WO2011055878A1

WO2011055878A1 - Transmission apparatus using two rotational power sources and a gear assembly

Info

Publication number: WO2011055878A1
Application number: PCT/KR2009/007761
Authority: WO
Inventors: 강성원; 강동헌; 한광희; 조재민
Original assignee: Kang Sung Woon; Kang Dong Hun; Han Kwang Heul; Cho Jae Min
Priority date: 2009-11-09
Filing date: 2009-12-24
Publication date: 2011-05-12
Also published as: KR20090122419A; KR100965101B1

Abstract

The present invention relates to a transmission apparatus using two rotational power sources and a gear assembly, and more particularly, to a transmission apparatus using two rotational power sources and a gear assembly configured with a transmission such that when the rotational speed of a main power source transferred from a driving input shaft is shifted via a gear ratio of a planetary gear unit or a differential gear unit and transferred to driving means, a gear assembly is configured such that at least one or more planetary gear units and at least one or more differential gear units are combined in dual or triple engagement by means of parallel shafts thereof, after which a gear ratio for the rotational speed of a first rotational power source and a gear ratio for the rotational speed of an auxiliary power source are synchronized to an optimum state by means of multiple gear ratios of the gear assembly, such that with minimal input from the first rotational power source, a shifting range for the rotational speed of a driving output shaft at a set rotational speed can be arbitrarily and broadly increased.

Description

Transmission using two rotary power sources and gear combination

The present invention relates to a transmission using two rotational power sources and a gear assembly, and more particularly, a transmission in which the rotational speed of the main power source transmitted from the driving input shaft is shifted to the gear ratio of the planetary gear unit or the differential gear unit and transmitted to the driving means. In the configuration, after the gear assembly consisting of a combination of at least one planetary gear unit and at least one differential gear unit in a double or triple by the parallel between the axes, and then the first rotation by the multiple gear ratio of the gear assembly By arbitrarily combining the speed ratio for the rotational speed of the power source and the speed ratio for the rotational speed of the auxiliary power source, the speed range for the rotational speed of the drive output shaft can be arbitrarily varied at the rotational speed at which the first rotational power source is set as the lowest input. To a transmission using two rotating power sources and a gear combination .

In general, in various industrial sites, the input rotational speed of main motive power is shifted through the gear ratio to the driving shaft in various places such as industrial machines, hoists, conveyors for transferring goods, winches, elevators, and escalators according to the purpose. Various types of stepped transmissions and continuously variable transmissions that transmit a variable speed of output are widely used.

In the case of the stepped transmission in which the output rotational speed must be sequentially shifted at a predetermined interval, the manual transmission and the automatic transmission are widely used for vehicles. When the above stepped transmissions are applied to the vehicle, the efficiency of the engine is increased, but the driver There was a hassle to operate the transmissions according to the situation.

Therefore, without the driver operating the gearbox, high speed transmission efficiency, eliminating the shift shock while driving, and automatically control the gear ratio, improve the fuel efficiency performance and develop the continuously variable gears for automotive and industrial use In the case of the continuously variable transmissions, a separate power transmission means is added to one component of the planetary gear unit having a specific gear ratio, and the belt type continuously variable transmission device according to the power transmission form of the power transmission means. It can be divided into hydraulic continuously variable transmission and gearless continuously variable transmission.

However, in the case of the belt continuously variable transmission, there was a problem in that the transmission range was limited to a certain section due to the limited size of the belt, and the hydraulic continuously variable transmission had a large power due to the shear force of the lubricant due to the rolling contact of the rotor. However, as a separate hydraulic device for controlling the power transmission means is required, various problems such as weight and price increase due to a complicated structure and high fuel consumption exist.

Due to the above problems, recently, various types of transmissions using planetary gear units capable of transmitting large powers with a simple structure using a gearless continuously variable principle have been developed and are known in the art.

In other words, a stepped gearbox or continuously variable transmission using a planetary gear unit consisting of a planetary gear carrier that connects a central sun gear, an outer ring gear, and a planetary gear therebetween as one. It is designed to change the rotational force of the axial rotational shaft by using two of these three elements, consisting of a ring gear and a planetary gear carrier, as input / output shafts and connecting a separate power control mechanism such as a clutch to the other one. .

However, the conventional stepped transmission or continuously variable transmissions using the planetary gear units described above are limited to the designated gear ratios of the respective components of the planetary gear unit (sun gear (S), ring gear (R), planetary gear carrier (C)). As a result of the structure in which the output rotation speed is shifted, the output rotation speed is shifted only within a certain range. Especially, the size of each component is large due to the characteristics of the planetary gear unit composed of a combination of a sun gear and a ring gear planetary gear carrier. Since it is relatively structured to be limited to a certain ratio, the transmission range of the output rotation speed using the gear ratio of each component of the planetary gear unit is hard to exceed the range of 3: 1 ~ 6: 1. In the conventional continuously variable transmission using a single or a plurality of planetary gear units, the speed range of the output rotation speed is extremely limited. It had a fundamental problem.

The first object of the present invention for solving the above problems is to form a gear assembly with an extended gear ratio by a combination of at least one planetary gear unit and at least one differential gear unit and to form a gear assembly. The first rotational power source and the second rotational power source, which are the main power source, are added to each one component of the other gear unit, respectively, to expand the shift range of the output rotational speed of the drive output shaft in various ways. It is to provide a transmission using a rotational power source and a gear assembly.

And the second object of the present invention is to arbitrarily desired rotation of the initial output rotational speed of the drive output shaft from the stop output (0 RPM) by the multi-gear ratio by the combination of the components for each gear unit constituting the gear assembly It is to provide a transmission using two rotational power sources and a gear combination that can be adjusted by number.

The third object of the present invention is the first rotational driving force (P1) and the first auxiliary shaft that is connected to any component of the planetary gear unit or differential gear unit used as the main shaft and the main power source of the engine is transmitted to the drive input rotation of the main shaft When the second rotational driving force (P2) is connected to any one component of the planetary gear unit or the differential gear unit to be used as the auxiliary power source is transmitted to the shift control rotation of the first sub-shaft, the rotational speed of the auxiliary power source is fixed fixed By selecting a variable speed or a variable number of sequential changes, two rotary power sources and gear combinations can be used to expand the use of the transmission, such as a stepped transmission including a speed reducer, an industrial continuously variable transmission, and an automobile continuously variable transmission. To provide a transmission.

The fourth object of the present invention is that the planetary gear unit of each gear assembly or each component of the differential gear unit can arbitrarily expand the transmission range of the output rotation speed by each gear ratio by the engagement of different gears having a constant gear ratio. The present invention provides a continuously variable transmission using two rotary power sources and a gear assembly.

