KR101029316B1 - Continuously Variable Transmission of Hub Type - Google Patents

Abstract

Hub type continuously variable transmission device of the present invention including an input shaft 110 pivotally mounted on one side of the case 211 fixedly inscribed to the hub of the drive wheel and an idle shaft (S2) pivotally mounted on the other side of the case, A driven sprocket (D) is fixedly circumscribed on one side of the input shaft protruding out of one side of the case, and a variable input link is rotatably inserted in the center of the standing frame in the case, and on one side of the variable input link (130) The leading end of is rotated and inserted, radially outward with respect to the variable input link with the variable input link interposed therebetween, and a plurality of output links are pivotally mounted on the frame with a constant phase difference in the circumferential direction of the input shaft. On the side there is a built-in reaction device (S) for urging the variable cam (P), the rotation radius of which is variable by an external load, in the radially outward direction. At the end, the disk plate 140 rotating idling with respect to the rotation center of the variable input link is pivotally coupled, and each of the output links is externally driven with a one-way clutch bearing, and the disk plate has a hole having the same phase difference as the phase difference. One end of the coupler link of the same length is link-coupled, the other end of the coupler link is link-coupled to each of the output links, and the output gear G3 which engages all the driven gears is rotated and circumscribed at the base of the input shaft, and the output gear The annular output shaft (G4) protruding toward the base end of the input shaft and concentric with the rotation center of the input shaft is integrally formed, and the annular output shaft is fixedly inscribed on one side of the case.

Coupler link, variable input link, output link, input shaft, driven shaft

Description

Continuously Variable Transmission of Hub Type

The present invention relates to a hub type compact continuously variable transmission device in which the instantaneous torque output is increased or decreased automatically according to the increase or decrease of the load acting on the output shaft.

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 variable transmission 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 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 coaxial 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.

The present invention has its problems in solving the above problems.

The present invention relates to a hub type continuously variable transmission including an input shaft rotatably mounted to one side of a case fixedly inscribed to a hub of a driving wheel and an idler shaft rotatably mounted to the other side of the case. A driven sprocket is fixedly circumscribed on one side of the input shaft protruding out of one side of the case, and a standing frame is built in the case, and a variable input link is rotatably inserted in the center of the frame. A front end of the input shaft is rotatably inserted at one side of the variable input link, and is disposed radially outward with respect to the variable input link with the variable input link interposed therebetween to have a constant phase difference in the circumferential direction of the input shaft. Multiple output links are rotatable It is, and has a built-in reaction force device to the other side of the turning radius of said variable pressure input link in a radial outward direction by elastically variable available variable cam by an external load, has the leading end of the variable cam A disk plate rotating in rotation with respect to the center of rotation of the variable input link is rotatably coupled with a variable cam. A plurality of driven gears are externally connected to each of the plurality of output links via a one-way clutch bearing. One end of a plurality of coupler links of the same length is rotatably linked to each of the plurality of holes formed to have the same phase difference as the phase difference at One output gear rotated in engagement with all of the plurality of driven gears at the base end of the input shaft is rotatably circumscribed, and the one output gear protrudes toward the base end of the input shaft and is connected to the input shaft. Center of rotation and concentricity of An annular output shaft having an all-axis line is integrally formed, and the annular output shaft is a hub type continuously variable transmission that is fixedly inscribed on one side of the case.

According to the present invention, four link parts linking with phase difference from each other are arranged at the same two-dimensional level and symmetrically in the up, down, left, and right directions, thereby making the continuously variable transmission compact and not giving the torsional load doubled to the input shaft. Enhancing this durability, the link portions can turn the pivoting movement in a clockwise motion counterclockwise or counterclockwise in a clockwise direction.

Moreover, according to the compact continuously variable transmission of the present invention as described above, even when loaded into the hub of the driving wheels such as bicycles, electric bicycles, electric wheel chairs, electric cars, it does not protrude prominently. Does not hurt the appearance of the back.

Hereinafter, an embodiment according to the present invention will be described with reference to FIGS. 5 to 7, which are accompanying drawings.

FIG. 6 is a cross-sectional view showing an embodiment of a hub type continuously variable transmission that can be applied to a hub of a driving wheel not shown, and FIG. 6 is a perspective view of the hub and the first and second support pieces as viewed from the input shaft side. 7 is shown as a perspective view from the disc plate side with the case and the second support piece removed.

The hub type continuously variable transmission of this embodiment includes an input shaft 110 which is rotatably mounted through one side of a case 211 fixedly inscribed to a hub of a driving wheel (not shown) via a bearing B1. The other side of the case 211 includes an idle shaft (S2) is rotatably mounted through the bearing (B2).

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

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 front end of the variable cam (P) is revolved about the center of rotation of the variable input link 130 in accordance with the rotational movement of the variable input link (130) Together with the variable cam (P) is a disk plate 140 that rotates about the rotation center of the variable input link 130 is rotatably coupled.

