WO2014046418A1

WO2014046418A1 - Transmission

Info

Publication number: WO2014046418A1
Application number: PCT/KR2013/008243
Authority: WO
Inventors: 나종오; 오명수; 김영일
Original assignee: Ra Chong Oh; Oh Myeong Soo; Kim Young Il
Priority date: 2012-09-18
Filing date: 2013-09-12
Publication date: 2014-03-27
Also published as: KR20140037435A; KR101487816B1

Abstract

The present invention relates to a transmission and, more particularly, to a transmission for shifting gears without a clutch. An aspect of the present invention includes: an input shaft where a first input shaft gear and a second input shaft gear are disposed; a torque converter unit that has a turbine which rotates by converting an input shaft torque; an input carrier that is disposed so as to be coupled with the turbine and revolve around the input shaft and has a first transmission gear which is engaged with the first input shaft gear; a drive shaft ring gear that is engaged with the first transmission gear; a drive carrier that is connected with the drive shaft ring gear and has a first differential gear and a second differential gear which is engaged with the first differential gear; an output shaft where an output ring gear that is engaged with the second differential gear is disposed; a fixed carrier that is fixed to a housing of the torque converter unit and has planetary gears which are engaged with the second input shaft gear; a first unilateral bearing the outer side of which is disposed so as to be fixed to the fixed carrier and the inner side of which is provided so as to be capable of rotating only in a single direction; a first adjustment gear that is disposed so as to be fixed to an inner side of the first unilateral bearing and is engaged with the first differential gear; a ring gear-shaped transmission gear that is engaged with the planetary gear; a second unidirectional bearing the outer side of which is disposed so as to be fixed to the transmission gear and the inner side of which is provided so as to be capable of rotating only in a single direction; a second adjustment gear that is disposed so as to be fixed to an inner side of the second unidirectional bearing and is engaged with the first differential gear; a third unidirectional bearing the inner side of which is fixed to the input shaft and the outer side of which is provided so as to be capable of rotating only at or below an input speed of rotation; and a third adjustment gear that is coupled with an outer side of the third unidirectional bearing and is engaged with the second differential gear.

Description

gearbox

The present invention relates to a transmission, and more particularly to a transmission that automatically shifts without a clutch.

The transmission is a device that transmits a rotation generated from a power source such as an engine to a driven body such as a wheel of a vehicle. In general, all the transmissions are shifted according to a predetermined gear ratio, and when shifting, cumbersome clutch operation is required for separation and replacement of gears.

Recently, researches on an automatic transmission that automatically shifts to compensate for this are being actively conducted. However, the belt-type automatic transmission developed so far is very complicated in structure and costs a lot in manufacturing, and is not widely used due to wear, noise and slip of the belt.

One object of the present invention is to provide a transmission that is automatically shifted without detachment and replacement of gears.

The problem to be solved by the present invention is not limited to the above-described problem, and the objects not mentioned may be clearly understood by those skilled in the art from the present specification and the accompanying drawings. will be.

According to an aspect of the invention, the first input shaft gear, the input shaft is provided with a second input shaft gear; A torque converter unit having a turbine which rotates by converting torque of the input shaft; An input carrier coupled to the turbine and installed to revolve around the input shaft, the input carrier including a first transmission gear engaged with the first input shaft gear; A power shaft ring gear meshing with the first transmission gear; A power carrier connected to the power shaft ring gear and having a first differential gear and a second differential gear meshing with the first differential gear; An output shaft provided with an output ring gear meshed with the second differential gear; A fixed carrier fixed to a housing of the torque converter unit and having planetary gears meshing with the second input shaft gear; A first unidirectional bearing, the outer side of which is fixedly installed to the fixed carrier and the inner side of which is rotatably provided in one direction; A first adjusting gear fixedly installed inside the first unidirectional bearing and engaged with the first differential gear; A shift gear in the form of a ring gear engaged with the planetary gear; A second unidirectional bearing fixed to the transmission gear and having an outer side rotatably provided in one direction; A second adjusting gear fixedly installed inside the second unidirectional bearing and engaged with the first differential gear; A third unidirectional bearing having an inner side coupled to the input shaft and the outer side being rotatable only at an input rotational speed lower; And a third adjusting gear coupled to the outside of the third unidirectional bearing and engaged with the second differential gear.

In addition, when the rotational speed of the turbine relative to the rotational speed of the input shaft is less than the first threshold value, the rotation and idle of the first transmission gear cancel each other so that the power shaft ring gear is kept stationary, the rotational speed of the input shaft When the rotational speed of the turbine with respect to is less than the first threshold value or less than the second threshold value, the first unidirectional bearing acts as a rotating load such that the output shaft is rotated at a first transmission ratio with respect to the rotational speed of the input shaft, When the rotational speed of the turbine with respect to the rotational speed is less than the second threshold value or less than the third threshold value, the second unidirectional bearing acts as a rotational load so that the output shaft is rotated at a second speed ratio with respect to the rotational speed of the input shaft, When the rotational speed of the turbine with respect to the rotational speed of the input shaft is greater than or equal to the third threshold and less than or equal to the fourth threshold, the third unidirectional bearing acts as a rotational load to The output shaft may be rotated by the third gear ratio with respect to the number of revolutions of the input shaft.

In addition, the first differential gear and the second differential gear is shifted by being constrained by any one of the first unidirectional bearing, the second unidirectional bearing and a third unidirectional bearing according to the rotational speed of the turbine, The restraint by the set number of revolutions is automatically released and another unidirectional bearing is fastened to transfer the rotation shifted to the output shaft.

In addition, when the rotation speed of the turbine is less than or equal to the first threshold value, the rotation and idle of the first transmission gear cancel each other so that the power shaft ring gear may be kept in a stopped state.

In addition, the power shaft ring gear, the first input shaft gear and the first transmission gear may be provided with a ratio of the number of gear teeth 3: 1: 1, the first threshold value may be 0.25.

In addition, when the rotational speed of the turbine relative to the rotational speed of the input shaft is less than the first threshold value or less than the second threshold value, the first differential gear receives the rotational load of the first unidirectional bearing and through the second differential gear The output ring gear can be rotated.