The fifth object of the present invention is that any one gear unit used as the first sub-shaft when the two gear units of the gear assembly due to the combination of at least one planetary gear unit and at least one differential gear unit is three rows or more is doubled. It is to provide a transmission using two rotational power sources and a gear combination that can be implemented as a brake.

It will be described in more detail the means for achieving the above object.

Gear combination of the transmission using the two rotational driving force and the gear combination according to the present invention

Each component for at least one planetary gear unit 110 (110 ') (110 ″) [sun gear (S) (S') (S ″), ring gear (R) (R ') (R ″ ), Planetary gear carriers (C) (C ') (C ″)] are planetary gear combinations in which the

planetary gear units

110, 110' and 110 ″ are combined in parallel so as to be parallel to each other by gear meshing. 100 and 100 ';

Each component for at least one differential gear unit (210) (210 ') (210 ") (differential A-axis (DA) (DA') (DA"), differential B-axis (DB) (DB ') (DB ″), pinion gear housings (DP) (DP ′) (DP ″)] are formed by combining each differential gear unit 210 (210 ') (210 ″) in parallel to each other by means of gears. Differential gear assembly 200 (200 ');

Each component for at least one planetary gear unit 110 (110 ') (110 ″) [sun gear (S) (S') (S ″), ring gear (R) (R ') (R ″) , Planetary gear carrier (C) (C ') (C ″)] and each component for the at least one differential gear unit (210) (210') (210 ″) [differential A-axis (DA) (DA ') ) (DA ″), differential B-axis (DB) (DB ′) (DB ″), pinion gear housing (DP) (DP ′) (DP ″)] by at least one planetary gear unit 110 due to gear teeth. 110 '(110') and at least one differential gear unit (210) (210 ', 210') are combined to form a composite gear assembly 300 (300 ') in parallel to each other parallel to each other It is composed of separation.

In addition, the rotational driving force P of the transmission using the two rotational driving force and the gear combination according to the present invention is a ratio of the gear ratio of any one gear unit of the first rotational driving force P1 and the gear assembly (A) serving as the main power source of the engine. It is composed of a second rotational driving force (P2) to be a secondary power source to control, the first rotational driving force (P1) is the first fixed power source (FP1) and the first variable power source (1) that the rotational speed is sequentially changed VP1), and the second rotational driving force P2 is divided into a second fixed power source FP2 whose rotational speed is always constant and a second variable power source VP2 whose rotational speed is sequentially changed.

The planetary gear assembly (100) (100 ') of the present invention comprises at least one planetary gear unit (110) (110') (110 ") is composed of a parallel combination by parallel between each other, two planets The planetary gear assembly 100, which is a parallel combination of the gear units 110 and 110 ', has any component of the planetary gear unit 110 used as the main shaft 10 (sun gear S, ring gear). (R) and planetary gear carrier (C) as the drive input rotation part 11, and other components (sun gear (S), ring gear (R), planetary gear carrier (C)) are drive rotation control rotation parts. (12), and any other component (sun gear (S), ring gear (R), planetary gear carrier (C)) is constituted by the drive output rotating part (13) and used as the first sub-shaft (20). One component of the other planetary gear unit 110 '(sun gear S', ring gear R ', planetary gear carrier C') to the first rotating shaft 21 of the first shaft 20 And another one. The small [sun gear (S ′), ring gear (R ′), planetary gear carrier (C ′) are the first sub-axis (20) shift control rotation part (22), and any other component [sun gear (S ′). ), The ring gear (R '), the planetary gear carrier (C') is composed of the output rotation part 23 of the first sub-shaft, the first rotation driving force (P1) to the drive input rotation part 11 of the main shaft (10) The first rotational driving force P1 is applied to the input of the first sub-shaft 20, the first rotational driving force P1 to the engagement of the main shaft 10, the input rotational portion 11 and the

different gears

14A and 14B having a constant gear ratio. The shift control rotation part 22 of the first sub-shaft 20 is coupled to the second rotational driving force P2 to which the auxiliary power source is transmitted and the gears of

different gears

14C and 14K having a constant gear ratio. The output rotation part 23 of the first subshaft 20 has a structure in which the control rotation part 12 for driving shift of the main shaft 10 is engaged with a gear of

different gears

14E and 14D having a constant gear ratio. It is.

And another planetary gear assembly (100 ') of the present invention in a three-row column is another planetary gear unit (110 ″) used as a second sub-axis 30 in the two-plane planetary gear assembly 100 in parallel to each other axis In parallel with each other, and any component of the other planetary gear unit 110 ″ used as the second auxiliary shaft 30 (sun gear S ″, ring gear R ″, planetary gear carrier C ″). ] Is the input rotation part 31 of the 2nd sub-shaft 30, and another component (sun gear S ", ring gear R", and planetary gear carrier C ") is the 2nd sub-axis 30. As shown in FIG. Of the output control part 33 of the second sub-shaft 30 by using any of the other components (sun gear S ″, ring gear R ″, planetary gear carrier C ″). ), Wherein the input rotation part 31 of the second sub shaft 30 has

different gears

14A, 14B, 14G, 14G 'having a constant gear ratio from the main shaft 10 driving input rotation part 11. ), The first rotational driving force (P1) And the second rotation driving force P2 is applied to the shift control rotation part 32 of the second subshaft 30 by engagement of different gears 14C 'and 14K' having a constant gear ratio. The output rotation part 33 of the two sub-shafts 30 is coupled to the shift control rotation part 22 of the first sub-shaft 20 by the engagement of different gears 14J and 14H having a constant gear ratio and operated by a sensor. A separate clutch means 34 is added.

In the transmission using two rotational driving force and the gear combination according to the present invention, the first rotational driving force P1 of the first fixed power source FP1 and the first variable power source VP1 is the planetary gear coupling body 100. (100 ') and the differential gear assembly (200) (200') and any one of the gear unit constituting any one of the gear combination (300) of the composite gear assembly (300) (300 '), The second rotational driving force P2 of any one of the second stationary power source FP2 and the second variable power source VP2 is connected to the first rotational driving force P1 of the gear assembly A. It is combined with either component.

