KR20100125782A - Device for infinitely variable transmission and method thereof - Google Patents

Abstract

PURPOSE: A device for infinitely variable transmission and a method thereof are provided to implement travel speed which is varied as the gear ratio is increased. CONSTITUTION: A second gear(42) is spaced from the first sun gear on a first sun gear shaft. A worm wheel(21) is arranged between a first planetary gear carrier and a second sun gear. A pair of worm gears is installed in a worm wheel to be faced with each other. A pair of second planet gears(31) is rotated to be circumscribed with second sun gear. A second planet gear carrier(30) has second planet gears penetrated therein. A second bevel gear(32) is contacted with the first bevel gear.

Description

Infinitely variable transmission and method

The present invention is an improvement of Patent No. 631090 (Registered on June 26, 2006, 'Infinite Speed Shifting Method'), and more specifically, the engine speed and output value are maximized and match the speed increasing with the law of gravity acceleration. It relates to an infinite shift method in which the transmission ratio is determined by itself.

In general, a clutch is used to control the rotational force of an input shaft driven by an engine or a motor in an automobile or an industrial machine operated by an engine operation such as a motor. After transmitting to the transmission, the transmission is shifted, and then the power transmission and transmission functions are transmitted to transmit the shifted state to the driven output shaft. That is, in the conventional method, the clutch action and the shift action had to be performed by separate means.

Meanwhile, in the related art, as shown in FIG. 1, the sun gear 2 or the ring gear 3 is driven to rotate rotationally by the driving of the input shaft 1, and the sun gear 2 is driven by the power control mechanism 12. ) Or because of the rotational driving force of the ring gear (3) has a problem that the shift is made only within a certain range.

In order to solve such a problem, the present applicant has been registered and registered in Korean Patent No. 631090. According to the above-mentioned technology, one of the sun gear and the ring gear does not correspond to the output gear after one of the sun gear and the ring gear is output. By constant speed rotation, the optimum speed ratio is continuously determined between the input and output stages, thereby achieving the desired driving speed. Thus, there is provided an infinite speed shifting method that does not require a separate oscillation mechanism and a shift control device.

However, since the patent 631090 is an infinite shift method in which the speed ratio is changed when the engine speed is changed with a constant speed tachometer, the maximum speed of the internal combustion engine is limited depending on the mechanical components, and the speed ratio is also limited. There was a problem that appeared. This will be described in detail as follows.

Looking at the driving of the manual transmission, which is usually 1 to 5 gears, the gravity acceleration law starts from 1 gear and increases from 2 gears to 5 gears in stages, so the maximum speed of the engine is limited when driving at high speed. To work continuously, you must continuously shift to a higher speed ratio, depending on the speed.

However, since the maximum rotational speed of the engine and the transmission ratio of the mechanical components are limited, the maximum speed of the driving is determined by the maximum speed of the engine and the maximum speed of the transmission, and the maximum speed of the engine is determined by the mechanical conditions. This results in maximum fuel efficiency when the engine speed is at optimum engine speed.

If this is called the optimum value and the gravity acceleration is constant at 10 and the resistance is 0, the speed is continuously increased according to the law of gravity acceleration.In the manual transmission with the highest fuel efficiency, the maximum rotation speed and the maximum speed ratio of the engine Because it is limited, it could not increase over a certain speed.

In other words, in order to increase the speed to infinity, the speed of the engine must be infinitely increased or the speed ratio is infinitely increased, either one, but the engine with infinitely increased speed has not been released yet.

The present invention has been made to solve the above problems, and increases the speed ratio to a value that corresponds to the speed of the speed increase when the running speed increases according to the law of gravity acceleration, that is, the infinite speed shifting speed that the speed is the speed ratio. It aims to provide.

The above object of the present invention and the first sun gear is axially rotated; A plurality of first planetary gears which are externally rotated with the first sun gear; A ring gear having a first planetary gear carrier and an inner circumferential surface thereof connecting the first planetary gears to an outer circumferential surface of the first planetary gears; A second sun gear installed on an axis of the first sun gear and spaced apart from the first sun gear; A worm wheel provided between the first planetary gear carrier and the second sun gear; A pair of worm gears installed on the worm wheel so as to face each other and having at least one first bevel gear; A pair of second planetary gears which are externally rotated with the second sun gear; A second planetary gear carrier which penetrates the axes of the second planetary gears and connects the second planetary gears; A second bevel gear that is in contact with the first bevel gear at the shaft end of the second planetary gear; It is achieved by providing an endless transmission, characterized in that configured to include.