Further, when the rotational speed of the turbine relative to the rotational speed of the input shaft is greater than or equal to the second threshold value and less than or equal to the third threshold value, the first differential gear receives the rotational load of the second unidirectional bearing and the second differential gear receives the rotational load. The output ring gear can be rotated.

In addition, when the rotational speed of the turbine relative to the rotational speed of the input shaft is greater than or equal to a third threshold value and less than or equal to a fourth threshold value, the second differential gear may receive the rotational load of the third unidirectional bearing to rotate the output ring gear. have.

In addition, the ratio of the number of gear teeth of the second input shaft gear and the transmission gear is provided as 1: 3, the first threshold value is 0.25, the second threshold value is 0.4035, the third threshold value is 0.6154, and the third The four threshold may be one.

According to the present invention, the shift may be automatically made according to the number of revolutions converted in the torque converter.

The effects of the present invention are not limited to the above-described effects, and effects that are not mentioned will be clearly understood by those skilled in the art from the present specification and the accompanying drawings.

1 is a block diagram of a transmission apparatus according to an embodiment of the present invention.

2 is a cross-sectional view of the transmission of FIG. 1.

3 is a perspective view of the input unit of FIG. 2.

4 is a cross-sectional view of the torque converter unit of FIG. 2.

5 is a cross-sectional perspective view illustrating main parts of the torque transmission unit, the transmission unit, and the output unit of FIG. 2.

6 is an exploded perspective view showing an input carrier provided with a first transmission gear and a second transmission gear.

7A and 7B are cross-sectional views taken along the lines A-A and B-B shown in FIG. 2.

FIG. 8 is a cross-sectional view taken along line C-C shown in FIG. 2.

9 and 10 are cross-sectional perspective views of main parts for explaining the speed change portion.

11A and 11B are cross-sectional views taken along the lines D-D and E-E of FIG. 2.

12 is a table relating to an example of the number of gears of the transmission of FIG. 2.

FIG. 13 is a table illustrating a shift stage in the shift method using the shift device of FIG. 12.

FIG. 14 is a graph illustrating a rotation speed of the first adjusting gear, the second adjusting gear and the third adjusting gear according to the shifting step of FIG. 13.

FIG. 15 is a graph of the rotation speed of the output shaft according to the shifting step of FIG. 13.

16 is a diagram relating to a transmission order of rotational force in the neutral state of FIG. 13.

FIG. 17 is a table of rotation directions of gears in the neutral state of FIG. 16.

18 is a diagram relating to a transmission order of rotational force in the low speed state of FIG. 13.

19 is a table relating to the rotational direction of the gears in the low speed state of FIG. 18.

20 is a diagram relating to a transmission order of rotational force in the middle speed state of FIG. 13.

FIG. 21 is a table of rotational directions of gears in the medium speed state of FIG. 20.

22 is a diagram relating to a transmission order of rotational force in the high speed state of FIG. 13.

FIG. 23 is a table relating to the rotational direction of the gears in the high speed state of FIG.

Since the embodiments described herein are intended to clearly explain the spirit of the present invention to those skilled in the art to which the present invention pertains, the present invention is not limited to the embodiments described herein, and the present invention. The scope of should be construed to include modifications or variations without departing from the spirit of the invention.

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

In addition, in describing the present invention, when it is determined that the detailed description of the related well-known configuration or function may obscure the gist of the present invention, the detailed description thereof will be omitted.

The transmission device 1000 according to the present invention shifts and outputs the rotation when it is input. Specifically, the transmission device 1000 converts an input rotational force, that is, a torque by applying a torque converter, and automatically operates the unidirectional bearings that are constrained for each shift stage, without a separate clutch operation. Shift to output.

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

1 is a block diagram of a transmission apparatus 1000 according to an exemplary embodiment of the present invention, and FIG. 2 is a cross-sectional view of the transmission apparatus 1000 of FIG. 1.

1 and 2, the transmission apparatus 1000 may include an input unit 1100, a torque converter 1200, a torque transmission unit 1300, a transmission unit 1400, and an output unit 1500.

The rotational force is input to the input unit 1100, and the torque converter 1200 converts the torque of the input rotational force. The torque transmission unit 1300 transmits the rotational force of the input unit 1100 and the rotational force of the torque converter unit 1200 to the transmission unit 1400 using the composite planetary gear and the fixed planetary gear structure. The transmission unit 1400 shifts the rotational force transmitted by using the

unidirectional bearings

1310, 1320 and 1330 and the differential gear structure and outputs the output to the output unit 1500.

Hereinafter, each component of the transmission apparatus 1000 will be described.

The input unit 1100 receives a rotation force from the outside.

3 is a perspective view of the input unit 1100 of FIG. 2.

Referring to FIG. 3, the input unit 1100 includes an input shaft 1110, an impeller connecting member 1120, a first input shaft gear 1130, a second input shaft gear 1140, and a bearing connecting member 1150. can do.

The input shaft 1110 is provided in the form of a rod having a circular cross section. The input shaft 1110 may receive a rotational force from the outside and rotate accordingly. Hereinafter, the rotation speed of the input unit 1100 will be referred to as an input rotation speed.

The impeller connecting member 1120, the first input shaft gear 1130, the second input shaft gear 1140, and the bearing connecting member 1150 may be sequentially provided on the input shaft 1110.

The impeller connecting member 1120 connects the input shaft 1110 and the impeller 1220. For example, the impeller connecting member 1120 may be provided in a disc shape around the input shaft 1110 such that the shaft or plate extending from the impeller 1220 or the impeller 1220 is engaged. Accordingly, the rotational force input to the input shaft 1110 may be transmitted to the torque converter unit 1200.

The first input shaft gear 1130 may be provided in the form of a sun gear formed on the input shaft 1110. The first input shaft gear 1130 may be engaged with the first transmission gear 1160 of the torque transmission unit 1300, thereby transmitting the rotational force input to the input shaft 1110 to the torque transmission unit 1300.

