KR101327332B1 - continuously variable transmission of hub type - Google Patents

continuously variable transmission of hub type Download PDF

Info

Publication number
KR101327332B1
KR101327332B1 KR1020110031969A KR20110031969A KR101327332B1 KR 101327332 B1 KR101327332 B1 KR 101327332B1 KR 1020110031969 A KR1020110031969 A KR 1020110031969A KR 20110031969 A KR20110031969 A KR 20110031969A KR 101327332 B1 KR101327332 B1 KR 101327332B1
Authority
KR
South Korea
Prior art keywords
link
input link
output
plurality
center
Prior art date
Application number
KR1020110031969A
Other languages
Korean (ko)
Other versions
KR20120114462A (en
Inventor
신용철
신현우
Original Assignee
신현우
신용철
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 신현우, 신용철 filed Critical 신현우
Priority to KR1020110031969A priority Critical patent/KR101327332B1/en
Priority claimed from PCT/KR2011/004233 external-priority patent/WO2012011662A2/en
Publication of KR20120114462A publication Critical patent/KR20120114462A/en
Application granted granted Critical
Publication of KR101327332B1 publication Critical patent/KR101327332B1/en

Links

Images

Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/76Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with an orbital gear having teeth formed or arranged for obtaining multiple gear ratios, e.g. nearly infinitely variable
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H37/00Combinations of mechanical gearings, not hereinbefore provided for
    • F16H37/12Gearings comprising primarily toothed or friction gearing, links or levers, and cams, or members of at least two of these types
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H35/00Gearings or mechanisms with other special functional features
    • F16H2035/001Gearings with eccentric mounted gears, e.g. for cyclically varying ratio

Abstract

The present invention relates to a hub type continuously variable speed transmission apparatus using 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. A variable pin for rotating by the electric motor built into the transmission and linking the input link and the plurality of coupler links to the load while preventing rotation and rotation in the state eccentrically disposed at the rotation center of the input link. According to the present invention, the input link is elastically variable in the radial direction of the rotation of the input link, and is 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. A plurality of clutch gears are the same as the rotation center of the input link By revolving around the center and engaging the output gears with the plurality of clutch gears, a variable pin, which is the most important component for continuously variable transmission, that is, a variable pin for linking the input link and the coupler link, is formed at the center of the input link's rotation. Easily and eccentrically positioning is possible, while at the same time it is possible to provide a compact unit continuously variable transmission with a built-in motor, it is a hub type of simple type with simple appearance without being enlarged externally A continuously variable transmission can be provided.

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 plurality of output links through 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.

The present invention is arranged eccentrically at the center of rotation of the input link without idling the variable pin, which is the most important component for continuously variable, that is, the variable pin for link coupling the input link and the coupler link that is driven by the motor, There is a problem in solving the above-described problems by making the eccentric positioning of the variable pin structurally easy.

The present invention provides a hub type continuously variable speed transmission apparatus using a lever crank mechanism in which an input link, a plurality of coupler links and an output link equal to the number of coupler links are connected to each other, wherein the input link is the continuously variable transmission. And a variable pin for rotating the input link and the coupler link coupled to the input link and the plurality of coupler links so as not to rotate and rotate in a state that the input pin is eccentrically disposed at the rotation center of the input link. A plurality of links externally connected to the output shafts of the plurality of output links through link pins that elastically vary in a radial direction of the input link and link the plurality of coupler links and the plurality of output links, and one-way clutch bearings. The clutch gear has the same center of rotation as the center of rotation of the input link The problem can be solved by allowing the idler to rotate and engaging the output gear with the plurality of clutch gears.

The present invention is to structurally determine the eccentric positioning of the variable pin, that is, the variable pin for link coupling the input link and the coupler link, which is the most important component for the continuously variable by the problem solving means as described above. It can be done easily.

In addition, the present invention makes it possible to provide a continuously variable transmission in a compact unit in the state in which the electric motor is built by the problem solving means as described above, the appearance of the hub type of the simple type, the appearance is simple and not enlarged while the motor is built in A continuously variable transmission can be provided.

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;
8 is a view showing the hub-type continuously variable transmission of this embodiment,
9 is a front view showing a coupling state between the variable pin and the fixed shaft of Figure 8,
10 is an enlarged perspective view of the variable pin of FIG. 8 and FIG.
11 shows a separate embodiment;

Hereinafter, an embodiment according to the present invention will be described with reference to FIGS. 8 to 9, which are accompanying drawings.

8 shows a separate 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.

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, the reduction gear 35 which rotates with the rotation center and the biased rotation center is included.

At the other end of the fixed central shaft 21, the drum-type input link 60 is rotatably circumscribed with respect to the fixed central shaft 21 in a state of interposing a bearing 42 therebetween. 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 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 with the input link 60 having the same center of rotation as the center of rotation).

