KR101496943B1 - Transmission apparatus - Google Patents

Abstract

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a speed shift device, and more particularly, to a speed shift device that is automatically shifted without a clutch. According to an aspect of the present invention, there is provided a transmission including: an input shaft to which rotation is input from the outside; A torque converter installed on the input shaft; A power gear rotated by the torque converter; An output gear engaged with the power gear and rotating at least one of revolution and rotation by the power gear; A transmission that is coupled to the output gear and generates idle rotation or rotation load; And a carrier rotating according to revolution of the output gear.

Description

[0001] TRANSMISSION APPARATUS [0002]

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001] The present invention relates to a speed shift device, and more particularly, to a speed shift device that is automatically shifted without a clutch.

The transmission is a device that shifts the rotation generated by a power source such as an engine and transfers the rotation to a driven body such as a wheel of an automobile. Generally, the speed change gears are all shifted in accordance with a predetermined gear ratio, and cumbersome clutch operation is required for shifting and releasing the gears during shifting.

In order to compensate for this, researches on an automatic transmission that performs automatic shifting are actively under way. However, the belt-type automatic transmission developed until now has a very complicated structure, which is costly to manufacture and is widely used due to belt wear, noise and slip phenomenon.

An object of the present invention is to provide a shift device that is automatically shifted without departing and replacing a gear.

The problems to be solved by the present invention are not limited to the above-mentioned problems, and the problems not mentioned can be clearly understood by those skilled in the art from the description and the accompanying drawings will be.

The present invention provides a transmission.

The transmission according to the present invention includes: an input shaft to which a rotation is inputted from the outside; A torque converter installed on the input shaft; A power gear rotated by the torque converter; An output gear rotating at least one of revolution and rotation by the power gear; A transmission that is coupled to the output gear and generates idle rotation or rotation load; And a carrier rotating according to revolution of the output gear.

The rotation of the output gear rotates only when the transmission gear idles, and revolves when a rotation load is generated.

The transmission is rotated by the power gear, and idles until the adjusted rotation speed. When the adjusted rotation speed reaches the adjusted rotation speed, the transmission is fixed at the adjusted rotation speed and rotates to generate the rotating load. The unidirectional bearing is configured such that one side of the unidirectional bearing rotates at an adjusted rotational speed by an input shaft and the other side rotates integrally with the transmission gear , It rotates idly until the adjusted rotation speed, and rotates at fixed rotation speed when it reaches the adjusted rotation speed.

Wherein the input shaft further includes an adjustment gear having an input shaft gear rotated at an input rotation speed and engaged with the input shaft gear, and one side of the bearing is rotatable by the adjustment gear at the adjustment speed .

The input shaft is provided with a protruding portion that rotates at an input rotational speed, and one side of the bearing can be rotated at the same rotational speed as the input rotational speed by the protruding portion.

The transmission gears are divided into first, second and third transmission gears, and the speeds of adjustment of the respective speed-change gears are different from each other, and the speed of rotation of the transmission gears sequentially reaches an adjustment speed as the number of rotations of the power gear increases .

When either of the transmission gears does not reach the adjustment rotation speed, the carrier does not rotate, and when either one of the transmission gears reaches the adjustment rotation speed, a rotation load is generated and the output gear rotates, .

The present invention is automatically shifted in accordance with the number of revolutions converted by the torque converter, and the shifting process is automatically shifted as the transmission gear selectively rotates idly or rotates at a fixed speed according to the load of the output shaft, It is effective.

1 is a block diagram of a transmission.
2 is a sectional view of the transmission shown in Fig.
Figure 3 is a perspective view of the input of Figure 1;
4 is a cross-sectional view of the torque converter of Fig.
Fig. 5 is a view showing a fastened state of the transmission gear of Fig. 2;
6 is a cross-sectional view of the control unit of Fig.
Fig. 7 is a view showing an example of the fastening state of the adjustment gear of Fig. 6;
8 is a view showing another example of the fastening state of the adjustment gear of Fig.
Figure 9 is a cross-sectional view of the unidirectional bearing of Figure 6;
10 is a cross-sectional view of one directional bearing of FIG. 6;
11 is a cross-sectional view of another operation of the uni-directional bearing of Fig.
Figure 12 is a perspective view of the unidirectional bearing of Figure 6;
Figure 13 is a cross-sectional view of the output of Figure 1;
FIG. 14 is a view of the engagement state of the output gear of FIG. 13; FIG.
15 is a diagram relating to an example of the output unit of Fig.
Fig. 16 is a view showing a fastened state of the first output gear of Fig. 15;
Fig. 17 is a view of the engagement state of the second output gear of Fig. 15; Fig.
Fig. 18 is a table concerning the number of gears of the transmission having the output portion of Fig. 15. Fig.
19 is a table relating to a shifting step according to an embodiment of the shifting state.
Fig. 20 is a graph relating to the number of revolutions of the transmission according to the shifting step of Fig. 19;
FIG. 21 is a graph relating to the number of rotations of the carrier in accordance with the shifting step of FIG. 19;
FIG. 22 is a diagram relating to the neutral state of FIG. 19; FIG.
23A is a rotation direction table of the operating gear in the low speed state of FIG.
Fig. 23B is a diagram relating to the low speed state of Fig. 19;
Fig. 24A is a rotation direction table of the operating gear in the middle speed state of Fig. 19;
FIG. 24B is a diagram relating to the intermediate speed state of FIG. 19;
Fig. 25A is a rotation direction table of the operating gear in the high-speed state of Fig.
FIG. 25B is a diagram relating to the high-speed state of FIG. 19;

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory and are intended to be illustrative of the present invention and not to limit the scope of the invention. Should be interpreted to include modifications or variations that do not depart from the spirit of the invention.