The second input shaft gear 1140 may be provided between the first input shaft gear 1140 and the bearing connecting member 1150 in the form of a sun gear formed on the input shaft 1110. The second input shaft gear 1140 may be engaged with the planetary gears 1315 of the torque transmission unit 1300, thereby transmitting the rotational force input to the input shaft 1110 to the torque transmission unit 1300.

The bearing connecting member 1150 may be formed to protrude in a circular ring shape on the input shaft 1110. The outer circumferential surface of the bearing connecting member 1150 is engaged with the inner bearing of the third unidirectional bearing 1330. Accordingly, the inner bearing of the third unidirectional bearing 1330 may rotate at an input speed.

The torque converter 1200 converts torque of the rotational force transmitted from the input unit 1100.

4 is a cross-sectional view of the torque converter 1200 of FIG. 2.

Referring to FIG. 4, the torque converter unit 1200 includes a housing 1210, an impeller 1220, a turbine 1230, and a turbine shaft 1240.

Housing 1210 houses impeller 1220, turbine 1230, and turbine shaft 1240 therein. The housing 1210 may be fixed to the outside to maintain a stop state regardless of the rotation of the input shaft 1110. A fixed gear 1250 is installed in the housing 1210, and the fixed gear 1250 is fastened to the second transmission gear 1161.

The impeller 1220 is connected to the impeller connecting member 1120 to rotate integrally with the input shaft 1110. The impeller 1220 may be provided in a wheel shape having a plurality of wings provided to be rotatable about the input shaft 1110.

The turbine 1230 may be provided in a wheel shape having a plurality of wings disposed to face the impeller 1220. The turbine 1230 may convert the torque of the rotational force of the impeller 1220.

Specifically, a fluid may be provided between the impeller 1220 and the turbine 1230 inside the housing 1210. As the fluid rotates, kinetic energy is transferred to the fluid, which in turn causes the turbine 1230 to rotate. As such, the torque may be converted while the impeller 1220 rotates the turbine 1230 through the fluid. Hereinafter, the rotation speed of the converted turbine 1230 is referred to as turbine rotation speed.

Meanwhile, a stator (not shown) may be additionally disposed between the impeller 1220 and the turbine 1230 in the torque converter 1200. The stator (not shown) may increase the efficiency with which the torque is converted.

The turbine shaft 1240 has one end extending from the turbine 1230 and the other end coupled with the input carrier 1170. Accordingly, the turbine shaft 1240 may rotate together with the turbine 1230 to transmit the rotational force of the turbine 1230 to the input carrier 1170.

The torque transmission unit 1300 receives the rotational force from the input unit 1100 and the torque converter 1200 and transfers the rotational force to the transmission unit 1400.

5 is a cross-sectional perspective view illustrating main parts of the torque transmission unit, the transmission unit, and the output unit of FIG. 2, and FIG. 6 is an exploded perspective view illustrating an input carrier provided with a first transmission gear and a second transmission gear. 7A and 7B are cross-sectional views taken along the lines A-A and B-B shown in FIG. 2.

2 and 5 to 7b, the torque transmission unit 1300 may include an input carrier 1170, a first transmission gear 1160, a second transmission gear 1161, a power shaft ring gear 1180, and a power source. A shaft 1181, a first control shaft gear 1312, a first control shaft 1311, a fixed carrier 1313, a planetary gear 1315, a transmission gear 1322, and a second control shaft 1321. Can be.

The input carrier 1170 is provided revolved about the input shaft 1110. The input carrier 1170 may be coupled to the turbine shaft 1240 to rotate with the turbine 1230 and the turbine shaft 1240 to revolve around the input shaft 1110. The input carrier 1170 is coupled to a flange 1242 formed outwardly at the rear end of the turbine shaft 1240.

The input carrier 1170 has a first fixing pin 1171a and a second fixing pin so that the first transmission gear 1160 and the second transmission gear 1161 rotate and rotate about the input shaft 1110 at the same time. 1171b is provided.

The first transmission gear 1160 is arranged to be rotatable to the first fixing pin 1171a. One side of the first transmission gear 1160 is coupled to the first input shaft gear 1130. Accordingly, the first transmission gear 1160 may rotate by receiving rotational force from the first input shaft gear 1130. In addition, the other side of the first transmission gear 1160 is coupled to the power shaft ring gear 1180.

As described above, the first transmission gear 1160 rotates by the first input shaft gear 1130 while revolving together with the input carrier 1170. 1180 may transmit a rotational force.

The second transmission gear 1161 is arranged to be rotatable on the second fixing pin 1171b. The second transmission gear 1161 includes a front end 1161a and a rear end 1161b, and a fixed gear 1250 is fastened to the front end 1161a, and a first control shaft gear (1) at the rear end 1161b. 1312 may be fastened. The second transmission gear 1161 is formed concavely between the front end portion 1161a and the rear end 1161b so that interference with the first transmission gear 1160 does not occur.

The power shaft ring gear 1180 is provided in the form of a ring gear to which the first transmission gear 1160 is fastened therein. The power shaft ring gear 1180 may rotate by receiving rotational force from the first transmission gear 1160 according to a combination of revolution and rotation of the first transmission gear 1160.

One end of the power shaft 1181 extends from the power shaft ring gear 1180, and the other end is coupled to the power carrier 1182. Accordingly, the power shaft 1181 transmits the rotational force of the power shaft ring gear 1180 to the power carrier 1182, whereby the power shaft ring gear 1180, the power shaft 1181, and the power carrier 1182 are It can be rotated integrally.

Here, the fixed gear 1250 and the first control shaft gear 1312 are not configured for power transmission purposes, but are provided for the purpose of fixing the first unidirectional bearing 1310 and fastening the second unidirectional bearing 1320. In more detail, the fixed gear 1250 integral with the housing 1210 fixes the first control shaft gear 1312 through the second transmission gear 1161.

For example, since the number of teeth of the fixed gear 1250 is 20T, the number of teeth of the first control shaft gear 1312 is 20T, and the number of teeth of the second transmission gear 1161 are connected to 14T, the fixed gear 1250 remains fixed without any rotation. Can be. However, the second transmission gear 1161 will only idle with the input carrier 1170.

FIG. 8 is a cross-sectional view taken along line C-C shown in FIG. 2.