According to another aspect, the worm wheel is formed on the outer circumferential surface of the ring gear, or is formed on the outer circumferential surface of the connecting portion configured to be adjacent to the front surface of the second sun gear in the ring gear.

In addition, at least one bearing is installed between the inner circumferential surface of the connecting portion and the outer circumferential surface of the driven output shaft and between the outer circumferential surface of the connecting portion and the inner circumferential surface of the second planetary gear carrier.

Infinite speed shift method of the present invention, by using the infinite shift gear manufactured in the above-described structure, the first planetary gear carrier as the input terminal, the first sun gear and the second sun gear as the output end of the second external to the second sun gear A second bevel gear that interlocks with the second sun gear while rotating the circumference of the second sun gear when the rotation speed of the worm wheel is w when the planetary gear rotates one circumference of the second sun gear; And driving the first bevel gear of the worm gear in contact with the worm wheel interlocked with the ring gear so that the ring gear rotates forward, stop and reverse rotation of the first sun gear and the second sun gear as output terminals according to the value of w. do.

, 일 때, 링기어의 회전수 x =

인 관계를 갖고, 변속비(제1선기어의 회전수) y = -3x + 4 이며, 상기 링기어의 회전수 x와 웜휠의 회전수 w와의 관계에서, x = w 일 때 y는 정지하고, x > w 일 때 y는 정회전하고, x < w 일 때 y는 역회전하는 것을 특징으로 한다.In the infinitely variable method, S = number of revolutions of the first sun gear, C = number of revolutions of the first planetary gear carrier, s = number of teeth of the first sun gear, r = number of teeth of the ring gear, A =

,,, Rotational speed of ring gear x =

Relationship, and the speed ratio (speed of the first sun gear) y = -3x + 4, y is stopped when x = w in the relationship between the rotation speed x of the ring gear and the rotation speed w of the worm wheel, and x When y> y rotates forward, when x <w y is reverse rotation.

In the infinite shift method of the present invention, since the running speed is the speed ratio, the speed ratio increases with the increase of the speed according to the law of gravity acceleration, so that the state of the engine is always at the optimum state with the acceleration of gravity 10 and the speed increases.

For example, a typical manual transmission engine may run at about 240 km when the engine rotates at 3,000 rpm per minute and the driving speed is about 120 km / h and the fuel economy is 12 km / l at five speeds, the highest speed. 20 liters is consumed. To maintain the running speed at 120 km / h, the engine speed must be maintained at 3,000 rpm.

According to the present invention, since the speed increases in accordance with the acceleration law of gravity using the same engine as above, the engine speed must be lowered by the rate of increase of the speed ratio in order to maintain the speed of 120 km / H, .

That is, while driving about 240 km, the total rotational speed of the engine is reduced by ½ compared to the conventional manual transmission, and fuel consumption is about 50%, which is about 10 liters of fuel. This can be expected to save about 35% more fuel than conventional, even considering both mechanical losses and resistance.

Infinite speed shifting method of the present invention is suitable for a transmission of a high-speed railway train, it can be applied when manufacturing two-wheeled vehicle and a pollution-free vehicle using a battery.

In addition, it is possible to save energy by greatly improving the fuel economy of the car, and when applied to a bicycle, the same effect can be obtained, such as to increase the use rate of the bicycle and to solve the traffic shortage.

Hereinafter, the present invention will be described in detail with reference to the accompanying drawings.

FIG. 2 is a cross-sectional view showing an infinite shift apparatus according to the present invention, FIG. 3 is an exploded perspective view showing the first and second sun gears, the first planetary gear carrier and the ring gear of FIG. 2, and FIG. 4 is the worm wheel of FIG. And a worm gear is a plan view, Figure 5 is a side view of Figure 4, Figure 6 is a cross-sectional view showing the input and output direction of the infinitely variable method according to the present invention.

As shown in FIGS. 2 to 6, the infinitely variable speed shift apparatus according to the present embodiment includes a plurality of first planetary gear carriers 10 and a plurality of first planetary gear carriers disposed at regular intervals on a rear edge of the first planetary gear carrier 10. First planetary gears 12 and a first sun gear 41 that is axially rotated by a driven output shaft 40 therein so that all of the first planetary gears 12 and the respective first planetary gears 12 are rotated externally; The circular ring gear 20 is installed so as to surround the outer circumferential surface of the first planetary gear 12 so as to contact the outer circumferential surface of each of the first planetary gears 12, and a driven member extending backward from the first sun gear 41. And a second sun gear 42 which is integrally arranged apart from the first sun gear 41 on the output shaft 40.