In addition, the terms used in the present specification and the accompanying drawings are for explaining the present invention easily, and thus the present invention is not limited by the terms used in the present specification and the accompanying drawings.

In the following description of the present invention, a detailed description of known configurations or functions will be omitted when it is determined that the gist of the present invention may be obscured.

The transmission 1000 according to the present invention shifts and outputs the rotation when it is input. Specifically, the transmission 1000 converts the input torque, that is, torque, by applying a torque converter 1210 and automatically shifts the planetary gear unit through the planetary gear unit without operating a clutch And outputs it to a carrier 1440 (carrier).

Hereinafter, the configuration of the transmission 1000 according to the present invention will be described.

Fig. 1 is a block diagram of the transmission 1000. Fig. The transmission 1000 includes an input portion 1100, a torque converter portion 1200, a control portion 1300, and an output portion 1400. [ The rotation is input to the input unit 1100, and the torque converter unit 1200 converts the torque of the rotation input to the input unit 1100 and transfers the torque to the output unit 1400. The output unit 1400 shifts and outputs the rotational force transmitted from the torque converter unit 1200, and the control unit 1300 controls the shift of the output unit 1400.

Hereinafter, each component of the transmission 1000 will be described with reference to FIG.

2 is a sectional view of the transmission 1000 of FIG.

The input unit 1100 receives the rotation from the external power source, and transmits the rotation to the torque converter unit 1200 and the control unit 1300.

3 is a perspective view of the input unit 1100 of FIG.

The input unit 1100 includes an input shaft 1110, a spline 1120, an input shaft gear 1130, and a protrusion 1140. The input shaft 1110 is provided in the form of a bar having a circular section.

The input shaft 1110 is connected to an external power source and receives a rotational force to rotate. Here, the number of revolutions of the input unit 1100 is defined as the number of input revolutions.

The spline 1120 is formed on the input shaft 1110. The spline 1120 is engaged with a spline 1221 formed in the impeller 1220 of the torque converter 1210 to transmit torque to the torque converter unit 1200.

The input shaft gear 1130 is integrally formed with the input shaft 1110 and is coupled to the adjustment driving gears 1311a and 1311b of the adjusting gear 1310 to transmit the rotational force to the controller 1300. [

The protrusion 1140 is formed in the shape of a circular ring on the input shaft 1110. The protrusion 1140 is engaged with the inner side 1331c of the third unidirectional bearing 1330 to rotate the inner side.

A spline 1120, an input shaft gear 1130 and a protrusion 1140 are sequentially provided on the input shaft 1110 along the longitudinal direction of the input shaft 1110.

The torque converter unit 1200 converts the torque of the rotation transmitted from the input unit 1100 and transmits the torque to the output unit 1400. The torque converter section 1200 includes a torque converter 1210, a turbine shaft 1240, a transmission gear 1250, and a power shaft 1260.

4 is a cross-sectional view of the torque converter 1210 of FIG.

Torque converter 1210 includes an impeller 1220 and a turbine 1230 to convert torque.

The impeller 1220 is provided such that the input shaft 1110 passes through the center thereof. A spline 1221 is formed at the center of the impeller 1220 and is coupled to the spline 1120 of the input shaft 1110. Accordingly, the impeller 1220 rotates integrally with the input shaft 1110.

The turbine 1230 is provided to face the impeller 1220. A fluid is provided between the impeller 1220 and the turbine 1230. When the impeller 1220 rotates, kinetic energy is transferred to the fluid, and the kinetic energy of the fluid again rotates the turbine 1230. The torque is converted as the impeller 1220 rotates the turbine 1230 through the fluid. Here, the number of revolutions of the turbine 1230 is defined as the number of revolutions of the turbine.

The torque converter 1210 may be provided with a stator (not shown) disposed between the impeller 1220 and the turbine 1230. The stator (not shown) can increase the efficiency with which the torque is converted. The torque converted at the torque converter 1210 is transmitted to the output portion 1400 through the turbine shaft 1240, the transmission gear 1250, and the power shaft 1260.

One end of the turbine shaft 1240 is coupled to the turbine 1230 and a turbine shaft gear 1241 is formed at the other end. The turbine shaft gear 1241 is coupled to the transmission gear 1250 to rotate the transmission gear 1250.

A power shaft gear 1261 is formed at one end of the power shaft 1260 and a power gear 1410 of the output unit 1400 is formed at the other end to transmit the rotational force to the output unit 1400. The power shaft gear 1261 is coupled to the transmission gear 1250 and rotated by the transmission gear 1250.

Fig. 5 is a view of the fastening state of the transmission gear 1250 of Fig.

The transmission gear 1250 is coupled to the turbine shaft gear 1241 and the power shaft gear 1261 to transmit the rotational force from the turbine shaft 1240 to the power shaft 1260. The transmission gear 1250 includes a transmission drive gear 1251 and a transmission driven gear 1252. The transmission drive gear 1251 and the transmission driven gear 1252 are formed in one body and rotate integrally. The transmission drive gear 1251 is coupled to the turbine shaft gear 1241 and the transmission driven gear 1252 is coupled to the power shaft gear 1261. The transmission gear 1250 is formed with a fixing pin 1253 at the center thereof and fixed by a fixing plate (not shown). The transmission gear 1250 may be provided to be symmetrical with respect to the input shaft 1110 in order to balance the torque.

Meanwhile, the transmission gear 1250 may be provided as one gear instead of two gears, that is, the drive gear 1251 and the driven gear 1252. In this case, the turbine shaft gear 1241 and the power shaft gear 1261 can be fastened to one gear at different positions. With this structure, when the turbine shaft 1240 rotates, the power shaft 1260 rotates through the turbine shaft gear 1241, the drive transmission gear 1251, the driven transmission gear 1252, and the power shaft gear 1261 do. The number of revolutions of the power shaft 1260 with respect to the number of revolutions of the turbine shaft 1240 is determined by the gear ratio between the engaged gears. In this case, the turbine shaft 1240 and the power shaft 1260 rotate in the same direction and at the number of revolutions. That is, the power shaft 1260 rotates by the number of revolutions of the turbine.