2 and 8, the fixed planetary gear member is positioned between the input carrier 1170 and the power carrier 1182 and includes the fixed carrier 1313 and the planetary gears 1315.

The fixed carrier 1313 is engaged with the first control shaft gear 1312 and remains stationary. The first control shaft 1311 is coupled to the fixed carrier 1313. The first control shaft 1311 is connected to the first transmission 1310a.

The planetary gears 1315 are arranged to be rotatable on the fixing pins 1313a installed in the fixed carrier 1313. One side of the planetary gear 1315 is coupled to the second input shaft gear 1140. Accordingly, the planetary gear 1315 may rotate by receiving rotational force from the second input shaft gear 1140. The other side of the planetary gear 1315 is engaged with the transmission gear 1322. Therefore, the transmission gear 1322 is rotated by receiving a rotation force from the planetary gear 1315. The transmission gear 1322 is connected to the second transmission 1320a through the second control shaft 1321.

The transmission unit 1400 shifts the rotational force transmitted from the torque transmission unit 1300 and outputs the output to the output unit 1500.

9 and 10 are cross-sectional perspective views of main parts for explaining the speed change unit, and FIGS. 11A and 11B are cross-sectional views taken along the lines D-D and E-E shown in FIG. 2.

2 and 9 to 11B, the transmission unit includes a power carrier 1182, a first differential gear 1410, a second differential gear 1420, a first transmission 1310a, a second transmission 1320a, The third transmission 1330a is included.

Power carrier 1182 is provided to be rotatable to input shaft 1110. The power carrier 1182 may be coupled to the power shaft 1181 to revolve around the input shaft 1110 together with the power shaft ring gear 1180 and the power shaft 1181.

The power carrier 1182 may include a first fixing pin 1183a and a second fixing pin so that the first differential gear 1410 and the second differential gear 1420 rotate and rotate about the input shaft 1110 at the same time. 1183b) is installed.

The first differential gear 1410 includes a front end 1411 and a rear end 1412 having different sizes of gears. The first adjusting gear 1317 is fastened to the front end 1411, the second adjusting gear 1324 is fastened to one side of the rear end 1412, and the second differential gear 1420 is connected to the other end of the rear end 1412. ) Can be fastened.

The second differential gear 1420 includes a front end 1421 and a rear end 1422 having the same size of the gears. The rear end portion 1412 of the first differential gear is fastened to the front end portion 1421, and the third adjustment gear 1332 and the output ring gear 1510 are fastened to the rear end 1422.

Due to this structure, the first differential gear 1410 and the second differential gear 1420 revolve around the input shaft 1110 by the power carrier 1182 and are fastened to each other. Accordingly, the shift is performed by being constrained by the transmissions, and the rotational force transmitted to the output ring gear 1430 may be transmitted. The shifting process will be clearer in the shifting method described below.

In order to balance torque, the first differential gear 1410 and the second differential gear 1420 are provided in pairs, respectively, and the first differential gear 1410 and the second differential gear 1420 are provided to transmit stable torque. The input shaft 1110 may be provided to be symmetrical to each other.

The first differential gear 1410 and the second differential gear 1420 may be fastened to each other. In addition, a first transmission 1310a and a second transmission 1320a are connected to the first differential gear 1410, and a third adjustment gear 1330a is connected to the second differential gear 1420. The second differential gear 1420 is also connected to the output ring gear 1510.

The first transmission 1310a includes a first unidirectional bearing 1310, a first adjusting shaft 1316 and a first adjusting gear 1317.

The first unidirectional bearing 1310 is a unidirectional bearing centered on the input shaft 1110 and has an inner bearing and an outer bearing. The outer bearing is coupled to the fixed carrier 1313 via the first control shaft 1311, and the inner bearing is coupled to the first adjustment shaft 1316. One end of the first adjustment shaft 1316 is coupled to the inner bearing, and the other end is provided with a first adjustment gear 1317. The first adjusting gear 1317 is engaged with the front end 1411 of the first differential gear 1410.

In the unidirectional bearings, the inner and outer bearings are freely idle without load when the rotational force is applied in the opposite direction, whereas the inner and outer bearings are not rotated when the inner direction and the rotational force are applied. This can act as a rotating load. Hereinafter, a direction in which idling is possible is referred to as a free direction, and an opposite direction is referred to as a load direction.

In the first unidirectional bearing 1310, since the outer bearing is coupled to the fixed carrier 1313, the outer bearing remains fixed, and the inner bearing is coupled to the first adjustment shaft 1316, so the first adjustment is performed. Rotate with shaft 1316. Here, when the inner bearing rotates in the free direction (+) with respect to the outer bearing, rotation is possible without a load, and when the rotational force is applied in the load direction (-), the rotation of the first unidirectional bearing 1310 is impossible. Both the inner bearing and the first adjustment shaft 1316 remain stationary.

According to this structure, when a rotational force in the free direction (+) is applied to the first unidirectional bearing 1310 from the first differential gear 1410, the first unidirectional bearing 1310 rotates idlingly to the first differential gear 1410. When no load is applied and rotational force in the load direction is applied to the first unidirectional bearing 1310 from the first differential gear 1410, the first unidirectional bearing 1310, the first adjustment shaft 1316, and the first All of the adjusting gears 1317 may stop to apply a load to the first differential gear 1410.

For example, when the rotation speed of the turbine 1230 with respect to the rotation speed of the input shaft 1110 is less than the first threshold value or less than the second threshold value, the first differential gear 1410 may load the rotation load of the first unidirectional bearing 1310. And rotates the output ring gear 1510 through the second differential gear 1420.

The second transmission 1320a includes a second unidirectional bearing 1320, a second adjusting shaft 1323, and a second adjusting gear 1324.

The second unidirectional bearing 1320 is a unidirectional bearing centered on the input shaft 1110 and has an inner bearing and an outer bearing. The second unidirectional bearing 1320 is located between the first unidirectional bearing 1310 and the fixed carrier 1313. The outer bearing is connected to the transmission gear 1322 via the second control shaft 1321, and the inner bearing is coupled to the second adjustment shaft 1323. One end of the second adjustment shaft 1323 is coupled to the inner bearing, and the other end of the second adjustment shaft 1324 is provided. The second adjustment gear 1324 is engaged with the rear end 1412 of the first differential gear 1410.