The differential gear assembly (200) (200 ') of the present invention comprises at least one differential gear unit (210) (210') (210 ") is composed of a parallel combination by parallel between each other, two differential The differential gear assembly 200 in parallel combination by the interaxial parallelism of the gear units 210 and 210 'is a component of the differential gear unit 210 which is used as the main shaft 40 (differential A-axis ( DA), differential B axis (DB), pinion gear housing (DP)] as the drive input rotation part 41 of the main shaft 40, and other components (differential A axis DA, differential B axis DB). , The pinion gear housing (DP)] as the control rotation part 42 for the drive shift of the main shaft 40, and any other components (differential A-axis (DA), differential B-axis (DB), pinion gear housing ( DP)] as the drive output rotation part 43 of the main shaft 40, and any component of the other differential gear unit 210 'used as the first sub-shaft 50 (differential A-axis DA'). , Differential B-axis (DB ′), pinion The housing DP 'as the input rotation part 51 of the first sub-shaft 50, and the other components (differential A-axis DA', differential B-axis DB ', and pinion gear housing DP'). ) As the shift control rotation part 52 of the first sub-shaft 50, and any other component (differential A-axis DA ', differential B-axis DB', pinion gear housing DP '). Is composed of an output rotation part 53 of the first sub-shaft 50, the first rotation driving force (P1) is applied to the drive input rotation part 41 of the main shaft 40, the input rotation part ( 51, a first rotational driving force P1 is applied by engagement of the main shaft 40 driving input rotational portion 41 with

different gears

44A and 44B having a constant gear ratio. The shift control rotation part 52 is coupled by the engagement of the second rotation driving force P2 to which the auxiliary power source is transmitted and the different gears 44C and 44K having a constant gear ratio, and the output rotation part of the first subshaft 50. Reference numeral 53 is a drive shift agent of the main shaft 40 The engagement of different gear (44E) (44D) having a constant gear ratio and the rotation unit 42 is a combined structure.

In addition, another differential gear assembly 200 'of the present invention in three rows has another differential gear unit 210 ″ used as the second sub-axis 60 in the two-gear differential gear assembly 200 in parallel to each other. As a parallel combination of the components of another differential gear unit 210 ″ (differential A axis DA ″, differential B axis DB ″, pinion gear housing) DP ″)] as the input rotation part 61 of the second sub-axis 60, and the other components (differential A-axis DA ″, differential B-axis DB ", pinion gear housing DP "). The shift control rotation part 62 of the 2nd sub-shaft 60 is used, and the other components (differential A-axis DA ", differential B-axis DB", and pinion gear housing DP ") are made into 2nd. Comprising an output rotation portion 63 of the sub-shaft 60, the input rotation portion 61 of the second sub-shaft 60 has a different gear 44A having a constant gear ratio from the main shaft 40 drive input rotation portion 41 (44B) by the engagement of (44G) (44G ') The first rotational driving force P1 is applied, and the second rotational driving force P2 is applied to the shift control rotation part 62 of the second sub-shaft 60 by engagement of different gears 44C 'and 44K' having a constant gear ratio. ) Is coupled to the output rotation part 63 of the second sub-shaft 60 by engagement of the gear shift control rotation part 52 of the first sub-shaft 50 with different gears 44J and 44H having a constant gear ratio. And a separate clutch means 64 which is operated by a sensor is added.

The composite gear assembly (300) (300 ') of the present invention is at least one planetary gear unit (110) (110') (110 ") and at least one differential gear unit (210) (210 ') (210) ″) Are composed of parallel combinations of parallel to each other, and the two-column composite gear assembly 300 includes each component of the planetary gear unit 110, which is used as the main shaft 70 (sun gear). S), ring gear (R), planetary gear carrier (C)] or one component of any differential gear unit 210 (differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)) ] As the drive input rotation part 71 of the main shaft 70, and the other components (sun gear S, ring gear R, planetary gear carrier C, or differential A axis DA, differential B axis). (DB), pinion gear housing (DP)] as the control rotation part 72 for the drive shift of the main shaft 70, and any other component (sun gear (S), ring gear (R), planetary gear carrier ( C) or differential A axis (DA), differential B axis (DB), pinion Housing (DP)] as the drive output rotation part 73 of the main shaft 70, and the other of the planetary gear unit 110 'or the differential gear unit 210' of the first sub-axis 80 is used. Either component (sun gear (S '), ring gear (R'), planetary gear carrier (C ') or differential A-axis (DA'), differential B-axis (DB '), pinion gear housing (DP') ] Is the input rotation part 81 of the 1st sub-shaft 80, and has another component (sun gear S ', ring gear R', planetary gear carrier C ', or differential A-axis DA'). ), Differential B-axis (DB '), pinion gear housing (DP') as the shift control rotation part 82 of the first sub-shaft 80, and any other component (sun gear (S '), ring gear (R '), planetary gear carrier (C'), differential A-axis (DA '), differential B-axis (DB'), pinion gear housing (DP '), and the output rotation part 83 of the first sub-shaft 80. A first rotation driving force (P1) is applied to the driving input rotation part (71) of the main shaft (70) and the input of the first sub shaft (80). The first rotational driving force P1 is imparted to the entirety 81 by the engagement of the main shaft 70, the input rotational portion 71 and the

different gears

74A and 74B having a constant gear ratio, and the first minor shaft 80. The shift control rotation unit 82 of the second rotational driving force (P2) to which the auxiliary power source is transmitted is coupled by the engagement of the different gears 74C (74K) having a constant gear ratio, the output of the first auxiliary shaft 80 The rotating portion 83 is configured to be coupled to the drive gear control rotation portion 72 of the main shaft 70 and the gears of

different gears

74E and 74D having a constant gear ratio.

And another compound gear assembly (300 ') of the present invention in three rows is another planetary gear unit (110 ") or differential gear unit that is used as the second sub-axis 90 in the two-gear composite gear assembly (300) ( 210 ″) is a parallel combination by parallel to each other, and any component of the other planetary gear unit 110 ″ or the differential gear unit 210 ″ used as the second sub-axis 90 (sun gear S ″). ), Ring gear (R ″), planetary gear carrier (C ″), or differential A axis (DA ″), differential B axis (DB ″), pinion gear housing (DP ″)] The input rotation part 91 is used to form another component (sun gear S ″, ring gear R ″, planetary gear carrier C ″, or differential A axis DA ″, differential B axis DB "). And pinion gear housing DP ″ as the shift control rotation part 92 of the second sub-shaft 90, and any other component (sun gear S ″, ring gear R ″, planetary gear carrier ( C ″), or differential A axis (DA ″), differential B axis (DB ″), pinion Housing DP "] as an output rotation part 93 of the second sub-shaft 90, and the input rotation part 91 of the second sub-shaft 90 from the main shaft 70 driving input rotation part 71. The first rotational driving force P1 is applied by the engagement of

different gears

74A, 74B, 74G, 74G 'having a constant gear ratio, and the shift control rotation part 92 of the second sub-shaft 90 is provided. The second rotational driving force P2 is applied by the engagement of the different gears 74C 'and 74K' with a constant gear ratio, and the first sub-shaft 80 is attached to the output rotational portion 93 of the second sub-axis 90. It is coupled to the gear of the shift control rotation 82 and the gears of the different gears 74C (74H) having a constant gear ratio and has a structure in which a separate clutch means 94 is operated by the sensor is added.