However, the number and types of gears of the gears 1241, 1251, 1252, and 1261 are not limited to those described above, and may be appropriately selected depending on the number of rotations of the power shaft 1260 with respect to the number of rotations of the turbine shaft 1240 Can be selected.

The control unit 1300 controls the shift of the output unit 1400.

6 is a cross-sectional view of the control unit 1300 of FIG.

The control unit 1300 includes the control gears 1310a and b and the control shafts 1320a and b and the unidirectional bearings 1330a and 1340b .

The adjustment gears 1310a and b are coupled to the adjustment shaft gears 1321a and b formed on the input shaft gear 1130 and the adjustment shafts 1320a and 1320b and transmit rotational force from the input shaft 1110 to the adjustment shaft 1320 . The rotational direction and the rotational speed of the adjusting shaft 1320 with respect to the rotation of the input shaft 1110 are determined by the number of teeth of the adjusting gear 1310. For example, the adjusting gear 1310 may be provided as a differential gear. Here, the adjusting gear 1310 may be provided in a plurality of positions symmetrical with respect to the input shaft 1110 in order to balance the torque.

Fig. 7 is a view of the fastening state of the adjusting gear 1310a of Fig.

The adjusting gear 1310a includes a driving gear 1311a and a driven gear 1312a. The adjustment drive gear 1311a and the adjustment driven gear 1312a are formed in one body and are integrally rotated. The adjustment drive gear 1311a is coupled to the input shaft gear 1130 and the adjustment driven gear 1312a is coupled to the adjustment shaft gear 1321a. Here, the adjustment shaft gear 1321a is provided as a ring gear. The adjustment gear 1310a has a center pin 1313 formed at its center and fixed by a fixing plate (not shown).

With this structure, when the input shaft 1110 rotates, the adjusting shaft 1320a rotates via the input shaft gear 1130, the driving gear 1311a, the driven gear 1312a, and the adjusting shaft gear 1321a.

The number of revolutions of the adjusting shaft 1320a with respect to the number of revolutions of the input shaft 1110 is determined by the gear ratio between the engaged gears. For example, when the gear ratio of the input shaft gear 1130 and the drive gear 1311a is 15:20 and the gear ratio of the driven gear 1312a and the adjustment shaft gear 1321a is 15:50, When rotating, the adjustment shaft 1320a is rotated 0.225 times. The rotation direction of the adjustment shaft 1320 with respect to the rotation of the input shaft 1110 is as follows. The direction of rotation of the input shaft 1110 is denoted by "+" and the direction opposite to the direction of rotation of the input shaft 1110 is denoted by "-". Also, if there is no notation of '+' or '-', it means rotation speed without rotation direction. The input shaft 1110 rotates by +, the drive gear 1311a by -, the driven gear 1312a by -, and the adjustment shaft gear 1321a by -. Thus, the adjustment shaft 1320a rotates in the direction opposite to -, that is, the input shaft 1110.

8 is a view showing the fastening state of the adjusting gear 1310b of Fig.

The adjusting gear 1310b includes an adjusting driving gear 1311b and a driven gear 1312b which are engaged with each other. The adjustment drive gear 1311b is fastened to the adjustment drive gear 1311a and the adjustment drive gear 1311b is fastened to one side of the driven gear 1312b and fastened to the adjustment shaft gear 1321b at the other side. Here, the adjustment shaft gear 1321b is provided as a sun gear. A fixing pin 1313 is formed at the center of the driving gear 1311b and the driven gear 1312b to be fixed by a fixing plate (same as described above).

delete

With this structure, when the input shaft 1110 rotates, the adjusting shaft 1320b rotates via the input shaft gear 1130, the driving gear 1311b, the driven gear 1312b, and the adjusting shaft gear 1321b.

The number of revolutions of the adjusting shaft 1320b with respect to the number of revolutions of the input shaft 1110 is determined by the gear ratio between the engaged gears. For example, when the number of gears of the input shaft gear 1130, the driving gear 1311b, the driven gear 1312b, and the adjusting shaft gear 1321b are all the same, the adjusting shaft 1320b is shifted from the rotational speed of the input shaft 1110 And rotates at the same number of revolutions.

The rotation direction of the adjustment shaft 1320 with respect to the rotation of the input shaft 1110 is as follows. The input shaft gear 1110 rotates by +, the drive gear 1311b by -, the driven gear 1312b by +, and the adjustment shaft gear 1321b by -. Thus, the adjustment shaft 1320b rotates in the-direction.

However, the number and types of gears of the input shaft gear 1130, the adjusting gear 1310 and the adjusting shaft gear 1320b are not limited to the above example, and the rotational speed of the adjusting shaft 1320 with respect to the desired input shaft 1110 It can be suitably deformed in consideration of the direction of rotation.

The adjustment gears 1310b may be provided in one or more than one.

9 is a cross-sectional view of the unidirectional bearing 1330 of FIG.

The bearing 1330 is made up of three (3) unidirectional bearings 1330a, b and c which are known in the art and one unidirectional bearing is operated for each of the speed change (low speed, medium speed and high speed) And another unidirectional bearing is operated at the same time. The structure of the unidirectional bearing 1330 is divided into inner bearings 1331a, b and c and outer bearings 1332a, b and c. b and c are coupled to the adjustment shaft gears 1321a and b and adjustment shafts 1320a and b that rotate by the adjustment gears 1310a and b and to the protruding portion 1140 of the input shaft 1110. [

The control shaft 1340a is coupled to the outer bearing 1332a and the control shaft 1340a is coupled to the inner bearing 1331a by the adjustment shaft 1320a integrated with the adjustment shaft gear 1321a, A control shaft 1340b is coupled to the outer bearing 1332b and a protrusion 1140 integral with the input shaft 1110 is coupled to the other inner bearing 1331c, A control shaft 1340c is coupled to the outer bearing 1332c, which is integrated with the inner and outer bearings at the time of engagement.

