KR20100076361A - Continuously variable transmission - Google Patents

Abstract

PURPOSE: A continuously variable transmission is provided to improve the durability of an input shaft by arranging four link parts which conduct link-movement with a phase difference each other on a same 2D level and are bilaterally and vertically symmetrical. CONSTITUTION: An input shaft(110) receives the torque inputted from the outside. A plurality of slave gears receives the driving power from an input shaft by being arranged in the peripheral direction of the input shaft with a uniform phase difference. A variable input link(130) is rotatably connected to the input shaft by receiving the torque of the input shaft. A disk plate(140) is rotatably combined in the leading end of the variable cam and is rotated around the rotational center of the variable input link. A plurality of output links have an one end which is internally combined by interposing a bearing capable of rotating a plurality of slave gears in a single direction after receiving the bidirectional torque only in a single direction. A plurality of coupler links have a different end which is rotatably linked and combined with a plurality of output links.

Description

Continuously Variable Transmission

The present invention relates to a compact continuously variable transmission 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.

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

The present invention provides an input shaft for receiving a rotational force input from the outside; A plurality of driven gears disposed radially outward with respect to the input shaft with the input shaft interposed therebetween, and having a constant phase difference in the circumferential direction of the input shaft to receive power from the input shaft; Reaction force is coupled to the input shaft to receive the rotational force of the input shaft rotationally rotatably, the urging force to elastically radially outwardly press the variable cam rotational radius is variable by an external load with the variable cam A variable input link receiving; Rotatably coupled to the distal end of the variable cam to revolve about the center of rotation of the variable input link according to the rotational movement of the variable input link; A disk plate which rotates revolving about a rotation center of the variable input link together with a variable cam; A plurality of output links, one end of which is inscribed and coupled through a one-way clutch bearing that receives the bidirectional rotational force transmitted to each of the plurality of driven gears in only one direction and rotates each of the plurality of driven gears in one direction; And a plurality of couplers of the same length having one end rotatably linked to each of the plurality of holes formed on the disk plate having the same phase difference as the phase difference, and the other end rotatably linked to each of the plurality of output links. It consists of a continuously variable transmission with a link.

In the continuously variable transmission of the present invention, the four link portions linking with the phase difference from each other are arranged at the same two-dimensional level and symmetrically up, down, left, and right, so that the continuously variable transmission becomes compact, and the torsional load doubled to the input shaft can be obtained. Without this, the input shaft enhances durability, so that the link portions can turn the pivoting movement in the clockwise motion counterclockwise or counterclockwise clockwise at the correct time.

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

5 and 6 show a conceptual view of a continuously variable transmission of this embodiment as a perspective view and FIG. 7 shows a continuously variable transmission of FIG.

The continuously variable speed transmission apparatus of the present embodiment includes: an input shaft 110 rotatably mounted to the frame F to receive a rotational force input from the outside; 4 which is disposed radially outward with respect to the input shaft 110 with the input shaft 110 interposed therebetween to receive power from the input shaft 110 while being rotatably mounted to the frame with a phase difference of 90 degrees. Two driven gears 121, 122, 123, 124; The variable cam P, which is coupled to the input shaft 110 to be rotated in a rotational manner by receiving the rotational force of the input shaft 110 and whose rotation radius is variable by an external load, is elastically pressed radially outward. A variable input link 130 accommodating a reaction force device S together with the variable cam P; The rotatably coupled to the front end of the variable cam (P) is revolving about the center of rotation of the variable input link 130 in accordance with the rotational movement of the variable input link (130) A disk plate 140 that rotates revolving about the center of rotation of the variable input link 130 together with the variable cam P; One-way clutch bearing which receives two-way rotational force transmitted to each of the four driven gears 121, 122, 123, and 124 only in one direction and rotates each of the four driven gears 121, 122, 123, and 124 in one direction ( Four output links 171, 172, 173, and 174, one end of which is inscribed and coupled via 151, 152, 153 and 154; And one end rotatably linked to each of the four holes formed with the phase difference of 90 degrees in the disk plate 140, and the other end rotatably connected to each of the four output links 171, 172, 173, and 174. It includes four coupler links 191, 192, 193, 194 of equal length that are link coupled.

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.

Here, in the driving coupling method between the input shaft 110 and the variable input link 130, as shown in Figure 5, the variable input link 130 is fixedly inscribed at the front end of the input shaft 110 The variable input link 130 may be fixedly circumscribed on the outer circumferential surface of the input shaft 110.

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 the annular output shaft G4, driven sprockets, driven gears, and driven pulleys, which are not shown, of the external device to which power should be transmitted, are externally fixed to drive the external device.