The present invention as described above is not limited to the reduction ratio of any one unit of the gear combination, there is an advantage that can implement a wide variety of transmission range up to a low speed range and a high speed range, according to various embodiments of the gear assembly By making it possible to easily realize a large reduction ratio with a simple structure, the field of application has a very large effect that can be applied to various types of transmissions including a gear reducer and also for automobile and industrial use.

In particular, in the case of a vehicle transmission, the engine power is transferred to the gear assembly to maximize the engine efficiency in the power transmission process, thereby reducing fuel costs, and having a simple structure, the compactness of the gear assembly that can realize a very large reduction ratio can be produced. As a result, the manufacturing cost can be significantly reduced, and thus the economic effect is very great.

[Revision under Rule 91 02.02.2010]
1,2,3 are constituting the gear assembly of the present invention

Each embodiment showing the coupling relationship of each planetary gear assembly

[Revision under Rule 91 02.02.2010]
4, 5 and 6 are constituting the gear assembly of the present invention

Each embodiment showing the coupling relationship of each differential gear assembly

[Revision under Rule 91 02.02.2010]
7, 8, 9 and 10 constitute a gear assembly of the present invention.

Each embodiment showing the coupling relationship of each compound gear assembly

[Revision under Rule 91 02.02.2010]
11, 12 and 13 constitute a gear assembly of the present invention.

Each other embodiment showing the coupling relationship of each compound gear assembly

A: Gear Combination

100,100 ′: Planetary gear assembly 110,110′110 ″: Planetary gear unit

200,200 ′: Differential gear assembly 210,210′210 ″: Differential gear unit

300,300 ′: Complex gear assembly

10,40,70:

Spindle

20,50,80: First Shaft

11, 41, 71: drive

input rotation part

21, 51, 81: input rotation part of the first sub-shaft

12, 42, 72: shift

control rotation part

22, 52, 82: shift control rotation part of the first sub-shaft

13,43,73:

output rotation part

23,53,83: output rotation part of the first sub-shaft

14,44,74

Gear

34,64,94 Clutch means

30,60,90: Second Shaft

31, 61, 91: input rotation part of the second sub-shaft 32, 62, 92: shift control rotation part of the

second sub-shaft

33, 63, 93: output rotation part of the second sub-shaft

On the basis of the accompanying drawings an embodiment of the present invention showing the configuration and effects as described above will be described in more detail.

<유성기어결합체(100)(100′)와 2개의 회전 원동력을 이용한 변속장치의 실시예><Example of the transmission using planetary gear assembly 100 (100 ') and two rotational driving forces>

1 is a cross-sectional view showing a coupling relationship according to the first embodiment of the present invention comprising a planetary gear assembly (100) coupled to a two-plane planetary gear unit (110) (110 '). 2 is a cross-sectional view showing a coupling relationship according to the second embodiment of the planetary gear assembly 100 of the present invention, Figure 3 is a three-row planetary gear unit (110) (110 ') of the gear assembly (A) Fig. 1 is a cross sectional view showing a coupling relationship according to the third embodiment of the planetary gear assembly 100 'coupled to (110 ″).

First, as shown in FIG. 1, the coupling relationship between two rotational driving forces consisting of the planetary gear assembly 100 according to the first embodiment of the present invention and the transmission device using the planetary gear assembly 100 will be described.

After setting the following conditions [Table 1] as a prerequisite for explaining the shifting process according to the first embodiment using the planetary gear assembly 100 of the present invention, the shifting process of the output rotational speed for the vehicle was examined. .

Table 1

The sun gear S of the planetary gear unit 110 of the main shaft 10 drives the main shaft 10 through which the first variable power source VP1, in which the rotation speed of the first rotational power source P1 is varied, is transmitted through the main shaft 10. It is used as the input rotation part 11 and is coupled with the gear 14A having a constant gear ratio, and the planetary gear carrier C is used as the shift control rotation part 12 of the main shaft 10, and the outer peripheral surface has a constant gear ratio with gears. It is coupled to the gear 14E, the ring gear (R) is used as the output rotation portion 13 of the main shaft (10).

In addition, the planetary gear carrier C ′ of the planetary gear unit 110 ′ of the first subshaft 20 is used as the driving input rotation part 21 of the first subshaft 20, and the gear 14B has a gear ratio with a constant outer circumferential surface. ), The sun gear S 'is the first sub-shaft 20 while receiving a second fixed power source FP2 having a constant rotational speed of the second rotary power source P2 by the engagement of the

different gears

14C and 14K. It is used as the shift control rotation part 22 of, and the ring gear (R ') is used as the output rotation part 23 of the first sub-shaft 20 is coupled to the gear 14D having a constant gear ratio.

Here, the drive input rotation part 11 of the planetary gear unit 110 of the main shaft 10 may have different gears 14A having a constant gear ratio with the input rotation part 21 of the planetary gear unit 110 ′ of the first subshaft 20. 14B are coupled to each other, and the shift control rotation part 12 of the planetary gear unit 110 of the main shaft 10 and the output rotation part 23 of the planetary gear unit 110 ′ of the first sub shaft 20 are connected to each other. The gears are engaged by the engagement of

different gears

14E and 14D with a constant gear ratio.

At this time, the rotation ratio of each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft (10) planetary gear unit 110 and the first sub-axis (20) planetary gear unit (110 ') After the rotation ratio of each component (sun gear S ', ring gear R', planetary gear carrier C ') is set to 5: 1: 1, the drive input rotation part of the main shaft 10 The gear 14A built into the gear 11 and the gear 14B built into the input rotation part 21 of the first sub-shaft 20 have a gear ratio of 1: 5 and the sun gear of the first planetary gear unit 110. (S) and the gear ratio of the second planetary gear unit (110 ') to the planetary gear carrier (C') is set to 5: 1, and built up in the shift control rotation part 12 of the main shaft (10). 14E) and the gear 14D arranged on the output rotation part 23 of the first subshaft 20 have a gear ratio of 1: 1, and the planetary gear carrier C and the first gear 10 of the planetary gear unit 100 of the main shaft 10 are formed. 1 shaft 20 of the planetary gear unit 100 'with respect to the ring gear R' It was set at 1: 1 ratio.

Also, after setting the rotation speed of the second fixed power source FP2 to 1,400 RPM, the initial minimum input rotation speed of the first variable power source VP1 transmitted to the drive input rotation part 11 of the main shaft 10 is 4,000 at 700 RPM. As a result of varying the RPM, as shown in the following [Table 2], the amount of change in the number of revolutions appearing in the output rotating part 13 of the main shaft 10 was obtained from the speed change from '0' RPM to '1,320' RPM.