The number of rotations of the inner bearings 1331a, b and c is determined by the number of teeth of the adjusting gears 1310a and 1330b and the rotation of each of the adjusting shaft gears 1321a and b is controlled by the respective inner bearings 1331a, The projecting portion 1140 rotates in the same manner because it is integrated with the input shaft 1110. This rotation speed is defined as a basic adjusted rotation speed set in the inner bearings 1331a, b and c. The rotation of the outer bearings 1332a, b and c is the same as the rotation of the transmission gears 1420a, b and c. 18), the inner bearing 1331a rotates by -0.225 and the first adjustment rotation speed, the inner bearing 1331b rotates by -1, and the second adjustment rotation speed, The inner bearing 1331c rotates by +1 and is referred to as the third adjusted rotation speed.

The unidirectional bearings operate in unison by the associated control shafts 1340a, b, c and the adjustment shafts 1320a, b, with the inner bearings 1331a, b, c and the outer bearings 1332a, The first unidirectional bearing 1330a, the inner bearing 1331b and the outer bearing 1332b operate in the intermediate speed region and the second unidirectional bearing 1330b and the second unidirectional bearing 1330b operate in the low speed region, The inner bearing 1331c and the outer bearing 1332c operate in the high speed section and are called the third unidirectional bearing 1330c.

10 is a cross-sectional view of one operation of unidirectional bearing 1330 of FIG.

For example, the number of revolutions of the transmission gear 1420 may be equal to or less than the regulated revolution number. Here, the meaning of " less than the adjustment rotation speed " means that the rotation is slower or the opposite direction in the same direction as the rotation direction of the inner bearing 1331. [ In this case, the outer bearing 1332 rotates in the free direction relative to the inner bearing 1331, so that no rotational load is applied to the transmission 1420, and the idler can freely idle.

11 is a cross-sectional view of another operation of unidirectional bearing 1330 of Fig.

As another example, the transmission gear 1420 may be rotated at an adjusted rotation speed. In this case, since the outer bearing 1332 rotates integrally with the inner bearing 1331, a rotational load is applied to the transmission gear 1420.

As another example, the transmission gear 1420 may attempt to rotate at an adjustment rotation speed or more. In this case, since the outer bearing 1332 tries to rotate in the load direction relative to the inner bearing 1331, a rotational load is applied to the transmission 1420, so that the number of revolutions of the transmission 1420 is adjusted . In this state, the transmission gear 1420 transmits the rotational load to the output gear 1430 inversely.

12 is a perspective view of the unidirectional bearing 1330 of FIG.

The unidirectional bearing 1330 is constituted by three unidirectional bearings 1330 of a first unidirectional bearing 1330a, a second unidirectional bearing 1330b and a third unidirectional bearing 1330c.

13 is a cross-sectional view of the output section 1400 of FIG.

The output section 1400 includes a power gear 1410, transmission gears 1420a, b and c, output gears 1430a and b and a carrier 1440 and an output shaft 1442. [

The power gear 1410 is coupled to the other end of the power shaft 1260 and rotates integrally with the power shaft 1260 and is identical to the number of revolutions of the turbine 1230.

The transmission gears 1420a, b and c are integrally coupled to the other ends of the control shafts 1340a, b and c and freely idle or receive rotary loads by bearings 1330a, b and c, Rotate.

Output gears 1430a, b are provided as compound planetary gears. Accordingly, the output gear 1430 rotates, revolves, or simultaneously rotates in accordance with the load state of the driven body.

A carrier shaft 1441 is inserted in the center of the output gear 1430 and the carrier shaft 1441 is fixed to the two carrier plates 1440 and the output shaft 1442 is integrally coupled to one carrier plate 1440 .

The output gear 1430 receives rotational force from the power gear 1410,

The rotating load can be received from the rotating shaft 1420.

The output gear 1430 may be provided as one or a plurality. And when the output gear 1430 is one, it is engaged with the power gear 1410 and the transmission gear 1420 and receives rotational force or rotational load directly from them. When there are a plurality of output gears 1430, it is possible to receive rotational force or rotational load directly or indirectly from the power gear 1410 and the transmission gear 1420.

According to this structure, the output gear 1430 rotates idly, rotates, or in parallel.

Fig. 14 is a view showing the engagement state of the output gears 1430a, b in Fig.

For example, when the speed changer 1420a, b, c rotates below the regulation speed, it freely idles and does not generate a rotating load. On the other hand, since the output shaft 1442 of the driven chain is connected to the carrier 1440, a rotational load due to the driven body is applied. Therefore, when the rotational force is transmitted from the power gear 1410 to the output gear 1430, the rotation of the output gears 1430a, b is not applied to the rotation of the output gears 1430a, Is rotated only.

When the number of rotations of the transmission gears 1420a, b and c reaches the adjusted rotation speed, the rotation speed is fixed at the adjusted rotation speed, and if the rotation speed exceeds the predetermined number, the rotation load is generated. It rotates while maintaining its rotation because it is relatively larger than the rotational load of the driven body and outputs rotational force to the output shaft 1442 through the carrier 1440. [

15 is a view of an example of the output section 1400 of Fig. 13, Fig. 16 is a view of the fastening state of the first output gear 1430a of Fig. 15, and Fig. 17 is a cross- (1430b).

The first transmission gear 1420a, the second transmission gear 1420b, the third transmission gear 1420c, the first output gear 1430a, and the first output gear 1430b are connected to the output section 1400. [ 2 output gear 1430b. The power gear 1410 and the first transmission 1420a are provided as ring gears and the second transmission gear 1420b and the third transmission gear 1420c are provided as sun gears.