For example, when the rotation speed of the turbine 1230 with respect to the rotation speed of the input shaft 1110 is greater than or equal to the second threshold value and less than or equal to the third threshold value, the first differential gear 1410 may load the rotation load of the second unidirectional bearing 1320. And rotates the output ring gear 1510 through the second differential gear 1420.

The third transmission 1330a includes a third unidirectional bearing 1330, a third adjustment shaft 1331, and a third adjustment gear 1332.

The third unidirectional bearing 1330 is provided as a unidirectional bearing about the input shaft 1110, similar to the first unidirectional bearing 1310, and has an inner bearing and an outer bearing. The inner bearing is coupled to the bearing connecting member 1150 and the outer bearing is coupled to the third adjustment shaft 1331. One end of the third adjustment shaft 1331 is coupled to the outer bearing, and the other end is provided with a third adjustment gear 1332. The third adjustment gear 1332 is engaged with the second differential gear 1420.

In the third unidirectional bearing 1330, since the inner bearing is coupled to the bearing connecting member 1150 formed on the input shaft 1110, the inner bearing rotates at an input speed with the input shaft 1110, and the outer bearing 3 is rotated together with the third adjustment shaft 1331 because it is coupled to the adjustment shaft 1331. Here, since the inner bearing rotates at the input rotation speed, when the outer bearing rotates at a lower rotation speed or in the opposite direction, the third bearing 1330 is rotated in the free direction, so that the rotation can be performed without load. When the rotation speed is greater than the input rotation speed, the third unidirectional bearing 1330 cannot be rotated, so that the outer bearing and the third adjustment shaft 1432 both rotate at the input rotation speed.

In this structure, the third adjusting gear 1332 coupled to the outer diameter of the third unidirectional bearing 1330 is idle when the third unidirectional bearing 1330 is idling when a rotational force of less than an input rotational speed is applied. 1420, the third unidirectional bearing 1330, the third adjusting shaft 1331, the third adjusting gear when the reverse rotational speed is applied to the third unidirectional bearing 1330 in the load direction Since all of the 1133 are fixed and rotated at the input rotation speed, the second differential gear 1420 may be loaded.

As described above, the transmission apparatus 1000 according to the present embodiment uses unidirectional bearings that are constrained for each shift stage. The rotational relationship of the unidirectional bearing is engaged when the directions are the same and the rotation of the outer diameter and the inner diameter is the same, and rotates until they are united when the speeds of the outer diameter and the inner diameter are different. In addition, when the directions are different from each other, they are rotated in an idling state according to the connected relative gears without being fastened, and are fastened as one in the same direction and speed.

2 and 10, the output unit 1500 includes an output ring gear 1510 and an output shaft 1520.

The output ring gear 1510 is provided in the form of a ring gear about the input shaft 1110. The second differential gear 1420 is fastened inside the output ring gear 1510. The output ring gear 1510 receives rotational force from the second differential gear 1420.

One end of the output shaft 1520 extends from the output ring gear 1510 and is bent at one point to extend along the direction of the input shaft 1110 in the form of a shaft. The output shaft 1520 may rotate integrally with the output ring gear 1510 to transmit rotational force to the outside.

Hereinafter, a shift method according to an embodiment of the present invention will be described.

On the other hand, the shift method here will be described based on the above-described speed change apparatus 1000 having the number of gears in FIG. However, this is merely for convenience of description, and the number of gears of FIG. 12 is a value determined arbitrarily, and is not limited thereto. In other words, the number of gears of the transmission apparatus 1000 may be set differently from the numerical value of FIG. 12. In this case, the timing at which the neutral, low speed, middle speed, and high speed are shifted in the shift method may be changed. That is, the number of teeth of the gear in the transmission apparatus 1000 may be appropriately added or reduced in consideration of a desired speed ratio or shift timing.

The transmission device 1000 may receive a rotational force from the outside and shift the output to output the rotational force. The transmission apparatus 1000 may perform a shift according to a neutral state, a low speed state, a middle speed state, and a high speed state.

FIG. 12 is a table illustrating an example of the number of gears of the transmission device 1000 of FIG. 2, and FIG. 13 is a table illustrating a shifting step in a shift method using the transmission device 1000 of FIG. 12, and FIG. Is a graph of the rotation speed of the first adjusting gear 1317, the second adjusting gear 1324, and the third adjusting gear 1332 according to the shifting step of FIG. 15, and FIG. 15 is an output shaft 1520 according to the shifting step of FIG. 13. ) Is a graph about the number of revolutions.

According to FIG. 12, the number of gear teeth is 16T for the first input shaft gear 1130, 15T for the second input shaft gear 1140, 16T for the first transmission gear 1160, 48T for the power shaft ring gear 1180, Planetary gear 1315 is 15T, first control shaft gear 1312 is 20T, transmission gear 1322 is 45T, second transmission gear 1161 is 14T, first adjustment gear 1317 is 24T, second adjustment Gear 1324 is 15T, rear end 1412 of first differential gear 1410 is 23T, tip 1411 of first differential gear 1410 is 14T, second differential gear 1420 is 14T, third adjustment Gear 1332 may be provided such that 24T and output ring gear 1510 have 52T.

Referring to FIGS. 13, 14 and 15, in the transmission apparatus 1000 having the aforementioned number of teeth, when the turbine rotational speed is 0 to 0.25 when the input rotational speed is 1, the torque transmission unit 1300 may include the power shaft ring. Since the rotation force is not transmitted to the gear 1180, the output shaft 1520 is in a neutral state in which the rotation does not rotate.

In addition, when the turbine rotational speed is 0.25 to 0.4035, the first adjusting gear 1317 generates a rotational load on the first differential gear 1410 by engaging the first unidirectional bearing 1310, and the second adjusting gear 1324. ) And the third adjustment gear 1332 are rotated in an idling state. Here, the rotation of the idling state refers to the idle state irrelevant to the rotation of the output shaft, it is also a state to rotate for fastening. Accordingly, the first differential gear 1410 transmits rotational force to the second differential gear 1420 while rotating and rotating in accordance with the rotational force of the power shaft ring gear 1180 and the rotational load of the first adjustment gear 1317. The second differential gear 1420 rotates the output ring gear 1510 to output rotational force to the output shaft 1520.