In addition, the connection part 26 is formed to have a hollow portion adjacent to the front surface of the second sun gear 42 in the ring gear 20, and a circular worm wheel 21 is formed on the outer circumferential surface of the connection part 26.

In addition, a pair of worm gears 22 may be interlocked with each other on the worm wheel 21, and a first bevel gear 23 may be installed at one end of each of the worm gears 22, and the second sun gear ( A pair of second planetary gears 31 are rotatably installed at predetermined intervals on the outer circumferential surface of 42, and shafts 31a of the second planetary gears 31 are respectively coupled to each other through the connecting portion 26. A second planetary gear carrier 30 is installed to surround the circumference, and each of the second planetary gears 31 has a second bevel gear that is in contact with the first bevel gear 23 at the end of the shaft 31a. 32) is installed.

At this time, the support 33 is installed at the end of the worm gear 22 to be connected to the second planetary gear carrier 30, between the inner peripheral surface of the connecting portion 26 and the outer peripheral surface of the driven output shaft 40, the connecting portion ( The driven output shaft 40, between the outer circumferential surface of 26 and the inner circumferential surface of the second planetary gear carrier 30, and the second planetary gear carrier 30 through which the shaft 31a of the second planetary gear 31 passes. One or more bearings 43 and 24 are respectively installed to reduce friction generated when the connecting portion 26, the second planetary gear carrier 30 and the shaft 31a of the second planetary gear 31 rotate. do.

Referring to the operation of the infinite speed shift device of the present invention configured as described above in detail.

In the first embodiment of the infinitely variable speed shift method according to the present invention, the number of teeth of the first sun gear 41 and the ring gear 20 has a ratio of 1: 3, and the second sun gear 42 and the second planetary gear ( 31 and the rotation ratio relationship between the worm gear 22 and the worm wheel 21 driven through the first and second bevel gears 23 and 32 are stopped by the second sun gear 42 and each of the second planetary gears ( The worm wheel 21 integrally formed on the outer circumferential surface of the connecting portion 26 extending from the ring gear 20 when the second planetary gear carrier 30 connecting the 31 is rotated once is the second planetary gear carrier 30. 1) Rotate in the direction of rotation.

The first sun gear 41 and the second sun gear 42 have an integral structure connected to the driven output shaft 40. When the first planetary gear carrier 10 rotates once, the first and second sun gears 41 ( The condition for stopping 42 is when the ring gear 20 is rotated by 1 ms.

That is, when the first planetary gear carrier 10, which is an input terminal, rotates once, the ring gear 20 is rotated by 1 ⅓ in a rotation ratio relationship between the second sun gear 42 and the worm wheel 21.

Such a condition is a stationary state in which power is not transmitted to the driven output shaft 40 even when the first planetary gear carrier 10, which is an input end, rotates and corresponds to 'neutral' in the gear shift state.

이하로 회전하는 조건이 될 때 입력단인 제1유성기어캐리어(10)가 1회전 하면 링기어(2)가

회전 이하의 위치에 있고, 상기 제1,2선기어(41)(42)는 유성기어장치 유닛의 결정조건에 따라 상기 링기어(20)의 위치가 변한 만큼의 비율로 상기 제1,2유성기어캐리어(10)(30)의 회전방향으로 회전하게 된다.The second embodiment of the infinitely variable method according to the present invention is that when the rotation ratio relation condition between the second sun gear 42 and the worm wheel 21 is smaller than 1 revolution, that is,

When the first planetary gear carrier 10, which is an input terminal, rotates once when the rotation condition is less than 1, the ring gear 2

The first and second sun gears 41 and 42 are positioned below rotation, and the first and second planetary gears are in proportion to the position of the ring gear 20 according to the determination condition of the planetary gear unit. It is rotated in the rotation direction of the carrier (10) (30).

회전보다 클 때, 즉

이상으로 회전하는 조건이 될 때 입력단인 제1유성기어캐리어(10)가 1회전 하면 링기어(2)가

회전 이상의 위치에 있고, 상기 제1,2선기어(41)(42)는 유성기어장치 유닛의 결정조건에 따라 상기 링기어(20)의 위치가 변한 만큼의 비율로 상기 제1,2유성기어캐리어(10)(30)의 회전반대방향으로 회전하게 된다.According to the third embodiment of the infinitely variable speed shift method according to the present invention, the rotation ratio relation condition between the second sun gear 42 and the worm wheel 21 is different.