The first output gear 1430a and the second output gear 1430b are provided with a compound planetary gear and are engaged with each other.

A first carrier shaft 1441a is inserted into the center of the first output gear 1430a and a second carrier shaft 1441b is inserted into the center of the second output gear 1430b. And second carrier shaft 1441b are coupled to two carrier plates 1440, respectively.

Accordingly, the first output gear 1430a and the second output gear 1430b rotate at the same rotational speed. The first output gear 1430a is provided with a first output front gear 1431a and a first output rear gear 1432a.

Here, the positions of the gears are not limited by the terms of the lines and the following. The first output front gear 1431a is coupled to the power gear 1410 and the first output rear gear 1432a is coupled to the second transmission gear 1420b. The second output gear 1430b is provided with a second output front gear 1431b and a second output rear gear 1432b. The second output front gear 1431b is engaged with the first transmission gear 1420a and the second output rear gear 1432b is engaged with the third transmission gear 1420c.

The first output rear end gear 1432a and the second output front end gear 1431b are engaged with each other.

According to this structure, the rotational force of the power gear 1410 is directly transmitted to the first output gear 1430a, and the second output gear 1430b is transmitted through the first output gear 1430a. It is directly or indirectly transmitted to the output gears 1430a and 1430b, which are generated by the respective transmission gears 1420a, 1420b and 1420c.

Accordingly, the first output gear 1430a and the second output gear 1430b are rotated by the power gear 1410 and the transmission gears 1420a, 1420b, and 1420c by idling, rotating, or a combination thereof.

Here, the first transmission gear 1420a is coupled to the other end of the first control shaft 1340a and connected to the first unidirectional bearing 1330a having the above-described first adjustment rotational speed of -0.225. The second transmission gear 1420b is coupled to the other end of the rearmost control shaft 1340b and is connected to the second unidirectional bearing 1330b having the second adjusted rotational speed of -1. The third transmission gear 1420c is coupled to the other end of the third control shaft 1340c and connected to the third unidirectional bearing 1330c having the above-described third adjusted rotation speed of +1.

Accordingly, when the power gear 1410 rotates at a low speed, both of the transmission gears 1420a, 1420b, 1420c and the output gears 1430a, b freely idle freely, and thus the carrier 1440 is in a neutral state do.

When the number of revolutions of the power gear 1410 increases in the neutral state, the first transmission 1420a first reaches the first adjustment speed and is fixed at the first adjustment speed and rotates to generate the rotation load.

Accordingly, the output gears 1430a and 1430b rotate at the first speed change ratio and output the rotational force to the outside through the carrier 1440. Here, the revolution number of revolution relative to the turbine revolution number is defined as a transmission ratio. Also, the transmission ratio when the first transmission 1420a is fixed at the first adjustment speed and rotates is defined as the first speed ratio.

When the turbine speed is further increased, the second transmission gear 1420b reaches the second adjusted speed and is then fixed at the second adjusted speed and rotates to generate the rotating load. Further, as the number of rotations of the second transmission mechanism 1420b is fixed, the first transmission mechanism 1420a lowers the number of revolutions and enters the idle state again. The gear ratio between the speed change gears 1420a, 1420b and 1420c and the output gears 1430a and 1430b are different from each other and the coupling relations between the speed change gears 1420a, 1420b and 1420c are also different from each other , The first speed ratio and the second speed ratio are different from each other.

Thus, the output gear 1430 revolves at a second speed ratio different from the first speed ratio. Similarly, when the turbine speed becomes higher, the third transmission gear 1420c reaches the third adjustment speed, is fixed at the third adjustment speed and rotates to generate the rotation load, and the second speed change gear 1420b is in the idling state . As a result, the output gears 1430a and 1430b revolve at the third speed ratio.

Finally, when all of the transmission gears 1420a, 1420b, 1420c and the output gears 1430a, 1430b rotate at +1, that is, at the input rotation speed, The ratio of the number of output rotations to the number of rotations reaches 100%.

The types, gear ratios, coupling relations, and the like of the gears 1410, 1420, and 1430 of the output unit 1400 are not limited to the above examples. As described above, since the number of gearshifts is determined according to the number of teeth of the transmission gear 1420, the number of teeth of the transmission gear 1420 can be changed according to the desired gearshift number. By adjusting the number of teeth of the gears according to the purpose, the number of revolutions of the required output shaft 1442 can be obtained.

Hereinafter, an embodiment of a shift method according to the present invention will be described. When the rotational force is inputted from the outside, the transmission 1000 automatically changes the speed ratio according to the rotational speed of the turbine and outputs a rotational force.

FIG. 18 is a table showing an example of the number of teeth of the gears used in the transmission 1000, FIG. 19 is a table relating to a shifting step according to an embodiment of the shifting state, and FIG. FIG. 21 is a graph relating to the number of rotations of the carrier 1440 according to the shifting step of FIG. 19; FIG.

The transmission 1000 sequentially goes through a neutral state, a low speed state, a medium speed state, and a high speed state from the state where the number of turbine rpm is 0 to the one rotation state. Here, the neutral state means a state in which all of the speed change gears 1420a, 1420b and 1420c idle, and the low speed state, middle speed state and high speed state correspond to the first transmission gear 1420a, the second transmission gear 1420b, 3 " means a state in which the third speed change gear 1420c is rotated at the fixed speed and rotates to generate a rotational force with respect to the load.

Hereinafter, each state will be described with a trajectory.

Hereinafter, the neutral state will be described with reference to FIG.

FIG. 22 is a diagram relating to the neutral state of FIG. 19; FIG.