In addition, when the turbine rotational speed is 0.4035 to 0.6154, the second adjustment gear 1324 generates a rotational load on the first differential gear 1410 by engaging the second unidirectional bearing 1320, and the first adjustment gear 1317. ) And the third adjustment gear 1332 are rotated in an idling state. Accordingly, the first differential gear 1410 rotates and rotates according to the rotational force of the power shaft ring gear 1180 and the rotational load of the second adjustment gear 1324, and transmits the rotational force to the second differential gear 1420. The second differential gear 1420 rotates the output ring gear 1510 to output rotational force to the output shaft 1520.

Finally, when the turbine rotational speed is 0.6154 to 1 (same as the input rotational speed), the third adjustment gear 1332 generates a rotational load on the second differential gear 1420 by engaging the third unidirectional bearing 1330. The first adjustment gear 1317 and the second adjustment gear 1324 are rotated in an idling state. Therefore, the second differential gear 1420 rotates the output ring gear 1510 to output rotational force to the output shaft 1520.

Hereinafter, each shift state will be described in more detail. Hereinafter, it is assumed that the input rotational speed is +1, and other rotational speeds are referred to as a ratio thereof. Here, the sign indicates that + is rotation in the same direction as the input rotation, and-is rotation in the opposite direction to the input rotation. For example, in the case of -0.333, it means to rotate at a speed of 1/3 of the input rotation speed in the direction opposite to the input rotation speed.

First, the neutral state will be described.

FIG. 16 is a diagram relating to a transmission order of rotational force in the neutral state of FIG. 13, and FIG. 17 is a table of rotation directions of gears in the neutral state of FIG. 16.

The neutral state is a state in which a rotation input below a predetermined rotation does not rotate the power shaft ring gear 1180 and the output shaft 1520 and only idles in the power shaft ring gear 1180.

Specifically, when the rotational force is input to the input shaft 1110, the rotational force is provided separately from the impeller 1220 and the first input shaft gear 1130 integrated with the input shaft 1110. The impeller 1220 and the first input shaft gear 1130 are rotated at the same input speed + 1 as the input shaft 1110.

Rotation of the impeller 1220 rotates the input carrier 1170 through the turbine shaft 1240 integrated with the turbine 1230, and rotation of the first input shaft gear 1130 is the first inserted into the input carrier 1170. Transmission to the transmission gear 1160, the rotation of these two paths is joined in the input carrier 1170.

Here, since the turbine 1230 and the impeller 1220 are not physically fastened and are configured to transmit rotational force through the fluid, the rotation of the turbine 1230 may be caused by the rotational resistance of the power shaft ring gear 1180 and the impeller ( It may appear different depending on the rotational force of 1220.

The first transmission gear 1160 is inserted into the input carrier 1170, revolves integrally with the input carrier 1170, and is engaged with the first input shaft gear 1130 to apply rotational force from the first input shaft gear 1130. Take it and rotate it. At this time, since the first transmission gear 1160 is fastened to the inner side of the power shaft ring gear 1180, the first transmission gear 1160 is a rotational force received from the input carrier 1170 and the first input shaft gear 1130 as a result. To the power shaft ring gear 1180.

Here, since the power shaft ring gear 1180 is connected to the power carrier 1182 (external output end), it is in a state of receiving a predetermined rotational load. When the turbine rotational speed with respect to the input rotational speed is less than the first threshold value, the rotational load of the power shaft ring gear 1180 is greater and the power shaft ring gear 1180 may not rotate. This is because the turbine 1230 is not in a physically engaged state with the impeller 1220 and is in a relationship in which rotational force is transmitted through the fluid, so that the idle of the input carrier 1170 connected to the turbine 1230 is equal to or less than the first threshold value. This is because it generates little load.

In other words, the input shaft 1110 is rotated by generating only the minimum power from an external power source (engine, etc.), and the rotation is such that the rotation speed of the turbine 1230 is less than 0.25 by the impeller 1220. Turbine 1230 has a rotation speed of 0.25 is a value set such that the rotation of the input carrier 1170 and the rotation of the first input shaft gear 1130 are detailed with each other when the power shaft ring gear 1180 is stationary. It is called the threshold of.

For example, when the number of teeth of the power shaft ring gear 1180 is 48T, the number of teeth of the first input shaft gear 1130 and the number of teeth of the first transmission gear 1160 is 16T, the turbine speed is +0.25, which is the first threshold value. Rotating and idle of the first transmission gear 1160 cancel each other and are not transmitted to the power shaft ring gear 1180 until reaching.

Specifically, when the turbine rotational speed is 0.25 or less, the rotation speed of the first transmission gear 1160 is four times the revolution speed, and when viewed from the outside, once rotation is canceled by one revolution, the first transmission gear (viewed from the outside) 1160) The number of revolutions is three times the number of revolutions.

In this case, the number of teeth of the power shaft ring gear 1180 is three times the number of gears of the first transmission gear 1160 and the first input shaft gear 1130, and as a result, the power shaft ring gear 1180 may maintain a stopped state. .

Therefore, no output occurs in the neutral state where the turbine rotational speed is 0 to +0.25.

Next, the low speed state will be described.

FIG. 18 is a diagram relating to a transmission order of rotational force in the low speed state of FIG. 13, and FIG. 19 is a table relating to the rotation direction of the gears in the low speed state of FIG. 18.

In the low speed state, the power shaft ring gear 1180 is rotated by increasing the rotation speed of the turbine 1230 until the first threshold value +0.25 is reached in the neutral state in which the power shaft ring gear 1180 is stopped. The output shaft 1520 is rotated through the power carrier 1182 integrated with the power shaft ring gear 1180.

When the rotational speed of the turbine 1230 reaches the first threshold value, the rotational force begins to be transmitted from the first transmission gear 1160 to the power shaft ring gear 1180.

