrically at the center of rotation of the input link (60), the variable pin (P1) is elastically in the direction of the rotational motion of the input link 60 by an external load In order to be variable, the variable pin (P1) is supported by a reaction force device (S) such as a spring built in the guide rail groove (65) in the state of elastically pressing radially outward. .

In addition, the input link 60, one end is coupled to the one variable pin (P1) in a state arranged adjacent to the inner surface of the token-shaped portion 61 is radial in the center of rotation of the case 50 Four coupler links 90 spaced apart in the outward direction with a phase difference of 90 degrees and one end of each of the four coupler links 90 are linked to each other via a link pin P2 and the case 50. 4 output links 70 (only two are shown in FIG. 8) are arranged at a phase difference of 90 degrees spaced radially outward from the center of rotation.

Each other end of the four output links 70 is rotatably mounted on an inner surface of the second token shape portion 62 of the input link 60 and radially outward from the center of rotation of the case 50. It is fixedly circumscribed on each of the four output shafts 80 (only two of which are shown in FIG. 8), which are spaced apart by 90 degrees of phase difference.

Each of the four output shafts 80 is externally provided with four clutch gears 81 via one-way clutch bearings 43 to receive bidirectional rotational force transmitted to each of the four output links 70 only in one direction. Each of the four clutch gears 81 is rotated in one direction.

In addition, the boss 51 formed on the inner surface of the case 50 facing the fixed center axis 21 is fixed to the final output shaft 85 to have the same rotation center as that of the case 50. The output gear 82 meshes with all of the four clutch gears 81 on the final output shaft 85.

Also, at least one of the four output shafts 80 is externally provided with a first intermediate gear 87 via a one-way clutch bearing 86, and the final output shaft 85 is interposed with a one-way clutch bearing 88. The second intermediate gear 89 is circumscribed, and the third intermediate gear 84 is circumscribed on the final output shaft 85.

The first intermediate gear 87 is provided with two gear portions 87a and 87b to be engaged with the second and third intermediate gears 89 and 84 simultaneously.

The one-way clutch bearings 43 are all stepped on the four clutch gears 81 in the same direction, and transmit power to the clutch gear 81 in the reverse rotation direction when the output shaft 80 rotates in the reverse direction. In the forward rotation of the clutch gear 81, power is transmitted to the output shaft 80 in the forward rotation direction.

The one-way clutch bearing 86 transmits power to the first intermediate gear 87 in the reverse rotation direction when the output shaft 80 is reversely rotated, and at the forward rotation of the first intermediate gear 87, the output shaft ( 80) to transmit power in the forward direction.

The one-way clutch bearing 88 transmits power to the second intermediate gear 89 in the forward rotation direction at the time of forward rotation of the final output shaft 85 and at the end of the reverse rotation of the second intermediate gear 89. Power is transmitted to the output shaft 85 in the reverse rotation direction.

 Therefore, when any one of the output shaft 80 of the four output shaft 80 is rotated in the reverse rotation direction, the clutch gear 81 is rotated in the reverse rotation direction, the first intermediate gear 87 Also rotated in the reverse rotation direction, so that the final output shaft 85 is rotated in the forward rotation direction.

As the final output shaft 85 rotates in the forward rotation direction, the third intermediate gear 84 rotates in the forward direction, and the second intermediate gear 89 of the final output shaft 85 rotates in the forward rotation direction. Done.

As a result, the first and second intermediate gears 87 and 89 smoothly mesh with each other as the first intermediate gear 87 rotates in the reverse rotation direction and the second intermediate gear 89 rotates in the forward rotation direction. Will rotate.

In addition, when the output shaft 80 is rotated in the forward rotation direction, the clutch gear 81 and the first intermediate gear 87 is in a stopped state, the state that can not transmit power to the final output shaft 85 do. However, the other one of the four output shafts 80 is in the reverse rotation state, the final output shaft 85 is rotated in the forward direction, accordingly, the clutch gear 81 is the final output shaft 85 By the reverse rotational power, but the clutch gear 81 and the one-way clutch bearing 86 is in a sliding state so that the clutch gear 81 is rotated in reverse and the one output shaft 80 is in a stopped state. In this manner, the first intermediate gear 87 also rotates in a reverse rotation direction without transmitting power to the one output shaft 80, and the second intermediate gear diagram 89 also includes the first intermediate gear diagram 89. The intermediate gear 87 is rotated in the forward direction while being engaged with the intermediate gear 87.