First, when a rotational force is inputted to the input shaft 1110, the rotational force is transmitted through the input shaft 1110, the impeller 1220, the turbine 1230, the turbine shaft 1240, the transmission gear 1250, the power shaft 1260, 1410). The turbine 1230, the turbine shaft 1240, the transmission gear 1250, the power shaft 1260, and the power gear 1410 are rotated by the turbine rotation speed, and the input shaft 1110 and the impeller 1220 rotate by +1. , And the range is rotated from 0 to +0.245.

Another rotational force is transmitted to the first unidirectional bearing 1330a via the input shaft 1110, the input shaft gear 1130, the first adjusting gear 1310a, and the first adjusting shaft 1320a.

The first adjustment shaft 1320a and the first inner bearing 1331a of the first unidirectional bearing 1330a are rotated by the first adjustment gear 1310a at the first adjustment speed of -0.225.

The rotational force is transmitted to the second unidirectional bearing 1330b via the input shaft 1110, the input shaft gear 1130, the second adjusting gear 1310b, and the second adjusting shaft 1320b.

The second inside bearing 1331b of the second adjusting shaft 1320a and the second bearing 1330b is rotated by the second adjusting driving gear 1311b and the second adjusting driven gear 1312b to the second adjusting rotation speed .

The rotational force is transmitted to the third inside bearing 1331c of the third unidirectional bearing 1330c via the input shaft 1110 and the protruding portion 1140. [ And the third inside bearing 1331c rotates at a third adjusted rotational speed of +1.

In this state, the power gear 1410 is coupled to the first output gear 1430a and transmits torque to the first output gear 1430a and the second output gear 1430b. The transmission gears 1420a, 1420b and 1420c receive rotational force from the output gears 1430a and 1430b and rotate. As shown in the graph of FIG. 20, the rotation of the respective transmission gears 1420a, Since the rotation speed is sufficiently lower than the first, second, and third adjustment rotations, it is possible to freely idle without receiving a rotational load from the bearing 1330. [ Accordingly, the output gears 1430a and 1430b are not revolved by the rotational load of the output shaft 1442 connected to the carrier 1440, but rotate only.

When the turbine speed is increased from zero to +0.245, the transmission gears 1420a, 1420b, and 1420c are rotated from 0 to -0.225, 0 to -0.8245, and 0 to +0.4909, respectively. In this section, since the output gear 1430 rotates only and does not revolve, the number of rotations of the carrier 1440 becomes zero. That is, in the neutral state, the transmission 1000 does not output rotation to the outside.

As described above, the adjustment rotation speed and the shifting method for each step are -0.225 rotation to the first inner unidirectional bearing 1331a, -1 rotation to the second inner unidirectional bearing 1331b, and -1 rotation to the third inner unidirectional bearing 1331c The adjustment rotation speed set by +1 rotation always has a constant rotation speed in any state of the shift.

Since the rotation of the outer unidirectional bearing relative to the adjustment rotation speed set for the first, second and third inner bearings is controlled so that it can not rotate faster than the adjustment rotation speed set by the characteristics of the unidirectional bearings, the inner and outer unidirectional The bearings are fastened together and rotated at the adjusted rotation speed.

According to this shift method, unidirectional bearings capable of corresponding to the load among the first, second, and third unidirectional bearings are automatically engaged according to the load of the input shaft and the output shaft, and are rotated by the set rotation speed.

Hereinafter, the low-speed state will be described with reference to Figs. 23A and 23B. FIG. 23A is a rotation direction table of the operating gear in the low speed state of FIG. 19, FIG. 23B is a diagram of the low speed state of FIG. 19, and FIG.

As in the neutral state, the power gear 1410 receives torque from the input shaft 1110 through the torque converter unit 1200 and rotates. Here, the turbine 1230 is closer to the rotational speed of the impeller 1220 than in the neutral state. Thus, the power gear 1410 rotates at a turbine speed in the range of +0.245 to +0.3847. This rotation corresponds to the low-speed section of FIG.

In this state, the inner bearings 1331a, 1331b, and 1331c rotate at the adjusted rotational speed of -0.225, -1, +1, respectively, as in the neutral state.

As described above, when the turbine speed is +0.245, the first speed change gear 1420a rotates at a first adjustment speed of -0.225. When the turbine rpm is higher than this, the first transmission gear 1420a tries to rotate faster than 0.225 in the direction opposite to the input rotation. However, since the first inner bearing 1331a rotates to -0.225, the first outer bearing 1332a attempts to rotate faster than 0.225 in the direction opposite to the input rotation, but can not be accelerated because of the nature of the unidirectional bearing. Accordingly, the first transmission gear 1420a receives a rotational load from the first unidirectional bearing 1330a through the first control shaft 1340a, and is fixed at -0.225 and is rotated.

As the number of rotations of the turbine increases, the output gear 1430 tries to rotate more rapidly. Since the rotational load applied to the output gear 1430 from the first transmission gear 1420a is larger than the rotational load applied from the carrier 1440 As a result, the number of revolutions of the output gear 1430 is reduced and the idle revolution starts with the carrier.

When the turbine speed is increased from +0.245 to +0.3847, the first transmission 1420a rotates fixedly at -0.225, and the second transmission 1420b and the third transmission 1420c rotate at a speed of -0.8245 to -1 , + 0.4909 to + 0.7005. In this section, the output gear 1430 revolves at a rotation speed of 0 to +0.0659. Therefore, the carrier 1440 also rotates from 0 to +0.0659.

Hereinafter, the medium-speed state will be described with reference to FIG. Fig. 24A is a rotation direction table of the operating gear in the intermediate speed state of Fig. 19, Fig. 24B is a diagram of the intermediate speed state of Fig. 19, which corresponds to the middle speed section of Fig.

The power gear 1410 rotates at a turbine speed of + 0.3847 to +0.6286 when the turbine 1230 is closer to the rotational speed of the impeller 1220 than to the low speed state. Also, the inner bearings 1331a, 1331b, and 1331c always rotate at the adjusted rotation speed of -0.225, -1, +1, respectively, as described above.