That is, the speed change apparatus according to the first embodiment of the present invention has an input rotational speed by a combination of gears in which at least one planetary gear unit (110) (110 ') is in parallel with each other so that the components are parallel to each other. It is possible to arbitrarily extend the shift range of the output rotational speed with respect to.

At this time, not limited to the above-described setting example of the present invention, if the structure of the coupling form, the number of revolutions of P2, each gear ratio is changed arbitrarily, the speed ratio corresponding to the corresponding combination conditions will appear, so as not to depart from the technical spirit of the present invention Of course, it can be variously performed within the range.

TABLE 2

※ Example of speed conversion (RPM)

Component	RPM (RPM)
14A	700	800	900	1000	1500	2000	2500	3000	3500	4000
14B	140	160	180	200	300	400	500	600	700	800
14K	1400	1400	1400	1400	1400	1400	1400	1400	1400	1400
14D	140	120	100	80	-20	-120	-220	-320	-420	-520
14E
	140	160	180	200	300	400	500	600	700	800
13	0	40	80	120	320	560	720	920	1120	1320

Component 14E in Table 2 shows the theoretical value of the rotation ratio of each planetary gear unit 110 with respect to the input rotation unit 11.

Next, as shown in Figure 2, after setting the prerequisites for explaining the shifting process according to the second embodiment using the planetary gear assembly 100 of the present invention as shown in Table 3 below, the output rotation speed We looked at the shifting process of.

TABLE 3

The sun gear S ′ of the planetary gear unit 110 ′ of the first subshaft 20 is used as an input rotation part 21 of the first subshaft 20 and is coupled with a gear 14B having a constant gear ratio. The gear carrier C ′ has a first sub-shaft 20 while receiving a second fixed power source FP2 having a constant rotational speed of the second rotary power source P2 by engagement of

gears

14C and 14K having different outer circumferential surfaces. It is used as the shift control rotation part 22 of, and the ring gear (R ') is used as the output rotation part 23 of the first sub-shaft 20 is coupled to the gear 14D having a constant gear ratio.

different gears

14E and 14D with a constant gear ratio.

At this time, the rotation ratio of each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft (10) planetary gear unit 110 and the first sub-axis (20) planetary gear unit (110 ') After the rotation ratio of each component (sun gear S ', ring gear R', planetary gear carrier C ') is set to 5: 1: 1, the drive input rotation part of the main shaft 10 The gear 14A built into the gear 11 and the gear 14B built into the input rotating part 21 of the first sub-shaft 20 have a gear ratio of 1.5: 1 and the planetary gear unit 100 of the main shaft 10. The rotation ratio of the sun gear S and the first sub shaft 20 to the sun gear S 'of the planetary gear unit 100' is set to 1: 1.5, and the shaft is installed in the shift control rotation part 12 of the main shaft 10. The gear 14D arranged in the gear 14E and the output rotation part 23 of the first subshaft 20 has a gear ratio of 1: 1 and a planetary gear carrier of the planetary gear unit 100 of the main shaft 10. (C) and the first gear shaft 20 to the ring gear R 'of the planetary gear unit 100'. It was set at 1: 1 ratio to one.

Also, after setting the rotation speed of the second fixed power source FP2 to 70 RPM, the initial minimum input rotation speed of the first variable power source VP1 transmitted to the driving input rotation part 11 of the main shaft 10 is 4,000 RPM from 700 RPM. As a result of varying until the change in the number of revolutions appearing in the output rotation portion 13 of the main shaft 10 as shown in the following [Table 4] obtained a result of shifting from '0' RPM to '330' RPM.

Table 4

※ Example of speed conversion (RPM)

Component	RPM (RPM)
14A	700	800	900	1000	1500	2000	2500	3000	3500	4000
14B	1050	1200	1350	1500	2250	3000	3750	4500	5250	6000
14K	70	70	70	70	70	70	70	70	70	70
14D	140	170	200	230	380	530	680	830	980	1130
14E	140	160	180	200	300	400	500	600	700	800
13	0	10	20	30	80	130	180	230	280	330

Component 14E in Table 4 shows the theoretical value of the rotation ratio of each planetary gear unit 110 with respect to the input rotation unit 11.

That is, the speed change apparatus according to the second embodiment of the present invention has an input rotation speed in parallel combination by engagement of gears such that each component of at least one planetary gear unit 110 (110 ') is parallel to each other. It is possible to arbitrarily extend the shift range of the output rotational speed with respect to.

The second embodiment is also not limited to the above-described setting example, and when the structure of the coupling type, the rotational speed and the gear ratio of the gears are arbitrarily changed, the gear ratio corresponding to the corresponding combination condition will appear, so as not to depart from the technical spirit of the present invention. Of course, it can be variously performed as long as it does not.

Next, as shown in Figure 3, after setting the prerequisites for explaining the shifting process according to the third embodiment using the planetary gear assembly 100 'of the present invention as shown in Table 5, the output rotation We looked at the number shifting process.

Table 5

The sun gear S ′ of the planetary gear unit 110 ′ of the first sub-shaft 20 is used as the input rotation part 21 of the first sub-shaft 20 and is coupled with the

gears

14B and 14G having a constant gear ratio. The planetary gear carrier C ′ is used as the shift control rotation part 22 of the first sub-shaft 20, and the outer circumferential surface thereof is coupled with the gear 14J having a constant gear ratio, and the ring gear R ′ is It is used as the output rotation part 23 of the first sub-shaft 20 is coupled to the gear 14D having a constant gear ratio.

Meanwhile, the sun gear S ″ of the planetary gear unit 110 ″ of the second subshaft 30 is used as the input rotation part 31 of the second subshaft 30 and is coupled with a gear 14G ′ having a constant gear ratio. The planetary gear carrier C ″ receives a second fixed power source FP2 having a constant rotational speed of the second rotational power source P2 by the engagement of the gears 14C ′ and 14K ′ having different outer circumferential surfaces. Used as the shift control rotation part 32 of the sub-shaft 30, the ring gear (R ") is used as the output rotation part 33 of the second sub-shaft 30, coupled to the gear 14H having a constant gear ratio and the sensor There is a separate clutch means 34 which is operated by.

different gears

14E and 14D with a constant gear ratio.

The input rotation part 21 of the planetary gear unit 110 ′ of the first subshaft 20 has different gears 14G having a constant gear ratio with the input rotation part 31 of the planetary gear unit 110 ″ of the second subshaft 30. 14G 'coupled to each other, and the shift control rotation part 22 of the first subshaft 20 and the planetary gear unit 110' has an output rotation part of the planetary gear unit 110 "of the second subshaft 30. 33) is engaged by the engagement of different gears 14J and 14H with a constant gear ratio.