The continuously variable transmission of the embodiment having such a configuration is powered and shifted as follows.

When the motor 30 embedded in the case 50 is operated in the forward direction, the power of the motor is sequentially transmitted to the input gear 34 and the reduction gear 35, and the reduction gear 35 is connected to the input link ( When the input link 60 is rotated in the forward rotation direction about the center axis of the fixed central axis 21 by transmitting power to the 60, and the motor 30 is operated in the reverse direction, the one-way clutch The bearing 21b is in a non-walking state so that the input link 60 rotates in the reverse rotation direction.

As the input link 60 rotates in the forward direction, the coupler link 90, the output link 70, the output shaft 80, and the clutch gear 81 embedded in the input link 60 are fixed to the central shaft. Orbital movement about the central axis of (21).

The coupler link 90 is coupled to the variable pin (P1) eccentric to the revolving center of the coupler link 90, 0 degrees ~ 90 degrees orbital movement of the coupler link 90, 91 degrees ~ The four coupler links 90 are four outputs linked to each of the four coupler links 90 by 180 degree idle motion, 181 degree 270 degree idle motion, and 271 degree 360 degree idle motion. In the case where one output link 70 of the links 70 is pivoted at an angle for actual driving, the other output link having a phase difference within −180 degrees with respect to the one output link 70. Forward and backward pivoting (70) in the forward direction, another output link (70) having a phase difference within +180 degrees with respect to the one output link (70) in the forward pivoting direction, the one output The other output link 70 having a phase difference of 180 degrees or more with respect to the link 70 Turn in the reverse direction.

One direction for transmitting the movement to the clutch gear 81 only in the reverse swing motion of the output shaft 80 between the output shaft 80 and the clutch gear 81 fixedly inscribed at the other end of the output link 70. Since the clutch bearing 43 is interposed, the output gear 82 meshed with the four clutch gears 81 is always rotated in the forward direction when the electric motor 30 is driven in the forward direction. As a result, the case 50 rotates in the forward direction, such that the driving wheel fixedly circumscribed to the case 50 rotates in the forward direction.

Here, a large load transmitted to the output gear 82 through the driving wheel is transmitted to the reaction force device S through a clutch gear, an output link, a coupler link, and a pin, so that the variable pin P1 is connected to the input link ( 60, the angle of the turning reciprocating motion of the output link 70 becomes smaller so that the clutch gear 81 is in the low speed mode, and conversely, the small transmission from the output gear 82 When the load is transmitted to the reaction force device S in the same manner as described above, and the variable pin P1 moves away from the center axis of the input link 60, the angle of the turning reciprocating motion of the output links is It becomes large so that the clutch gears are in the high speed mode.

And when the load transmitted from the output gear compresses the reaction device (S) so that the variable pin (P1) is located on the center axis of the input link 60, the coupler link is only idle, without turning motion, Since the angle of the turning reciprocating motion of the output link becomes zero, the speed of the clutch gears becomes "0", and at this time, since the minimum speed as the reference of the speed ratio becomes "0", the shift ratio is theoretically 0 to ∞. The continuously variable transmission of the embodiment can be continuously transmitted.

In the above embodiment, although four coupler links radially outward with respect to the fixed center axis 21 are shown and described as being coupled to the variable pin P1 with a phase difference of 90 degrees, the fixing in the embodiment Two coupler links coupled to the variable pins P1 having a phase difference of 180 degrees with respect to each other in a radially outward direction with respect to the central axis 21, and a link coupling to the variable pins P1 with a phase difference of 120 degrees with each other. Three coupler links that are connected to the variable pin P1 having a phase difference of 72 degrees to each other, and five coupler links that are linked to the variable pin P1 having a phase difference of 60 degrees to each other. At least 10 coupler links, such as coupler links, are coupled to the variable pin P1 at a predetermined angle to each other in the circumferential direction of the fixed central axis 21. Implemented way is an implementation which may be substituted as apparent to the art agent.