For example, when the number of gears of the power shaft ring gear 1180, the first input shaft gear 1130, and the first transmission gear 1160 is 48T, 16T, or 16T, the first transmission is performed when the turbine speed is +0.25. The rotation and idle of the gear 1160 cancel each other, so that the input ring gear 1330 does not rotate. In this case, when the turbine rotation speed increases, the number of gears of the first transmission gear 1160 meshes with the idle and rotation. As the number of gears of the shaft ring gear 1180 is greater, the rotation of the power shaft ring gear 1180 may be started.

When the power shaft ring gear 1180 rotates, the first and second

differential gears

1410 and 1420 installed in the power carrier 1182 and the power carrier 1182 may be integrally formed with the power shaft ring gear 1180. Idle.

In this case, the first differential gear 1410 is connected to the first adjustment gear 1317 of the first transmission 1310a and the second adjustment gear 1324 of the second transmission 1320a. The first adjusting gear 1317 is connected to the inner bearing of the first unidirectional bearing 1310 via the first adjusting shaft 1316, but the rotation is idle. The second adjusting gear 1324 is connected to the inner bearing of the second unidirectional bearing 1320 via the second adjusting shaft 1323.

Here, the first unidirectional bearing 1310 is connected to the housing 1210 whose outer bearing is stationary so that the inner side of the first unidirectional bearing 1310 when the power carrier 1182 tries to rotate in the negative direction The bearing generates a load.

Accordingly, the first adjusting gear 1317 connected to the inner bearing of the first unidirectional bearing 1310 has a stationary state, and the load is transmitted to the first differential gear 1410 via the first adjusting gear 1317. do. That is, the first differential gear 1410 transmits rotational force to the second differential gear 1420 while receiving the load of the first adjusting gear 1317 due to the fastening of the first unidirectional bearing 1310.

The second differential gear 1420 is mounted to the power carrier 1182 and is coupled to the first differential gear 1410 and the output ring gear 1510. The second differential gear 1420 may rotate by the first differential gear 1410 while revolving by the power carrier 1182. Accordingly, the second differential gear 1420 may transmit rotational force to the output ring gear 1510.

Therefore, in the low speed state, the transmission unit 1400 transmits the rotational force to the output unit 1500 according to a constraint condition in which the first transmission 1310a maintains the stop state.

13 to 15, in the case of the transmission 1000 having the number of gears of FIG. 12, when the turbine ring speed is +0.25, the output ring gear 1510 starts to rotate and the turbine speed reaches +0.4035. The rotation speed of the ring gear 1510 reaches +0.0495. Of course, the rotation speed of the first transmission 1310a (first adjusting gear) is maintained at zero during this time.

On the other hand, the second transmission 1320a (second adjusting gear) is held in the first differential gear 1410. The rotation speed of the second transmission 1320a (second adjusting gear) is 0 at turbine speed +0.25. At turbine speed of +0.4035, it reaches -0.333.

A third transmission 1330a (third adjustment gear) is held in the second differential gear 1420. The third transmission 1330a (third adjustment gear) has a rotational speed of 0 to 0 at turbine speed of +0.25. Turbine revolutions reach +0.5409 at +0.4035.

Next, the medium speed state will be described.

FIG. 20 is a diagram illustrating a transmission order of rotational force in the medium speed state of FIG. 13, and FIG. 21 is a table relating to a rotation direction of gears in the medium speed state of FIG. 20.

The medium speed state increases the rotation of the turbine 1230 to a second threshold value of +0.4035 in the low speed state in which the output ring gear 1510 is rotating at a low speed, and through the power shaft ring gear 1180 and the power carrier 1182. The rotation of the output ring gear 1510 is more than the rotation of the low speed state.

The power transmission process is the same as in the low speed state described above, but the first adjustment gear 1317, which is connected to the first differential gear 1410 to generate a rotational load, is idle due to the termination of the first unidirectional bearing 1310 that is engaged. Becomes A second adjustment gear 1324 configured for speed increase is connected to the first differential gear 1410 to generate a rotational load so that the increased speed rotates the output ring gear 1510 through the second differential gear 1420.

Rotation of the second regulating gear 1324 causes the second unidirectional bearing 1320 to engage when the turbine 1320 reaches +0.4035 to generate a load on the first differential gear 1410. The outer bearing of the second unidirectional bearing 1320 is coupled to the planetary gear 1315, the fixed carrier 1313 and the transmission gear 1322 connected to the second input shaft gear 1140, and the inner bearing is the second adjusting gear 1324. ) Is combined.

Since the number of rotations of the second unidirectional bearing 1320 is set to the number of gears 15 of the second input shaft gear 1140 and the number of gears 45 of the transmission gear 1322, the rotation speed is -0.333, and the rotation thereof is adjusted by the second adjustment. A rotation load is generated in the first differential gear 1410 through the gear 1324.

Specifically, in the case of the transmission apparatus 1000 having the number of gears in FIG. 12, when the turbine rotational speed reaches 0.4035 to 0.6154, the rotation speed of the output ring gear 1510 increases from 0.0495 to 0.2505 rotation.

Here, the output rotation speed is 0 ~ 0.0495 when the first adjustment gear 1317 is in operation, the output rotation speed is 0.0495 ~ 0.2505 when the second adjustment gear 1324 is in operation and outputs the rotation which is increased from the low speed state. Transmitted to gear 1510.

At this time, the first adjusting gear 1317 rotates +0.1635 in idle state (idling state), and the second adjusting gear 1324 makes -0.333 turns.

Next, the high speed state will be described.

FIG. 22 is a diagram illustrating a transmission order of rotational force in the high speed state of FIG. 13, and FIG. 23 is a table relating to a rotation direction of gears in the high speed state of FIG. 22.

The high speed state increases the rotation of the turbine 1230 at a state in which the output ring gear 1510 is rotating at medium speed, starting from 0.6154, the third threshold value, and increasing to 1, such as the power shaft ring gear 1180 and the power carrier 1182. By increasing the rotation of the output ring gear 1510 than the rotation of the medium speed state through the state to reach one revolution.