A pinion gear 36 is interposed between the rack gear 64 and the reduction gear 35.

The pinion gear 36 is coupled to the reduction gear 35 to have the same rotation center as the rotation center of the reduction gear 35 and has a center that is biased with the rotation center of the rack gear 64. Rotating with 35, and is engaged with the gear portion of the rack gear 64 to transfer power to the rack gear (64).

In this embodiment, it is assumed that the pinion gear 36 is interposed between the rack gear 64 and the reduction gear 35, but as shown in FIG. 11, the reduction gear 35 is directly It may be engaged with the rack gear 64 so that the reduction gear 25 also acts as a pinion gear.

The other end of the fixed central shaft 21 is formed with a long guide rail groove 65 in the radial direction of the rotation of the input link 60, the guide rail groove 65 is the guide rail groove 65 A variable pin (P1) movable along is mounted eccentrically at the center of rotation of the input link (60), and the variable pin (P1) is elastic in the direction of rotation of the input link (60) by an external load. In order to be variable, the reaction force device (S; see Fig. 9), such as a spring built in the guide rail groove 65 in the state that the elastically pressing the variable pin (P1) in the radially outward direction Is supported by.

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 outwardly and arranged at a phase difference of 90 degrees and one end is coupled to each other end of each of the four coupler links 90 so as to radially outward from the center of rotation of the case 50. Four output links 70 (only two are shown in FIG. 8) are arranged to be spaced apart by 90 degrees out of phase.

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.

The one-way clutch bearings 43 are all stepped on the four clutch gears 81 in the same direction, that is, clockwise or counterclockwise, so as to rotate the clutch gear 81 clockwise or counterclockwise. .

In addition, the boss 51 formed on the inner surface of the case 50 facing the fixed central axis 21 has an output gear 82 fixedly mounted to have the same rotation center as that of the case 50. In this state, the four clutch gears 81 are engaged with all of the four clutch gears 81.

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

When the motor 30 embedded in the case 50 is operated, power of the motor is sequentially transmitted to the input gear 34, the reduction gear 35, and the pinion gear 36, and the pinion gear 36 is Power is transmitted to the input link 60 so that the input link 60 rotates about the central axis of the fixed central axis 21.

As the input link 60 rotates, a coupler link 90, an output link 70, an output shaft 80, and a clutch gear 81 embedded in the input link 60 are fixed to the central shaft 21. Orbit around the central axis.

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.

Between the output shaft 80 and the clutch gear 81 fixedly inscribed at the other end of the output link 70 transmits only the forward rotation of the output link 70 to the clutch gear 81, respectively. Since the one-way clutch bearing 43 is interposed, eventually, the output gear 82 meshed with the four clutch gears 81 always rotates in the forward direction when the electric motor 30 is driven. As the case 50 rotates in the forward direction, 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 (P) 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 separate embodiment, although the four coupler links are radially outward with respect to the fixed center axis 21, the coupler links are linked to the variable pin P1 with a phase difference of 90 degrees. Two coupler links linked to the variable pins P1 having a phase difference of 180 degrees to each other in a radially outward direction with respect to the fixed central axis 21, and a link to the variable pins P1 having a phase difference of 120 degrees to each other. 3 coupler links coupled to each other, 5 coupler links coupled to the variable pin (P1) having a phase difference of 72 degrees to each other, 6 coupled to the variable pin (P1) having a phase difference of 60 degrees to each other At least 10 coupler links, such as two coupler links, are linked to the variable pin P1 at a predetermined angle to each other in the circumferential direction of the fixed central axis 21. Implementation way hapdoel is an implementation which may be substituted as apparent to the art agent.

In this embodiment, the fixed center axis 21 is a hollow shaft, as shown in FIG.

The front end of the hollow portion 22 of the fixed central shaft 21 is able to flow with the guide rail groove 65.

The spring 23 is inserted into the hollow portion 22. As shown in Figure 8 to 10, the body 66 of the variable pin (P1) that is slidably inserted into the guide rail groove (65) the spring as the reaction means (S) and the spring 23 A-shaped groove 67 exposed to the) is formed.

One end of the reaction means (S) is inserted into the L-shaped groove (67) to elastically press the ceiling of the L-shaped groove (67).

The tip end of the cam portion 24 whose proximal end is inserted into the tip end of the spring 23 has a tapered cam surface 25 that converges in the center axis direction of the fixed central axis 21.

The tapered cam surface 25 is inserted into the L-shaped groove 67 to be in line contact with the ceiling of the L-shaped groove 67.

The pressing piece 27 for pressing the base end of the spring 23 is inserted into the hollow portion 22 of the fixed central shaft 21.

The base end of the hollow part 22 is screwed, and the bolt 28 which presses the press piece is fastened to the base end of the hollow part 22.