At this time, the rotation ratio of each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft (10) planetary gear unit 110 and the first sub-axis (20) planetary gear unit (110 ') Rotation ratio of each component (sun gear S ', ring gear R', planetary gear carrier C ') and each component of the planetary gear unit 110 "of the second auxiliary shaft 30 (sun gear S ″), planetary gear carrier C ″ and ring gear R ″] are all set to 4: 1: 1, and the gears are built up in the drive input rotation part 11 of the main shaft 10. 14A, 14B, 14G geared to the input rotation part 21 of the 14th shaft and the

1st subshaft

20, and 14G and 14G geared to the input rotation part 31 of the 2nd subshaft 30. ) 14G ′ is a gear ratio of 1: 1 to 1: 1 and the sun gear S of the planetary gear unit 110 of the main shaft 10 and the sun gear S ′ of the planetary gear unit 110 ′ of the first sub-shaft 20. ) And the rotation ratio of the sunshaft gear unit S ″ of the second subshaft 30 planetary gear unit 110 ″ to both 1: 1: 1. The gear 14D built in the shift control rotation part 12 of the main shaft 10 and the gear 14D built in the output rotation part 23 of the first subshaft 20 have a gear ratio of 1: 1. The gear 14H built on the shift control rotation part 22 of the first subshaft 20 and the gear 14H built on the output rotation part 33 of the second subshaft 30 have a gear ratio of 1: 1. Set to.

Further, after setting the rotational speed of the second fixed power source FP2 rotating in the same direction as the rotation of the input rotation unit sun gear S ″ of the second subshaft 30 planetary gear unit 110 ″, the main shaft 10 As a result of varying the initial minimum input rotation speed of the first variable power source (VP1) transmitted to the drive input rotation unit 11 of from 700 RPM to 4,000 RPM, as shown in Table 6 below, the output rotation unit 13 of the main shaft 10 ), The amount of change in the rotational speed changes from '0' RPM to '825' RPM.

Table 6

※ Example of speed conversion (RPM)

Component	RPM (RPM)
14A	700	800	900	1000	1500	2000	2500	3000	3500	4000
14B	700	800	900	1000	1500	2000	2500	3000	3500	4000
14G ′	700	800	900	1000	1500	2000	2500	3000	3500	4000
14K ′	175	175	175	175	175	175	175	175	175	175
14C ′	175	200	225	250	375	500	625	750	875	1000
14H	0	25	50	75	200	325	450	575	700	825
14J	0	25	50	75	200	325	450	575	700	825
14D	175	175	175	175	175	175	175	175	175	175
14E	175	200	225	250	375	500	625	750	875	1000
13	0	25	50	75	200	325	450	575	700	825

In Table 6, the

elements

14E and 14C 'represent the theoretical values of the rotation ratios of the planetary gear units 110 and 110' with respect to the

input rotation parts

11 and 31.

That is, in the transmission device according to the third embodiment of the present invention, the combination of the gears in which at least three

planetary gear units

110, 110 'and 110 " Therefore, the shift range of the output rotational speed with respect to the input rotational speed can be arbitrarily extended.

On the other hand, the clutch 34 which is added to the output rotation part 33 of the second sub-shaft 30 at the time of sudden braking or stopping due to the sudden situation due to the non-operation and the foot brake abnormality of the second rotational power source P2 used as the auxiliary power source is By controlling the rotation of the second sub-shaft output unit by the sense operation under the above condition, the control rotary unit 22 of the first sub-shaft is controlled to operate the output rotation unit 13 at the combined rotation ratio of the main shaft 10 and the first sub-shaft 20. Induces an automatic engine brake by inducing 0 rpm or arbitrary low speed rotation, and at the same time, electrical functions of various operation devices connected to the output rotating part 13 of the main shaft 10 by the operation of the main rotational power source P1 are effective. In case of industrial use, the output is stopped to secure secondary accident prevention and safety.

The present invention has been described in the above embodiment, but can be carried out in various ways in combination with the structural change of the coupling form, gear engagement ratio, rotation ratio of P2, etc. within the scope not departing from the technical spirit of the present invention. Of course.

<차동기어결합체(200)(200′)와 2개의 회전 원동력을 이용한 변속장치의 실시예><Embodiment of Transmission Device Using Differential Gear Combination Body 200 (200 ') and Two Rotational Driving Forces>

4 is a cross-sectional view showing a coupling relationship according to the fourth embodiment in which the gear assembly (A) of the present invention comprises a differential gear assembly (200) coupled with two rows of differential gear units (210, 210 '), 5 is a cross-sectional view illustrating a coupling relationship according to a fifth embodiment of the differential gear assembly 200 according to the present invention, and FIG. 6 is a three-gear differential gear unit 210 (210 ') of the gear assembly (a). Fig. 1 is a cross sectional view showing a coupling relationship according to the sixth embodiment of the differential gear coupling body 200 'coupled to (210 ″).

First, as shown in FIG. 4, the coupling relationship between two rotational driving forces including the differential gear assembly 200 according to the fourth embodiment of the present invention and the transmission using the differential gear assembly 200 will be described.

After setting the following conditions [Table 7] as a prerequisite for explaining the shifting process according to the fourth embodiment using the differential gear assembly 200 of the present invention, the shifting speed of the output rotation speed was examined.

TABLE 7

The differential A-axis DA of the differential gear unit 210 has a main shaft 40 through which the first variable power source VP1, in which the rotation speed of the first rotational power source P1 is varied, is transmitted through the main shaft 40. It is used as a drive input rotation part 41 of the coupled gear 44A having a constant gear ratio, the pinion gear housing (DP) is used as a shift control rotation part 42 of the main shaft 40 while having a constant gear ratio ( 44E), the differential B-axis (DB) is used as the output rotation portion 43 of the main shaft (40).

The differential A axis DA ′ of the differential gear unit 210 ′ of the first subshaft 50 is used as an input rotation part 51 of the first subshaft 50 and is coupled with a gear 44B having a constant gear ratio. , The pinion gear housing DP ′ receives the second fixed power source FP2 having a constant rotational speed of the second rotational power source P2 by the engagement of the different gears 44C and 44K. Used as the shift control rotation part 52, the differential B-axis (DB ') is used as the output rotation part 53 of the first sub-shaft 50 is coupled to the gear 44D having a constant gear ratio.

Here, the driving input rotation part 41 of the differential gear unit 210 of the main shaft 40 has a different gear 44A having a constant gear ratio with the input rotation part 51 of the differential gear unit 210 'of the first subshaft 50. (44B) are coupled to each other, and the shift control rotation part 42 of the main shaft 40 differential gear unit 210 and the output rotation part 53 of the first sub-shaft 50 differential gear unit 210 '. The gears are engaged by the engagement of

different gears

44E and 44D with a constant gear ratio.