And when the turbine speed is +0.3847, the second speed change gear 1420b rotates at -1, which is the second adjusted speed. Accordingly, in the intermediate speed state, the second transmission gear 1420b receives the rotational force from the second bearing 1330b and is fixed at -1 and rotated.

As the number of turbine rpm increases, the output gear 1430, which is engaged with the power gear 1410, tries to rotate more rapidly, and rotation is reduced due to the load of the second transmission gear 1420b, Is increased.
The load applied to the output gear 1430 by the second transmission gear 1420b is larger than the rotational load applied from the carrier 1440 at this time.

Since the gear ratio of the second transmission gear 1420b with respect to the first output rear stage gear 1432a is smaller than the gear ratio of the first transmission gear 1420a with respect to the second output front gear 1431b, The second transmission 1420b rotates faster than the first transmission 1420a with respect to the number of revolutions of the first transmission 1420a. Accordingly, when the turbine speed is further increased on the basis of +0.3847, the rotational load by the second transmission 1420b becomes larger than the rotational load by the first transmission 1420a. Therefore, the ratio of the revolving speed to the turbine revolutions is reduced, so that the output rotation is increased.

Therefore, when the second transmission gear 1420b is fixed and rotated at the second adjusting rotational speed, the output gear 1430 is caused to revolve faster by the second transmission gear 1420b. Accordingly, the first transmission gear 1420a decreases in speed and rotates slower than the first adjustment rotation speed, and enters the idle rotation state.

When the turbine speed is increased from +0.3847 to +0.6286, the second transmission gear 1420b is fixedly rotated to -1, and the first transmission gear 1420a in the idle rotation state and the third transmission gear 1420c ) Are rotated from -0.225 to +0.0885 and +0.7005 to +1, respectively. In this section, the carrier 1440 revolves at a rotational speed of +0.0659 to 0.2536. As can be seen from this graph, the output rotation speed with respect to the input rotation speed is increased in the middle speed state in comparison with the low speed state.

In FIG. 21, the slope of the output rotation graph at the middle speed section is higher than that of the output rotation graph at the low speed section.

Hereinafter, the high-speed state will be described with reference to FIG.

FIG. 25A is a rotation direction table of the operating gear in the high speed state of FIG. 19, FIG. 25B is a diagram of the high speed state of FIG. 19, and FIG.

The power gear 1410 rotates at a turbine speed of + 0.6286 to +1 when the turbine 1230 is closer to the rotational speed of the impeller 1220 than to the intermediate speed state. Further, the inner bearings 1331a, 1331b, and 1331c always rotate at an adjusted rotation speed of -0.225, -1, +1.

And when the turbine speed is +0.6286, the third speed change gear 1420c is rotated at +1 being the third adjustment speed. Therefore, in the high-speed state, the third transmission gear 1420c receives the rotational load from the unidirectional bearing 1330c and is fixed at +1 and rotated.

As the number of rotations of the turbine increases, the output gear 1430 tries to rotate more quickly, and a rotational load larger than the rotational load applied from the carrier 1440 is applied from the third transmission gear 1420c to the output gear 1430, The gear 1430 is revolved by the third transmission gear 1420c.

Since the gear ratio of the third transmission gear 1420c to the second output rear stage gear 1432b is smaller than the gear ratio of the second transmission gear 1420b to the first output rear gear 1432a, The third speed changer 1420c rotates faster than the second speed changer 1420b with respect to the number of revolutions of the second speed changer 1420b. Therefore, when the turbine speed is further increased with reference to +0.6286, the rotational load by the third speed change gear 1420c is larger than the rotational load by the second speed change gear 1420b. Therefore, The number of revolutions per minute is increased.

Therefore, when the third transmission gear 1420c is fixed at the third adjustment rotational speed and rotated, the output gear 1430 is caused to revolve faster by the third transmission gear 1420c. Accordingly, the second transmission gear 1420b decreases in speed and rotates slower than the second adjustment rotation speed, thereby idling.

When the turbine speed is increased from +0.6286 to +1, the third speed change gear 1420c is fixedly rotated by +1, and the first speed change gear 1420a and the second speed change speed gear 1420b are + 0.0885 to +1 , -1 to +1. In this section, the output gear 1430 revolves at a rotational speed of +0.2536 to +1. Therefore, carrier 1440 also rotates from + 0.2536 to +1. As can be seen from this graph, the output rotation speed with respect to the input rotation speed is increased in the high speed state in comparison with the medium speed state.

Theoretically, the turbine rpm finally reaches +1 and becomes equal to the input rpm. In this case, the power gear 1410 rotates at +1, and all of the transmission gears 1420a, 1420b, and 1420c rotate at +1, and the output gear enters a state of revolving at +1 without rotating. Thus, the carrier 1440 is rotated by +1. That is, the input rotation speed and the output rotation speed become the same, and the output rotation reaches 100%.

Since all the components of the display device according to the present invention are not essential, the display device can selectively include all or a part of the above-described components.

In addition, the present invention can be variously modified, substituted, and modified without departing from the technical spirit of the present invention by those of ordinary skill in the art to which the present invention belongs. Therefore, And all or some of the embodiments may be selectively combined so that various modifications can be made.