The bolt 28 adjusts the elastic pressing amount of the spring 23, adjusts the degree of expansion and contraction of the spring 23, and cooperates with the reaction force (S) the displacement amount of the variable pin (P1) according to the load To make adjustments.

In addition, in the above embodiment, in order to drive the driving wheel in the forward direction by the forward and reverse rotational power of the electric motor 30, the variable pin (P1) is described as being elastically linear reciprocating movement mounted on the fixed center shaft (21) However, the present invention is a separate embodiment, in order to manually rotate the driving wheel, as shown in Figure 11, the variable pin (P1) in the fixed center shaft 21 is capable of elastic linear reciprocating motion The variable pin guide portion 21a is mounted separately, and a one-way clutch 21b is interposed between the fixed center shaft 21 and the variable pin guide portion 21a.

The one-way clutch 21b is in a stepped state when the driving wheel is rotated in the forward direction, and the variable pin guide portion 21a is fixed to the fixed center shaft 21, so that the input link 60 is the electric motor 30. Drive wheel rotated in the reverse direction, and in the non-walking state, the variable pin guide portion 21a is fixed to the fixed center shaft 21 and driven in the reverse direction manually. The reverse rotational force transmitted to the case 50 fixedly inscribed at the cutting edge is cut by the clutch gear 81 via the output gear 82, but the one-way clutch interposed between the clutch gear 81 and the output shaft 80. (43) is cut in the direction in which it can be walked, the clutch gear 81 does not rotate, but the load of the reverse rotational force is transmitted to the variable pin (P1), and eventually the one-way clutch 21b is not stepped. A room that can be brought into condition Be variable as to the pin guide portion (21a) is rotated in the reverse direction with respect to the fixed center rod 21 will allow the reverse rotation of the drive wheel.

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

Claims (9)

  1. 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,
    The input link 60 which is fixedly circumscribed to the fixed central axis 21 and rotatably circumscribed to the fixed central axis 21 by an electric motor 30 that is internally rotatable to the case 50. Being rotated,
    One variable pin P1 for linking the input link 60 and the plurality of coupler links 90 extends in a radial direction of the fixed central axis 21 to be formed on the fixed central axis 21. It is inserted into the groove (65) eccentrically 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,
    And the output gear (82) is fixed to the case (50) with the same rotation center as that of the case (50).
  2. The method of claim 1,
    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 of claim 1,
    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,
    At the other end of the fixed central shaft 21, an input link 60 having a drum shape in a state of interposing a bearing 42 is rotatably circumscribed with respect to the fixed central shaft 21,
    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.
  4. The method of claim 1,
    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.
  5. 5. The method of claim 4,
    The input link 60 may include a first token shape portion 61 and a second token shape portion 62 spaced apart from each other in the axial direction of the fixed central axis 21, and the first and second token shape portions ( 61, 62 includes a fastening member 63 for coupling in a state spaced apart from each other.
    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).
  6. 6. The method of claim 5,
    In the input link 60, one end is coupled to one of the variable pins (P1) in a state arranged adjacent to the inner surface of the first token shape portion 61 is radial in the center of rotation of the case (50) One end is coupled to each other end of each of the plurality of coupler links 90 and the plurality of coupler links 90 disposed to have the same phase difference spaced outward and radially outward from the center of rotation of the case 50. Four output links 70 are arranged to be spaced apart by the same phase difference is built in,
    Each other end of each of the plurality of output links 70 is rotatably mounted on an inner surface of the second token shape portion 62 of the input link 60, and radially outwardly from the center of rotation of the case 50. Hub type continuously variable transmission, characterized in that the output shaft 80 is fixedly circumscribed to each of the plurality of output shafts (80) spaced apart by the same phase difference.
  7. The method of claim 3, wherein
    The boss 51 formed on the inner surface of the case 50 facing the fixed central axis 21 is fixed to the output gear 82 having the same rotation center as the rotation center of the case 50. Hub type continuously variable transmission.
  8. The method of claim 3, wherein
    The fixed central shaft 21 has a hollow portion 22,
    The front end of the hollow portion 22 is made available for distribution with the guide rail groove 65,
    Spring 23 is inserted into the hollow portion 22,
    The body 66 of the variable pin (P1) is slidably inserted into the guide rail groove (65) is formed with an L-shaped groove (67) exposed to the reaction means (S) and the spring (23) There is,
    One end of the reaction means (S) is inserted into the L-shaped groove (67) to elastically press the ceiling of the L-shaped groove (67),
    The distal end of the cam portion 24, the proximal end of which is inserted into the distal end of the spring 23, has a tapered cam surface 25 that converges in the central axis direction of the fixed central axis 21,
    The tapered cam surface 25 is inserted into the L-shaped groove 67 to be in line contact with the ceiling of the L-shaped groove 67,
    The pressing piece 27 pressurizing the base end of the spring 23 is inserted into the hollow portion 22 of the fixed central shaft 21,
    The base end of the hollow portion 22 is threaded, and the hub type continuously variable transmission device, characterized in that the bolt 28 for pressing the pressing piece is fastened to the base end of the hollow portion 22.
  9. The method according to any one of claims 1 to 8,
    The fixed central shaft 21 is coupled to the variable pin guide portion 21a in which the variable pin P1 is elastically linearly reciprocated, and is coupled separately.
    A one-way clutch 21b is interposed between the fixed center shaft 21 and the variable pin guide portion 21a.
    And said one-way clutch (21b) is in a stepped state when the drive wheel is rotated in the forward direction, and in a non-walked state when the drive wheel is rotated in the reverse direction.