When greater than rotation, i.e.

When the rotation condition is the above, when the first planetary gear carrier 10, which is an input end, rotates once, the ring gear 2

The first and second sun gears 41 and 42 are located in a rotational position or more, and the first and second planetary gear carriers are in proportion as much as the position of the ring gear 20 is changed according to the determination condition of the planetary gear device unit. It rotates in the opposite direction of rotation of (10) (30).

회전하여 피동출력축(40)이 정지상태이고, 상기 제2실시예는 링기어(20)가

이하로 회전하여 피동출력축(40)이 정방향으로 변속비율만큼 회전하는 상태, 즉 전진상태이고, 상기 제3실시예는 링기어(20)가

이상으로 회전하여 피동출력축(40)이 역방향으로 변속비율만큼 회전하는 상태, 즉 후진상태가 된다.Therefore, when the first planetary gear carrier 10 is rotated one direction in the forward direction, the ring gear 20 is the first embodiment.

Rotating driven output shaft 40 is stationary, the second embodiment is the ring gear 20

In the third embodiment, the driven output shaft 40 is rotated by the speed change ratio in the forward direction, that is, in the forward state. In the third embodiment, the ring gear 20

The above rotation results in a state in which the driven output shaft 40 rotates in the reverse direction by the speed change ratio, that is, in the reverse state.

When this relationship is shown on the graph, it becomes a straight line as shown in Table 1, and when the following condition table is satisfied, the speed ratio of the output stage to one rotation of the input stage can be obtained from the linear function of the formula 'y = -3x + 4'. .

And S = number of revolutions of the first sun gear, C = number of revolutions of the first planetary gear carrier, s = number of teeth of the first sun gear, r = number of teeth of the ring gear, A = r / s The relationship of output (speed) x = ((1 + A) CS) / A is established.

Condition Table

y = speed ratio (speed of first sun gear)

x = number of revolutions of the ring gear for one revolution of the input stage (speed)

s = number of sun gear teeth, r = number of ring gear teeth

S = rotational speed of sun gear, R = rotational speed of ring gear

For one revolution of the first planetary gear carrier as an input,

1.S = 0 (when sun gear stopped)

2. R = 0 (when ring gear stopped)

Relationship is established.

보다 작을때 출력이 발생하여 상기 제1선기어(41) 및 제2선기어(42)가 변속비율대로 회전하게 되고, 상기 제2선기어(42)의 회전만큼 상기 제2유성기어(31)의 회전이 감소하여 상기 웜휠(21)의 회전수(w)도 감소되어 속력이 증가하게 되면 즉 상기 제2선기어(42)의 회전수가 증가하면 웜휠(21)의 회전수(w)가 감소하고, 링기어(20)의 회전수가

로부터 감소하면 출력이 정회전(전진)으로 증가하고, 상기 링기어(20)의 회전수가

로부터 증가하면 출력이 역회전(후진)으로 증가하게 된다.Therefore, when the speed increases, the second planetary gear 42 rotates around the second sun gear 42 by one rotation with respect to one rotation of the first planetary gear carrier 10 as an input stage, and the rotation of the worm wheel 21 is performed. The number w is the rotation speed of the ring gear 20

When it is smaller than the output occurs, the first sun gear 41 and the second sun gear 42 are rotated according to the speed ratio, and the rotation of the second planetary gear 31 is rotated by the rotation of the second sun gear 42. When the rotation speed w of the worm wheel 21 decreases to increase the speed, that is, when the rotation speed of the second sun gear 42 increases, the rotation speed w of the worm wheel 21 decreases, and the ring gear 20 revolutions

When it decreases from, the output increases in forward rotation (forward), and the rotation speed of the ring gear 20

Increasing from increases the output in reverse (reverse).

In this way, when the speed changes, the speed ratio changes, and the speed ratio which becomes the optimum state in the relationship between the output of the engine and the speed is determined by itself.

Referring to the infinite shift method in which the speed becomes the speed ratio in the forward state of the second embodiment, the ring gear 20 of the infinite shift method disclosed in Patent No. 631090 rotates at a constant speed and the first planetary gear carrier 10 Conversely, in the infinite shift method in which the speed ratio increases when the rotation increases, the same result is reached when the rotation of the first planetary gear carrier 10 rotates at constant speed and the rotation of the ring gear 20 changes. Will change.