When the input link 60 rotates in the reverse direction, the coupler link 90, the output link 70, the output shaft 80, and the clutch gear 81 embedded in the input link 60 are fixed to the central shaft. Orbital movement in the reverse direction about the central axis of (21).

At this time, the variable pin (P1) is also eccentric from the center axis of the fixed center axis 21 is subjected to a load by the reverse rotation of the input link 60, to accommodate the variable pin (P1) The variable pin guide portion 21a is also subjected to a load in the reverse rotation direction, so that the one-way clutch bearing 21b is in a non-walking state, and the variable pin P1 is idle in the reverse rotation direction, and the variable The pin guide portion 21a rotates in the reverse rotation direction.

Accordingly, the lever crank mechanism composed of the input link 60, the coupler link 90, the output link 70, the output shaft 80, and the clutch gear 81 does not perform a link movement so that the clutch gear 81 Orbital movement in the reverse direction, and thus the final output shaft 85 that is engaged to the four clutch gear 81 at the same time is to rotate in the reverse direction.

When the final output shaft 85 is rotated in the reverse direction, the clutch gear 81 and the first intermediate gear 87 is in a forward direction about the output shaft 80 without being caught by the one-way clutch bearings 43 and 86. And the second intermediate gear 89 is caught by the one-way clutch bearing 88 to rotate in the opposite direction, so that the first and second intermediate gears 87 and 89 mesh with each other and are in opposite directions. It will rotate smoothly.

Therefore, in the present embodiment, when the electric motor 30 gives the reverse rotational power, the final output shaft 85 is rotated in the reverse direction without stepless speed, the case 50 is rotated in the reverse direction, the case 50 The driving wheel fixedly circumferentially rotates in the reverse direction.

In the above embodiment, the first intermediate gear 87 is circumscribed with one output shaft 80 via the one-way clutch bearing 86, but for stable driving, that is, balanced driving of the continuously variable transmission. Another first intermediate gear may be circumscribed through the one-way clutch bearing in another output shaft 80 arranged with a phase difference of 180 degrees with respect to the one output shaft 80, and in one direction on all output shafts 80. The first intermediate gear may be circumscribed via the clutch bearing.

21; Fixed center axis, 43; One-way clutch bearing, 60; Input link, 70; Output link, 90; Coupler link, P1; Variable pin, S; Reaction

Claims (6)