In the description of the embodiments, the reaction force device is not only an elastic spring, as shown in FIG. 6, but also connected to a hydraulic or pneumatic circuit for advancing and reversing the cylinder according to the load transmitted to the reaction force device. It may be a pneumatic cylinder or a hydraulic cylinder.

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 outside rotates the variable input link 130 to rotate the variable cam P arranged to be eccentrically accommodated in the variable input link 130. Cam (P) rotational force is the disk plate 140 rotatably coupled to the variable cam (P) by the individual pin not shown in the variable cam (P) with respect to the center of rotation of the variable input link (130) Rotate by revolution.

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 the four output links 171, 172, 173, 174 linked to each of the four coupler link (191, 192, 193, 194) through In the case of pivoting at an angle for driving, the other output link 174 having a phase difference within -180 degrees with respect to the one output link 171 is forward-reversed in the forward direction, 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, the other output having a phase difference of 180 degrees or more with respect to the one output link 171 Pivoting the 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.

Here, a large load transmitted from the annular output shaft G4 provided in the output gear G3 is transmitted to the reaction force device S through a driven gear, an output link, a coupler link disk plate, and a variable cam, so that the variable cam ( When P) approaches the central axis of the variable input link 130, the revolving radius of the variable cam P becomes small, so that the angle of the turning reciprocating motion of the output link 171, 172, 173, 174 is The smaller the driven gears 121, 122, 123, and 124 become the 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 cam P moves away from the central axis of the variable input link 130, the revolving radius of the variable cam P increases, so that the angle of the turning reciprocating motion of the output links increases so that the driven gear Are in fast 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.

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 ten output links, such as five output links coupled to each other and six output links coupled to a disk plate with a phase difference of 60 degrees to each other, are at a predetermined angle 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 A.

1 is a conceptual view showing an embodiment of a conventional continuously variable transmission at an initial position;

FIG. 2 is a conceptual diagram illustrating the 180 degree phase shifted state of FIG. 1;

3 is a front view showing another conventional embodiment,

4 is a side view conceptually illustrating the continuously variable transmission of FIG. 3;

5 is a perspective view of the continuously variable transmission of the present invention as viewed from the input shaft side;

6 is a perspective view of the continuously variable transmission of FIG. 5 as seen from the disk plate side, and

7 is a partial cross-sectional view of FIG. 5.

Claims (7)

An input shaft 110 receiving a rotation force input from the outside; A plurality of driven members disposed radially outward with respect to the input shaft 110 with the input shaft 110 interposed therebetween, and having a constant phase difference in the circumferential direction of the input shaft to receive power from the input shaft 110. Gear; The variable cam P, which is coupled to the input shaft 110 to be rotated in a rotational manner by receiving the rotational force of the input shaft 110 and whose rotation radius is variable by an external load, is elastically pressed radially outward. A variable input link 130 accommodating a reaction force device S together with the variable cam P; The rotatable coupled to the front end of the variable cam (P) is revolving about the center of rotation of the variable input link 130 in accordance with the rotational movement of the variable input link (130) A disk plate 140 that rotates revolving about the center of rotation of the variable input link 130 together with the variable cam P; A plurality of output links, one end of which is inscribed and coupled through a one-way clutch bearing that receives the bidirectional rotational force transmitted to each of the plurality of driven gears in only one direction and rotates each of the plurality of driven gears in one direction; And A plurality of ends of the same length, one end of which 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 the other end of which is rotatably linked to each of the plurality of output links. Continuously variable speed transmission comprising two coupler links. The method of claim 1, The drive coupling method between the input shaft 110 and the variable input link 130 is a continuously variable transmission device, characterized in that the variable input link (130) is fixedly inscribed at the front end of the input shaft (110). The method of claim 1, In the drive coupling method between the input shaft 110 and the variable input link 130, the continuously variable transmission device, characterized in that the variable input link 130 may be fixedly circumscribed on the outer peripheral surface of the input shaft (110). The method of claim 1, Stepless speed change device, characterized in that one output gear (G3) rotatably circumscribed to the base end of the input shaft 110 is rotated in engagement with all of the plurality of driven gear. The method of claim 4, wherein Endless output shaft (G4) is formed in one output gear (G3) protruding toward the base end of the input shaft 110, the annular output shaft (G4) having a rotation center and the concentric rotation axis of the input shaft 110 is integrally formed Gearbox. The method of claim 5, And the driven sprocket, the driven gear, or the driven pulley of the external device to which power is to be transmitted to the annular output shaft (G4). The method of claim 1, And the reaction force device is a pneumatic cylinder or hydraulic cylinder connected to an elastic spring or a hydraulic or pneumatic circuit for advancing and retracting the cylinder according to the load transmitted to the reaction force device.

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