Here, the power transmission process is the same as the above-described medium speed state, but the second adjusting gear 1324, which is connected to the first differential gear 1410 and generates a rotational load, is idle due to the termination of the second unidirectional bearing 1320. do. The third unidirectional bearing 1330 rotates the output ring gear 1510 at high speed by generating a rotational load on the second differential gear 1420 through the third adjusting gear 1332.

Rotation of the third adjustment gear 1332 causes the third unidirectional bearing 1330 to engage when the turbine 1230 reaches +0.6154 to generate a load on the second differential gear 1420. The outer diameter of the third unidirectional bearing 1330 is connected to the third adjusting gear 1332, and the inner diameter of the third unidirectional bearing 1330 is connected to the bearing connecting member 1150 provided at the rear end of the input shaft 1110. That is, the rotation of the third adjustment gear 1332 is rotated in one rotation equal to the rotation of the input shaft 1110.

At this time, the rotation of the turbine 1230 is gradually increased from 0.6154, which is the highest rotation in the medium speed state, to one rotation. In other words, since the gears cannot rotate even when the turbine rotational speed is equal to the input rotational speed, all the gears revolve only in the form of one fixed shaft about the input shaft 1110.

At this time, the fixed first control shaft gear 1312 is stationary, and all the gears are idle in the + direction.

The transmission device 1000 according to the present embodiment is characterized in that the one-way bearing is used in each step in order to shift in the step of shifting. That is, according to the characteristic of the unidirectional bearing, the shift is performed by being restrained by any one of the first, second, and third bearings, and the restraint by the set rotation speed is automatically canceled, and another bearing is engaged to shift the output ring gear. It can transmit the rotation.

Since all of the components of the transmission apparatus 1000 according to the present invention are not essential, the transmission apparatus 1000 may selectively include all or a part of the above-described components.

In addition, the present invention, various modifications, substitutions and modifications can be made to those skilled in the art without departing from the spirit of the present invention as described above and the accompanying drawings The present invention is not limited thereto, and all or some of the embodiments may be selectively combined to enable various modifications.

Claims

An input shaft provided with a first input shaft gear and a second input shaft gear;

A torque converter unit having a turbine which rotates by converting torque of the input shaft;

An input carrier coupled to the turbine and installed to revolve around the input shaft, the input carrier including a first transmission gear engaged with the first input shaft gear;

A power shaft ring gear meshing with the first transmission gear;

A power carrier connected to the power shaft ring gear and having a first differential gear and a second differential gear meshing with the first differential gear;

An output shaft provided with an output ring gear meshed with the second differential gear;

A fixed carrier fixed to a housing of the torque converter unit and having planetary gears meshing with the second input shaft gear;

A first unidirectional bearing, the outer side of which is fixedly installed to the fixed carrier and the inner side of which is rotatably provided in one direction;

A first adjusting gear fixedly installed inside the first unidirectional bearing and engaged with the first differential gear;

A shift gear in the form of a ring gear engaged with the planetary gear;

A second unidirectional bearing fixed to the transmission gear and having an outer side rotatably provided in one direction;

A second adjusting gear fixedly installed inside the second unidirectional bearing and engaged with the first differential gear;

A third unidirectional bearing having an inner side coupled to the input shaft and the outer side being rotatable only at an input rotational speed lower; And

And a third adjustment gear coupled to the outside of the third unidirectional bearing and engaged with the second differential gear.
The method of claim 1,

When the rotational speed of the turbine relative to the rotational speed of the input shaft is less than or equal to the first threshold value, the rotation and idle of the first transmission gear cancel each other so that the power shaft ring gear is kept at a stop state.

When the rotational speed of the turbine with respect to the rotational speed of the input shaft is less than the first threshold value or less than the second threshold value, the first unidirectional bearing acts as a rotating load so that the output shaft rotates at a first speed ratio relative to the rotational speed of the input shaft. Become,

When the rotational speed of the turbine relative to the rotational speed of the input shaft is greater than or equal to the second threshold value and less than or equal to the third threshold value, the second unidirectional bearing acts as a rotational load such that the output shaft rotates at a second speed ratio relative to the rotational speed of the input shaft. ,

When the rotational speed of the turbine relative to the rotational speed of the input shaft is greater than or equal to a third threshold and less than or equal to a fourth threshold, the third unidirectional bearing acts as a rotational load such that the output shaft rotates at a third speed ratio relative to the rotational speed of the input shaft. Gearshift.
The method of claim 1,

The first differential gear and the second differential gear are shifted by being restrained by any one of the first unidirectional bearing, the second unidirectional bearing, and the third unidirectional bearing according to the rotational speed of the turbine, and set rotation. A transmission device in which the restraint by the number is automatically released and another unidirectional bearing is engaged to transmit the rotation shifted to the output shaft.
The method of claim 1,

And when the rotation speed of the turbine is equal to or less than the first threshold value, rotation and idle of the first transmission gear cancel each other to maintain the power shaft ring gear in a stopped state.
The method of claim 4, wherein

The power shaft ring gear, the first input shaft gear and the first transmission gear are provided with a ratio of the number of gear teeth 3: 1: 1,

And the first threshold is 0.25.
The method of claim 1,

When the rotational speed of the turbine with respect to the rotational speed of the input shaft is less than the first threshold value or less than the second threshold value, the first differential gear receives the rotational load of the first unidirectional bearing and the output ring through the second differential gear. Transmission to rotate gears.
The method of claim 6,

When the rotational speed of the turbine with respect to the rotational speed of the input shaft is greater than or equal to a second threshold value and less than or equal to a third threshold value, the first differential gear receives the rotational load of the second unidirectional bearing and the output ring through the second differential gear. Transmission to rotate gears.
The method of claim 7, wherein

And the second differential gear receives the rotational load of the third unidirectional bearing and rotates the output ring gear when the rotation speed of the turbine with respect to the rotation speed of the input shaft is equal to or greater than a third threshold value or less than a fourth threshold value.
The method of claim 8,

The ratio of the number of gear teeth to the second input shaft gear and the transmission gear is 1: 3,

The first threshold value is 0.25, the second threshold value is 0.4035, the third threshold value is 0.6154, and the fourth threshold value is 1.