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 stepped on the four driven gears 121, 122; 123, 124 in the same direction, that is, clockwise or counterclockwise, respectively. (121, 122; 123, 124) is 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.

The continuously variable transmission of this embodiment having such a 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 is rotated by revolution,

Four coupler links 191, 192, 193, and 194 coupled to the disc plate 140 by the orbital motion of the disc plate 140 at 0 degrees to 90 degrees. For example, one output link 171 of four output links 171, 172, 173, and 174 linked to each of the four coupler links 191, 192, 193, and 194 is actually driven. In the case of pivoting at a predetermined angle for the other output link, the other output link 174 having a phase difference within -180 degrees with respect to the one output link 171 forward and backward rotation, and the one output link ( The other output link 172 having a phase difference within +180 degrees with respect to 171 in the forward turning direction, and the other output link having a phase difference of more than 180 degrees with respect to the one output link 171 Pivoting 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 increases to increase the angle of the turning reciprocating motion of the output links. The driven gears are then in the 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 continuously variable transmission of the present embodiment can be continuously changed.

In this embodiment, the input shaft 110 is a hollow shaft. If the input shaft 110 is a hollow type, it is preferable in that it can insert a stop portion (not shown) that can control the upper limit of the variable cam (P) in the radially outward direction through the hollow portion of the input shaft (110). Of course.

Although the four output links are radially outward with respect to the input shaft 110 in this embodiment as shown and described as being coupled to the disk plate with a phase difference of 90 degrees, in this embodiment radially outward with respect to the input shaft 110. Two output links coupled to the disk plate with a phase difference of 180 degrees to each other, three output links coupled to the disk plate with a phase difference of 120 degrees to each other, and linked to the disk plate with a phase difference of 72 degrees to each other. At least 10 output links, such as five output links coupled to each other and six output links coupled to a disk plate having a phase difference of 60 degrees with each other, are fixed to each other in the circumferential direction of the input shaft 110. Implementation method that can be linked to the disk plate with the implementation method that can be obviously substituted to those skilled in the art to be.

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 conceptually illustrates an embodiment of the present invention;

FIG. 6 is a view illustrating a continuously variable transmission that is adapted to a hub type based on the concept of FIG. 5. FIG.

Claims (5)

And an input shaft 110 rotatably mounted to one side of the case 211 fixedly inscribed to the hub of the driving wheel, and an idle shaft S2 rotatably mounted to the other side of the case 211. Hub type continuously variable transmission, A driven sprocket D is fixedly circumscribed on one side of the input shaft 110 protruding out of one side of the case 211, In the case 211 is a standing frame (F) is built, The variable input link 130 is rotatably inserted in the center of the frame (F), On one side of the variable input link 130 is the front end of the input shaft 110 is rotatably inserted, A plurality of output links are arranged in the frame F with a predetermined phase difference in the circumferential direction of the input shaft 110 by being disposed radially outward with respect to the variable input link 130 with the variable input link 130 therebetween. Rotatably mounted, The other side of the variable input link 130 has a built-in reaction device (S) for urging the variable cam (P), the rotation radius is variable by an external load elastically in the radial outward direction, At the tip of the variable cam (P) is The disk plate 140 is rotatably coupled to the rotation center of the variable input link 130 with a variable cam (P), Each of the plurality of output links has a plurality of driven gears circumscribed through one-way clutch bearings, One end of a plurality of coupler links of the same length is rotatably linked to each of the plurality of holes formed in the disk plate 140 having the same phase difference as the phase difference, and each of the plurality of coupler links is connected to each of the plurality of output links. The other end of the is rotatably linked, One output gear G3 rotatably engaged with all of the plurality of driven gears is rotatably circumscribed at the base end of the input shaft 110, and one output gear G3 is rotatably circumscribed. An annular output shaft G4 protruding toward the proximal end and having a rotation center and a concentric rotation axis of the input shaft 110 are integrally formed. The annular output shaft (G4) is a hub type continuously variable transmission, characterized in that the fixed inscribed on one side of the case (211). The method of claim 1, Hub type continuously variable transmission device, characterized in that the front end of the input shaft 110 is rotatably inserted in one state of the variable input link (130) via the one-way clutch (C). The method of claim 1, And the one-way clutch bearings are all stepped in the same rotational direction to each of the plurality of driven gears. The method of claim 1, 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. Hub-type continuously variable transmission device, characterized in that the other end is fixed to the tip of the second support piece 230, the base end is standing up via the bearing (B4) to the boss (212). The method of claim 1, The reaction force device is a hub type continuously variable transmission device, characterized in that the pneumatic cylinder or hydraulic cylinder connected to the hydraulic spring or pneumatic circuit for advancing and retracting the cylinder in accordance with the load transmitted to the reaction force device.

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