At this time, the rotation ratio of each component (differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)) of each differential gear unit (210) (210 ') [pinion gear housing (DP) × 2 = differential A axis (DA) + differential B axis (DB)], and then the gears 44A and the first subshaft 50 built in the drive input rotation part 41 of the main shaft 40 are rotated. The gear 44B built in the input rotation part 51 has a gear ratio of 1: 1 and the differential A axis DA of the differential gear unit 210 of the main shaft 40 and the differential gear unit 210 of the first subshaft 50. ′) Is set to a ratio of 1: 1 to the differential A axis DA ′ and the outputs of the gear 44E and the first subshaft 50 built in the shift control rotation part 42 of the main shaft 40. The gear 44D built in the rotary part 53 has a gear ratio of 1: 1 and the differential B-axis (DB) and the first sub-shaft 50 of the differential gear unit 210 of the main shaft 40 and the differential gear unit 210 '. The rotation ratio for the pinion gear housing (DP ′) is set to 1: 1.

Also, after setting the rotation speed of the second fixed power source FP2 to 175 RPM, the initial minimum input rotation speed of the first variable power source VP1 transmitted to the driving input rotation part 41 of the main shaft 40 is set at 700 RPM to 4,000 RPM. As a result of varying the result, the variation in the number of revolutions appearing in the output rotation part 43 of the main shaft 40 is shifted from '0' RPM to '3,300' RPM as shown in Table 8 below.

Table 8

※ Example of speed conversion (RPM)

Component	RPM (RPM)
44A	700	800	900	1000	1500	2000	2500	3000	3500	4000
44B	700	800	900	1000	1500	2000	2500	3000	3500	4000
44 K	175	175	175	175	175	175	175	175	175	175
44D	350	450	550	650	1150	1650	2150	2650	3150	3650
44E	350	400	450	500	750	1000	1250	1500	1750	2000
43	0	100	200	300	800	1300	1800	2300	2800	3300

In Table 8, the component 44E represents the theoretical value of the rotation ratio of each differential gear unit 210 with respect to the input rotation part 41.

That is, the speed change apparatus according to the fourth embodiment of the present invention has an input rotational speed by a combination of gears such that at least one of the components of at least one differential gear unit (210) (210 ') is parallel to each other. It is possible to arbitrarily extend the shift range of the output rotational speed with respect to.

At this time, not limited to the setting example of the present invention, if the structure of the coupling form and the number of revolutions of the P2, each gear ratio is changed arbitrarily, the speed ratio corresponding to the corresponding combination conditions will appear, so as not to depart from the technical spirit of the present invention Of course, it can be variously performed within the range.

Next, as shown in Figure 5, after setting the following conditions [Table 9] as a prerequisite for explaining the shifting process according to the fifth embodiment using the differential gear assembly 200 of the present invention, the output rotation speed We looked at the shifting process of.

Table 9

The pinion gear housing DP ′ of the differential gear unit 210 ′ of the first subshaft 50 is used as an input rotation part 51 of the first subshaft 50 and is coupled with a gear 44B having a constant gear ratio. , The differential A-axis DA ′ receives the second fixed power source FP2 having a constant rotational speed of the second rotary power source P2 by the engagement of the different gears 44C and 44K. Used as the shift control rotation part 52, the differential B-axis (DB ') is used as the output rotation part 53 of the first sub-shaft 50 is coupled to the gear 44D having a constant gear ratio.

different gears

44E and 44D with a constant gear ratio.

At this time, the rotation ratio of each component (differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)) of each differential gear unit 210 [Pinion gear housing (DP) × 2 = differential A Axis DA + differential B axis DB], and then the input rotation part 51 of the gear 44A and the first subshaft 50 built in the drive input rotation part 41 of the main shaft 40. The gear 44B built in the shaft) has a gear ratio of 1: 2, and the pinion of the differential A-axis DA of the differential gear unit 210 of the main shaft 40 and the differential gear unit 210 'of the first sub-shaft 50 is formed. The rotation ratio with respect to the gear housing DP 'is set to 2: 1, and the gear 44E and the output rotation part 53 of the first subshaft 50 which are built up in the shift control rotation part 42 of the main shaft 40 are shown. The gear 44D built in the gearbox has a gear ratio of 1: 1. The differential B of the pinion gear housing DP of the differential gear unit 210 of the main shaft 40 and the differential gear unit 210 'of the first sub-shaft 50 is fixed. The rotation ratio with respect to the axis DB 'was set to 1: 1.

Also, after setting the rotation speed of the second fixed power source FP2 to 350 RPM, the initial minimum input rotation speed of the first variable power source VP1 transmitted to the drive input rotation part 41 of the main shaft 40 is from 4,000 RPM to 700 RPM. As a result of varying until the change in the number of revolutions appearing in the output rotation part 43 of the main shaft 40, as shown in the following [Table 10] was obtained to shift from '0' RPM to '3,300' RPM.

Table 10

※ Example of speed conversion (RPM)

Component	RPM (RPM)
44A	700	800	900	1000	1500	2000	2500	3000	3500	4000
44B	350	400	450	500	750	1000	1250	1500	1750	2000
44 K	350	350	350	350	350	350	350	350	350	350
44D	350	450	550	650	1150	1650	2150	2650	3150	3650
44E	350	400	450	500	750	1000	1250	1500	1750	2000
43	0	100	200	300	800	1300	1800	2300	2800	3300

In Table 10, the component 44E represents the theoretical value of the rotation ratio of each differential gear unit 210 with respect to the input rotation part 41.

That is, the transmission device according to the fifth embodiment of the present invention has an input rotational speed by a combination of gears such that at least one of the components of at least one differential gear unit (210) (210 ') are parallel to each other. It is possible to arbitrarily extend the shift range of the output rotational speed with respect to.

Next, as shown in Figure 6, after setting the prerequisites for explaining the shifting process according to the sixth embodiment using the differential gear assembly 200 'of the present invention as shown in Table 11, the output rotation We looked at the number shifting process.

Table 11

The differential A axis DA ′ of the differential gear unit 210 ′ of the first subshaft 50 is used as an input rotation part 51 of the first subshaft 50 and is coupled with a gear 44B having a constant gear ratio. , The differential B-axis DB ′ is used as the shift control rotation part 52 of the first sub-shaft 50 and is coupled to the gear 44J having a constant gear ratio, and the pinion gear housing DP ′ is connected to the first sub-shaft ( 50 is used as the output rotation portion 53 is coupled to the gear 44D having a constant gear ratio.