That is, the output is unilaterally controlled by the second sun gear 42, the second planetary gear 31, the second planetary gear carrier 30, the worm gear 22, and the worm wheel 21. When the first planetary gear carrier 10 is stopped due to the determination condition of the planetary gear unit, the rotational relationship between the first sun gear 41 and the ring gear 20 is reversely rotated and the first is rotated. With respect to one rotation of the sun gear 41 S, the rotation speed of the ring gear 20 R is rotated by s / r in the reverse direction.

In the first embodiment, the relationship between the second sun gear 42 S and the worm wheel 21 R also rotates by s / r in the reverse direction. The first embodiment is a condition for stopping.

회전하면 피동출력축(40)은 정지하고, 상기 링기어(20)의 회전수가

회전에서 1회전에 가까워지면 상기 피동출력축(40)의 회전도 정지에서 1회전에 가까워진다.In the rotational relationship between the first planetary gear carrier 10 and the ring gear 20, the first planetary gear carrier 10 rotates once and the ring gear 20 is rotated.

When rotated, the driven output shaft 40 stops, and the rotation speed of the ring gear 20

When the rotation is close to one rotation, the rotation of the driven output shaft 40 also approaches one rotation at the stop.

When the rotational speed of the ring gear 20 is gradually lowered to stop, the rotational speed of the output shaft 40 is four revolutions, and when the rotation of the ring gear 20 is increased in the reverse direction, the speed ratio is continuously increased to be infinite. Shift is made.

) 상기 링기어(20)는

위치에 있게 되고 상기 제1,2선기어(41)(42)는 변속비 함수 'y = -3x + 4'에서 0.1 회전 위치에 있게 되며, 상기 제2선기어(42)의 0.1 회전에 대하여 상기 링기어(20)는 상기 제1선기어(41)와의 회전비(상기 제1유성기어캐리어(10)가 정지하고 상기 제1선기어(41)가 정방향으로 1회전 할 때 상기 링기어(20)는 역방향으로

회전하게 되는데 제2선기어(42)가 0.1 회전한 때의 상기 제1유성기어캐리어(10)의 정지조건은 상기 링기어(20)가

회전위치에 있을 때이고,

회전위치에 있을 때 상기 제1유성기어캐리어(10)가 정방향으로 1/30 회전하는 즉 0.1 회전하는) 관계에 따라 입력단인 제1유성기어캐리어(10)는 1.1 회전하게 되고 피동출력축(40)은 0.11 회전하게 되고, 이 관계는 증가분이 0에 수렴하므로 회전의 증가는 1+0.1+0.01+0.001.......+0과 0.1+0.01+0.001.......+0의 관계가 되어 입력단과 피동출력축(40)의 회전비 관계는 1 : 1/10의 관계가 성립되고 중력가속도에 의해 상기 피동출력축(40)의 회전수가 변하게 되면 변속비가 변하게 되어 속력이 변속비가 되는 무한변속방법이 작용하는 것이다.In the second embodiment, when the first planetary gear carrier 10, which is an input end, rotates once, power is simultaneously transmitted to the ring gear 20 and the first sun gear 41, and the ring gear ( 20 starts to rotate, and the second planetary gear 31 rotates on the second sun gear 42. At this time, the rotation ratio between the first sun gear 41 and the ring gear 20 and the second sun gear 42 are rotated. And rotation ratio of worm wheel 21 does not match (

) The ring gear 20 is

Position and the first and second sun gears 41 and 42 are in a 0.1 rotational position in the speed ratio function 'y = -3x + 4' and the ring gear for 0.1 rotation of the second sun gear 42. 20 is the rotation ratio with the first sun gear 41 (when the first planetary gear carrier 10 stops and the first sun gear 41 rotates one direction in the forward direction, the ring gear 20 moves in the reverse direction.

When the second sun gear 42 rotates by 0.1, the stop condition of the first planetary gear carrier 10 is that the ring gear 20

When in the rotational position,

When the first planetary gear carrier 10 is in a rotational position, the first planetary gear carrier 10, which is an input stage, rotates 1.1 and the driven output shaft 40 is driven according to the relationship of the first planetary gear carrier 10. Becomes 0.11 rotations, and this relationship increases by 1 + 0.1 + 0.01 + 0.001 ....... + 0 and 0.1 + 0.01 + 0.001 ....... + 0 The relationship between the rotational ratio between the input end and the driven output shaft 40 is 1: 1/10, and when the rotational speed of the driven output shaft 40 is changed by gravity acceleration, the speed ratio is changed and the speed becomes the speed ratio. The shift method works.