KR1020110031969A 2011-04-07 2011-04-07 continuously variable transmission of hub type KR101327332B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020110031969A KR101327332B1 (en) 2011-04-07 2011-04-07 continuously variable transmission of hub type

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020110031969A KR101327332B1 (en) 2011-04-07 2011-04-07 continuously variable transmission of hub type
PCT/KR2011/004233 WO2012011662A2 (en) 2010-07-19 2011-06-09 Continuously variable transmission

Publications (2)

Publication Number Publication Date
KR20120114462A KR20120114462A (en) 2012-10-17
KR101327332B1 true KR101327332B1 (en) 2013-11-08

Family

ID=47283568

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020110031969A KR101327332B1 (en) 2011-04-07 2011-04-07 continuously variable transmission of hub type

Country Status (1)

Country Link
KR (1) KR101327332B1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101499934B1 (en) * 2013-08-05 2015-03-10 이춘우 Continuously Variable Transmission

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000335265A (en) 1999-05-24 2000-12-05 Kanzaki Kokyukoki Mfg Co Ltd Vehicle transmission for driving
JP2003508698A (en) 1999-08-27 2003-03-04 エスケイエフ エンジニアリング アンド リサーチ センター ビーブイ Continuously variable transmission system
JP2010076748A (en) 2008-08-29 2010-04-08 Kanzaki Kokyukoki Mfg Co Ltd Traveling system transmission structure of vehicle
KR20100076361A (en) * 2008-12-26 2010-07-06 신용철 Continuously variable transmission

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000335265A (en) 1999-05-24 2000-12-05 Kanzaki Kokyukoki Mfg Co Ltd Vehicle transmission for driving
JP2003508698A (en) 1999-08-27 2003-03-04 エスケイエフ エンジニアリング アンド リサーチ センター ビーブイ Continuously variable transmission system
JP2010076748A (en) 2008-08-29 2010-04-08 Kanzaki Kokyukoki Mfg Co Ltd Traveling system transmission structure of vehicle
KR20100076361A (en) * 2008-12-26 2010-07-06 신용철 Continuously variable transmission

Also Published As

Publication number Publication date
KR20120114462A (en) 2012-10-17

Similar Documents

Publication Publication Date Title
US8985254B2 (en) Pedal driven apparatus having a motor
US8636095B2 (en) Electric power-assisted bicycle
US7004487B2 (en) Continuously variable transmission for bicycles
JP4909322B2 (en) Transmission
JP4768715B2 (en) Continuously variable transmission
CN101115585B (en) Power tool gear-train and torque overload clutch therefor
US7727106B2 (en) Continuously variable transmission
CN1077668C (en) Built-in speed regulator for bicycle
EP2644493A1 (en) Clutch type driving mechanism for hybrid powered vehicle
CN103043171B (en) The driver element of bicycle
US8449426B2 (en) Continuously variable transmission and automobile drive system
JP4524191B2 (en) Rotor controlled transmission
EP2172671B1 (en) Gear device and rotation section structure adapted for industrial robot and using the gear device
TW201446584A (en) Continuously variable transmissions and systems with continuously variable transmissions for coupling with electric motors and human powered machines
KR101066233B1 (en) Reduction gear
JP2008267596A (en) Eccentric gear mechanism and method of transferring turning force thereby
EP2381130B1 (en) Speed change gear
US7942779B2 (en) Turning portion structure of industrial robot
JP5372842B2 (en) Vehicle engine starting device
DE102013220299A1 (en) Vehicle with electric auxiliary drive and steplessly adjustable planetary gearbox
EP2924317A1 (en) Input synthesis gear system
EP1650071A2 (en) Drive arrangement
EP2400184B1 (en) A roller type transmission device
SK278966B6 (en) Gearbox with cross reduction mechanism
CN101070898A (en) Harmonic gear drive

Legal Events

Date Code Title Description
A201 Request for examination
E902 Notification of reason for refusal
E701 Decision to grant or registration of patent right
GRNT Written decision to grant
LAPS Lapse due to unpaid annual fee