1000: transmission 1100: input unit 1110: input shaft
1120: spline 1130: input shaft gear 1140: protrusion
1200: torque converter section 1210: torque converter 1220: impeller
1221: spline 1230: turbine 1240: turbine shaft
1241: Turbine shaft gear 1250: Transfer gear 1251: Transfer drive gear
1252: transmission driven gear 1260: power shaft 1261: power shaft gear
1300: control unit 1310: adjusting gear 1311: adjusting driving gear
1312: Adjusting driven gear 1320: Adjusting shaft 1321: Adjusting shaft gear
1330: unidirectional bearing 1331: inner bearing 1332: outer bearing
1340: Control shaft 1400: Output part 1410: Power gear
1420: Transmission gear 1430: Output gear 1431: Output sun gear
1432: output terminal 1440: carrier 1441: carrier shaft
1442: Output shaft

Claims (13)

An input shaft 1110 to which rotation is input from the outside;
A torque converter 1210 mounted on the input shaft;
A power gear rotated by the torque converter;
An output gear (1430a, b) coupled to the power gear and rotating at least one of idle and rotating by the power gear;
Transmission gears 1420a, b, and c that are coupled to the output gear to generate idle rotation or rotational load; And
And a carrier (1440) rotating according to revolution of the output gear
A transmission (1000). The method according to claim 1,
The output gear is only rotated when the transmission gear idles,
When a rotational load is generated in the transmission,
Transmission. 3. The method of claim 2,
Wherein the transmission is rotated by the power gear and idles until the adjusted rotation speed, and when the adjusted rotation speed reaches the adjusted rotation speed, the transmission is fixed at the adjusted rotation speed,
Transmission. The method of claim 3,
And unidirectional bearings 1330a, b and c capable of only one direction of relative rotation of the other with respect to one side,
Wherein one side of the unidirectional bearing is rotated at the adjusted rotation speed by the input shaft,
The other side of the unidirectional bearing rotates integrally with the transmission, and the transmission rotates idly until the adjusted rotation speed. When the rotation reaches the adjusted rotation speed,
Transmission. 5. The method of claim 4,
The input shaft is provided with an input shaft gear 1130 rotating at an input revolution speed,
And an adjusting gear (1310a) fastened to the input shaft gear,
One side of the unidirectional bearing is rotated by the adjustment gear 1310a at the adjustment rotation speed
Transmission. 5. The method of claim 4,
The input shaft is provided with a protruding portion 1140 that rotates at an input rotational speed,
Wherein one side of the unidirectional bearing is rotated by the projecting portion at an adjustment rotation speed equal to the input rotation speed
Transmission. 7. The method according to any one of claims 3 to 6,
Wherein the number of the speed change gears of the plurality of transmission gears is different from each other,
Wherein the plurality of transmission gears are arranged such that as the number of rotations of the power gear increases,
Transmission. 8. The method of claim 7,
The carrier does not rotate when all of the plurality of transmission gears do not reach the adjustment rotation speed,
When one of the plurality of transmission gears reaches the adjustment rotation speed, the output gears 1430a, b are caused to revolve by a rotational load generated in the transmission gear that reaches the adjustment rotation speed
Transmission. 9. The method of claim 8,
The number of revolutions of the carrier with respect to the number of revolutions of the input shaft is different for each of the transmission gears 1420a (b, c)
Transmission. An input shaft rotating at an input revolution number;
A torque converter including an impeller coupled to the input shaft and a turbine rotating at a turbine speed by the impeller;
A turbine shaft gear 1241 rotated by the turbine;
An input shaft gear and a protrusion formed on the input shaft;
A first adjusting gear 1310a and a second adjusting gear 1310b fastened to the input shaft gear;
A first unidirectional bearing 1330a whose inner side rotates at a first adjusting rotational speed by the first adjusting gear;
A second unidirectional bearing 1330b whose inner side rotates at a second adjusting rotational speed by the second adjusting gear;
A third unidirectional bearing 1330c whose inner side rotates at a third adjustment rotational speed by the projecting portion;
A first transmission gear 1420a connected to the outside of the first unidirectional bearing;
A second transmission gear 1420b connected to the outside of the second unidirectional bearing;
A third transmission gear 1420c connected to the outside of the third unidirectional bearing;
An output gear 1430b engaged with the first and third transmission gears;
An output gear 1430a engaged with the second transmission gear and the power gear 1410;
And a carrier 1440 that rotates by the revolution of at least one of the output gear 1430b and the output gear 1430a
Transmission. 11. The method of claim 10,
The output gear 1430a is rotated by the power gear 1410 and the second transmission gear and the output gear 1430b are rotated by the output gear so that the first and second speed- Fish
Transmission. 12. The method of claim 11,
Wherein the first transmission gear is idle to the first adjustment rotation speed by the first unidirectional bearing and is fixed and rotated at the first adjustment rotation speed when the first unidirectional bearing reaches the first adjustment rotation speed,
The second transmission gear is idle to the second adjustment rotation speed by the second unidirectional bearing and is fixed at the second adjustment rotation speed when it reaches the second adjustment rotation speed,
The third transmission gear is idly rotated to the third adjustment rotation speed by the third unidirectional bearing and is fixed to the third adjustment rotation speed when it reaches the third adjustment rotation speed,
Transmission. 13. The method of claim 12,
The first transmission 1420a, the second transmission 1420b and the third transmission 1420c are idle when the turbine speed is in the first range and the output gear 1430b and the output The gear 1430a does not undergo a rotational load and only rotates,
When the turbine rotation speed is in the second range, the second transmission gear and the third transmission gear idle, the first transmission gear is fixed at the first adjustment rotation speed, and the output gear 1430a is rotated The first speed change gear is rotated at a first speed change ratio by a rotational load of the first speed change gear,
When the turbine speed is in the third range, the first transmission gear and the third transmission gear idle, the second transmission gear is fixed and rotated at the second adjustment speed, and the output gear 1430a A second speed change ratio larger than the first speed change ratio by a rotational load of the second speed change gear,
When the turbine speed is in the fourth range, the first transmission gear and the second transmission gear idle, the third transmission gear is fixed at the third steering speed and rotates, and the output gear 1430b , And is revolved at a third speed change ratio that is larger than the second speed change ratio by the rotational load of the third speed change gear
Transmission.

Images