In the infinite shift method as described above, when the vehicle is rotated in a relationship of a differential device having an output of 2 which is inversely related to the input of 1, the rotational relationship between the inner wheel and the outer wheel satisfies both conditions. In a state in which the rotation speeds of the inner wheel and the outer wheel are determined by themselves, the inverse relationship between the first sun gear 41 and the ring gear 20 with respect to the input of the first planetary gear carrier 10 is determined. With the output of 2, the speed is fed back and the ring gear 20 is unilaterally placed in the condition so that the speed ratio is determined and changed under the condition that the speed change becomes the speed ratio change.

Referring to the application of the infinitely variable speed gear of the present invention to a power device such as an automobile as follows.

As shown in FIGS. 7 to 9, first, the output shaft 44 is extended from the second sun gear 42 to the rear, and around the output shaft 44 on the rear surface of the second sun gear 42. The power transmission unit 53 is installed to be in close contact and transmits the rotational force of the output shaft 44 to the second sun gear 42. The power transmission unit 53 is formed by the elastic body 54 installed at the rear. It is to be in close or in close contact with the two-wire gear 42 to rotate with the output shaft 44 in close contact with the second sun gear 42.

In addition, first and second ring gears 51 and 52 which are inscribed by the rotary gears 56a and 56b extending from the second planetary gear 31 around the power transmission unit 53 are provided. A brake unit 55 for stopping and reversing the vehicle by selectively stopping rotation of the first and second ring gears 51 and 52 on an outer circumferential surface of the first and second ring gears 51 and 52. Is installed.

회전하는 경우 상기 제1선기어(41)가 정지하여 차량이 정지 즉 '중립'의 상태가 되는 것이며, 상기 제2선기어(42)가 출력단으로 작용하게 되면 상기 링기어(20)가

이하로 회전하는 경우 상기 제1선기어(41)가 상기 제1,2유성기어캐리어(10)(30)의 회전방향으로 회전하여 상기 제2선기어(42)가 상기 동력전달부(53)에 밀착된 상태로 출력축(44)과 함께 회전하여 차량이 전진하게 되고, 상기 웜휠(21)의 회전수가 자동차의 제2링기어(52)를 따르면, 상기 링기어(20)가

이상으로 회전하는 경우 상기 제1선기어(41)가 상기 제1,2유성기어캐리어(10)(30)의 회전반대방향으로 회전하여 차량이 후진하게 된다.In other words, when the rotation speed of the worm wheel 21 follows the first ring gear 51 of the vehicle, the ring gear 20 is rotated when the first planetary gear carrier 10 rotates once.

In the case of rotation, the first sun gear 41 stops and the vehicle is stopped or 'neutral'. When the second sun gear 42 acts as an output stage, the ring gear 20

When rotating below, the first sun gear 41 rotates in the rotational direction of the first and second planetary gear carriers 10 and 30 so that the second sun gear 42 comes into close contact with the power transmission unit 53. Is rotated together with the output shaft 44 to move the vehicle forward, and the number of revolutions of the worm wheel 21 follows the second ring gear 52 of the vehicle.

In the case of the above rotation, the first sun gear 41 rotates in the opposite direction of rotation of the first and second planetary gear carriers 10 and 30 so that the vehicle reverses.

That is, the worm gear 22 and the first contacting the worm wheel 21 in the state in which the stop and the reverse of the vehicle are spaced apart from the power transmission unit 53 so as to block power transmission. The second bevel gear 32, driven by the rotation of the bevel gear 23, rotates in the opposite direction and extends on the second planetary gear 31 and the extended shaft of the second planetary gear 31 provided on the axis. The rotating gear 56a installed together is rotated together to rotate the second ring gear 52 of the power unit in the opposite direction. This includes the stop state of the first ring gear 51.

On the other hand, Figure 10 shows another embodiment of the endless speed change apparatus according to the present invention, which is manufactured in a small size for a narrow installation space, such as a bicycle, in this case the worm wheel (21 ') constitutes a connection Without having a structure formed directly on the outer circumferential surface of the ring gear 20 '.