Hub type continuously variable transmission using a lever crank mechanism that links one input link 60, a plurality of coupler links 90, and the same number of output links 70 as the number of coupler links 90 together. To
The case 50 is fixedly inscribed in the hub of the drive wheel,
A fixed center axis 21 having the same center axis as the center of rotation of the drive wheel is rotatably inscribed in the case 50,
A variable pin guide portion 21a is circumscribed on the fixed central shaft 21 via a one-way clutch bearing 21b.
The input link 60 which is fixedly circumscribed to the fixed central shaft 21 and rotatably circumscribed to the variable pin guide portion 21a by an electric motor 30 which is internally rotatably connected to the case 50. ) Is rotated,
One variable pin P1 for linking the input link 60 and the plurality of coupler links 90 extends in the radial direction of the fixed center shaft 21 to be formed in the variable pin guide part 21a. The rail groove 65 is eccentrically inserted at the center of rotation of the input link 60 while being elastically pressed in the radially outward direction by the reaction means S,
A plurality of output shafts of the plurality of output links 70 via a plurality of link pins P2 for link coupling the plurality of coupler links 90 and the plurality of output links 70 and one-way clutch bearings 43. A plurality of clutch gears 81 circumscribed by 80 are mounted on the input link 60 to revolve with the same rotational center as that of the input link 60.
The output gear 82 which rotates with the same rotation center as the rotation center of the input link 60 has a plurality of clutch gears 81 circumscribed via the one-way clutch bearing 43 on the plurality of output shafts 80. Are engaged in,
The final output shaft 85 fixedly circumscribed to the output gear 82 is fixed to the case 50 with the same rotation center as that of the case 50.
At least one of the plurality of output shafts 80 is externally provided with a first intermediate gear 87 via a one-way clutch bearing 86, and the final output shaft 85 is provided with a one-way clutch bearing 88 therebetween. The second intermediate gear 89 is circumscribed, and the third output gear 85 is circumscribed.
The first intermediate gear 87 is provided with a hub type continuously variable gear having two gear parts 87a and 87b to be engaged with the second and third intermediate gears 89 and 84 at the same time. Device. The method of claim 1,
The one-way clutch bearing 21b is in a stepped state with respect to the forward rotation of the variable pin guide portion 21a and a non-stepped state with respect to the reverse rotation.
The one-way clutch bearings 43 are all stepped in the same direction to each of the plurality of clutch gears 81, and transmit power to the clutch gear 81 in the reverse rotation direction when the output shaft 80 rotates in the reverse direction. When the clutch gear 81 rotates forward, power is transmitted to the output shaft 80 in the forward rotation direction.
The one-way clutch bearing 86 transmits power to the first intermediate gear 87 in the reverse rotation direction when the output shaft 80 is reversely rotated, and at the forward rotation of the first intermediate gear 87, the output shaft ( 80) to forward power in the forward direction,
The one-way clutch bearing 88 transmits power to the second intermediate gear 89 in the forward rotation direction at the time of forward rotation of the final output shaft 85 and at the end of the reverse rotation of the second intermediate gear 89. Hub type continuously variable transmission, characterized in that for transmitting power to the output shaft 85 in the reverse rotation direction. 3. The method according to claim 1 or 2,
The plurality of link pins P2 are spaced apart from each other with the same phase difference in the rotational trajectory of the input link 60, and the plurality of output shafts 80 also have the same phase difference in the rotational trajectory of the input link 60. Hub type continuously variable transmission, characterized in that spaced apart with. 3. The method according to claim 1 or 2,
One end of the fixed central axis 21 extends to one side in the direction of the rotational center axis of the case 50, protrudes out of the case 50, and the other end of the fixed central axis 21 is the case 50. Extend in the other direction in the direction of the center of rotation of the axis of the case 50,
In the variable pin guide portion 21a circumscribed to the other end of the fixed central shaft 21, an input link 60 having a drum shape with the bearing 42 interposed therebetween with respect to the variable pin guide portion 21a. Rotatably circumscribed,
The input link 60 is rotatably circumscribed in a state in which a bearing 44 is interposed between a boss 51 formed on an inner surface of the case 50 facing the fixed central axis 21. Hub type continuously variable transmission. 3. The method according to claim 1 or 2,
The electric motor 30 is disposed radially inward with respect to the stator 32 and the stator 32 fixedly inscribed in the housing 31 of the electric motor 30, and rotates on the fixed central axis 21. A rotor 33 possibly circumscribed; The input gear coupled to the rotor 33 and rotatably circumscribed to the fixed central shaft 21 and the input gear 34 to be engaged with the input gear 34 in the case 50. 34. A hub type continuously variable speed gear comprising: a reduction gear (35) which rotates with a rotation center and a biased rotation center. 6. The method of claim 5,
The input link 60 is spaced apart from each other in the axial direction of the fixed central axis 21, the first token shape portion 61 and the second token shape portion 62 and the first and first token shape portion It includes a fastening member 63 for coupling in a state.
A ring-shaped rack gear 64 having gears formed on an inner circumferential surface thereof is mounted on an outer rim of the first token-shaped portion 61 of the input link 60 facing the reduction gear 35 so that the input link 60 Rotating movement with the input link 60 having the same rotation center as the rotation center of the),
The rack gear 64 is a hub type continuously variable transmission, characterized in that the drive gear is coupled to the reduction gear (35).

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