In this case, although there is an advantage of being less restricted by the installation space, the size of the second sun gear 42 is relatively increased as the worm wheel 21 'is installed on the outer circumferential surface of the ring gear 20'. As a result, an increase in the transmission ratio and stability at the time of shifting may be lowered. Thus, in the case of a general vehicle installation, a worm wheel 21 is formed at the connection portion 26 by providing the connection portion 26 at the rear side of the ring gear 20. It is preferable to follow the structure.

Although the present invention has been described with reference to specific embodiments, it is not necessarily limited thereto, and modifications and variations may be made without departing from the scope of the technical idea of the present invention.

For example, the same result occurs even if the input and output directions of the first planetary gear carrier 10 and the driven output shaft 40 which are input terminals are changed. In other words, even if the input is infinite, the output is at 0, and the output is the same as the input converges to 0 when the output is infinitely large due to the acceleration of gravity.

1 is a cross-sectional view showing a gear coupling state of a conventional transmission.

Figure 2 is a cross-sectional view showing an endless speed change apparatus according to the present invention.

3 is an exploded perspective view showing the first and second sun gears, the first planetary gear carrier and the ring gear of FIG.

4 is a plan view of the worm wheel and the worm gear of FIG.

5 is a side view of FIG. 4.

6 is a cross-sectional view showing the input and output direction of the infinite shift method according to the present invention.

7 is a state diagram used in the infinite speed change apparatus according to the present invention.

8 is a plan view of the worm wheel and the worm gear of FIG.

9 is a side view of FIG. 8;

Figure 10 is a perspective view showing another embodiment of the endless speed change apparatus according to the present invention.

Explanation of symbols on the main parts of the drawings

10; First planetary gear carrier 12; 1st planetary gear

20; Ring gear 21; Worm wheel

22; Worm gear 23; 1st Bevel Gear

24, 43; Bearing 30; 2nd planetary gear carrier

31; Second planetary gear 32; 2nd bevel gear

40; Driven output shaft 41; 1st Sun Gear

42; 2nd Sun Gear

Claims (6)

A first sun gear rotated axially; A plurality of first planetary gears which are externally rotated with the first sun gear; A ring gear having a first planetary gear carrier and an inner circumferential surface thereof connecting the first planetary gears to an outer circumferential surface of the first planetary gears; In consisting of, A second sun gear installed on an axis of the first sun gear and spaced apart from the first sun gear; A worm wheel provided between the first planetary gear carrier and the second sun gear; A pair of worm gears installed on the worm wheel so as to face each other and having at least one first bevel gear; A pair of second planetary gears which are externally rotated with the second sun gear; A second planetary gear carrier which penetrates the axes of the second planetary gears and connects the second planetary gears; A second bevel gear that is in contact with the first bevel gear at the shaft end of the second planetary gear; Infinite speed transmission, characterized in that configured to include. The method of claim 1, The worm wheel is infinitely variable, characterized in that formed on the outer peripheral surface of the ring gear. The method of claim 1, And the worm wheel is formed on the outer circumferential surface of the linking unit configured to be adjacent to the front surface of the second sun gear in the ring gear. The method of claim 3, At least one bearing is provided between the inner circumferential surface of the connecting portion and the outer circumferential surface of the driven output shaft and between the outer circumferential surface of the connecting portion and the inner circumferential surface of the second planetary gear carrier. By using the endless gear made of the structure of claim 1, When the first planetary gear carrier is the input terminal and the first sun gear and the second sun gear are the output terminals, when the second planetary gear circumscribed to the second sun gear rotates around the second sun gear once, the number of revolutions of the worm wheel is w. The second planetary gear rotates about the second sun gear to drive a first bevel gear of a worm gear in contact with a second bevel gear interlocking with the second sun gear and a worm wheel interlocking with the ring gear, And the first sun gear and the second sun gear, which are output stages, rotate forward, stop, and reverse according to the value of w. The method of claim 5, S = number of revolutions of the first sun gear, C = number of revolutions of the first planetary gear carrier, s = number of teeth of the first sun gear, r = number of teeth of the ring gear, A =

, when, Ring gear speed x =

Have a relationship Transmission ratio (speed of the first sun gear) y = -3x + 4, In the relation between the rotation speed x of the ring gear and the rotation speed w of the worm wheel, y stops when x = w, y rotates forward when x> w, and y rotates reverse when x <w. Infinite speed shift method.

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