Meanwhile, the differential A-axis DA ″ of the differential gear unit 210 ″ of the second sub-shaft 60 is used as the input rotation part 61 of the second sub-shaft 60 and is coupled with a gear 44G ′ having a constant gear ratio. The pinion gear housing DP ″ receives a second fixed power source FP2 while receiving a second fixed power source FP2 having a constant rotational speed of the second rotational power source P2 by engagement of different gears 44C ′ and 44K ′. 60 is used as the shift control rotation part 62, and the differential B axis DB ″ is used as the output rotation part 63 of the second sub-shaft 60, and is coupled with the gear 44H having a constant gear ratio and connected to the sensor. There is a separate clutch means 64 which is actuated by.

different gears

44E and 44D with a constant gear ratio.

The input rotation part 51 of the differential gear unit 210 'of the first subshaft 50 has a different gear 44G having a constant gear ratio with the input rotation part 61 of the differential gear unit 210 ″ of the second subshaft 60. And the shift control rotation part 52 of the first subshaft 50 and the differential gear unit 210 'of the first subshaft 50, and the output rotation part of the differential gear unit 210 " 53 and a combination of different gears 44J and 44H having a constant gear ratio.

At this time, the rotation ratio of the components (differential A-axis DA, differential B-axis DB, pinion gear housing DP) of the main gear 40 differential gear unit 210 and the first sub-shaft 50 differential gear unit Rotation ratio of each component (differential A-axis DA ', differential B-axis DB', pinion gear housing DP ') of the second sub-axis 60 and the differential gear unit 210 " Rotation ratio for each component [Differential A-axis (DA ″), Differential B-axis (DB ″), Pinion gear housing (DP ″)] [Pinion gear housing (DP) × 2 = Differential A-axis (DA) + Differential B-axis (DB)], and then the gear 44A and the input rotation part 51 of the first sub-shaft 50 are installed on the drive input rotation part 41 of the main shaft 40. The gears 44B 'and 44G' installed in the input rotation part 61 of the second sub-shaft 60 have a gear ratio of 1: 1: 1, and the differential shaft unit 210 of the main shaft 40 has a gear ratio of 1: 1. Differential A-axis DA and the first sub-axis 50 and differential A-axis DA 'and the second sub-axis 60 of the differential gear unit 210' The gear ratio 44E and the gears installed in the shift control rotation part 42 of the main shaft 40 are all set at a rotation ratio of the gear unit 210 ″ with respect to the differential A axis DA ″. The gear 44D built in the output rotation part 53 of the first subshaft 50 sets the gear ratio to 1: 1, and the gear 44J built in the shift control rotation part 52 of the first subshaft 50. ) And the gear 44H built in the output rotation part 63 of the second subshaft 60 set the gear ratio to 1: 1.

In addition, after setting the rotation speed of the second fixed power source FP2 rotating in the same direction as the rotation of the differential A-axis DA ″ of the second sub-axis 60 differential gear unit 210 ″ to 350 RPM, the main shaft ( As a result of varying the initial minimum input rotational speed of the first variable power source (VP1) transmitted to the drive input rotation unit 41 of the 40 from 700RPM to 3,500RPM, as shown in Table 12, the output rotation unit of the main shaft 40 ( The variation in the number of revolutions shown in (43) was shifted from '0' RPM to '2,800' RPM.

Table 12

※ Example of speed conversion (RPM)

Component	RPM (RPM)
44A	700	800	900	1000	1500	2000	2500	3000	3500
44B	700	800	900	1000	1500	2000	2500	3000	3500
44G ′	700	800	900	1000	1500	2000	2500	3000	3500
44C ′	350	400	450	500	750	1000	1250	1500	1750
44K ′	350	350	350	350	350	350	350	350	350
44H	0	100	200	300	800	1300	1800	2300	2800
44D	350	400	450	500	750	1000	1250	1500	1750
44E	350	400	450	500	750	1000	1250	1500	1750
43	0	100	200	300	800	1300	1800	2300	2800

In Table 12, the components 44E, 44C ', and 44D represent the rotational ratios of the respective

differential gear units

210, 210', and 210 "with respect to the respective

input rotation parts

41, 61, and 51. Theoretical values are shown.

That is, in the transmission device according to the sixth embodiment of the present invention, at least three or more

differential gear units

210, 210 ', 210 " are combined in parallel to each other so that the components of the gears are parallel to each other. Therefore, the shift range of the output rotational speed with respect to the input rotational speed can be arbitrarily extended.

On the other hand, the clutch 64 added to the output rotation part 63 of the second sub-shaft 60 when the second braking power source P2 used as an auxiliary power source is not operated and the braking or stopping suddenly due to an abnormal foot brake or a sudden situation is provided. Under the above conditions, the output rotation part 43 is controlled at the combined rotation ratio of the main shaft 40 and the first sub shaft 50 by controlling the control rotation part 52 of the first sub shaft by cutting off the rotation of the output portion of the second sub shaft by the sense operation. Induces the rotation of 0rpm or any low speed to serve as an automatic engine brake, and at the same time the electrical function of the various operating devices connected to the output rotating portion 43 of the main shaft 40 by the operation of the main rotary power source (P1) When it is valid and industrial, the output is stopped to secure secondary accident prevention and safety.

At this time, not limited to the above-described setting example of the present invention, if the structure of the coupling form, the number of revolutions of the P2, each gear ratio is changed arbitrarily, the speed ratio corresponding to the corresponding combination conditions will appear, so as not to deviate from the technical spirit of the present invention Of course, it can be variously performed in the inside.

<복합기어결합체(300)(300′)와 2개의 회전 원동력을 이용한 변속장치의 실시예><Embodiment of Transmission Device Using Composite Gear Combination Body 300 (300 ') and Two Rotational Driving Forces>

7 is a combination of any one of the planetary gear units 110 used as the main shaft 70 and the differential gear unit 210 'used as the first sub-shaft 80 is coupled to the gear assembly (a) of the present invention. 8 is a cross-sectional view showing a coupling relationship according to the seventh embodiment of the gear coupling body 300, Figure 8 is a coupling cross-sectional view showing a coupling relationship according to the eighth embodiment of the composite gear coupling body 300 of the present invention. 9 is made of a composite gear assembly 300 having any one differential gear unit 210 used as the main shaft 70 and one planetary gear unit 110 'used as the first sub-axis 80 coupled thereto. 9 is a cross-sectional view showing a coupling relationship according to the ninth embodiment, Figure 10 is a coupling cross-sectional view showing a coupling relationship according to a tenth embodiment of the composite gear coupling 300 of the present invention.

First, as shown in FIG. 7, the coupling relationship between two rotational driving forces consisting of the compound gear assembly 300 according to the seventh embodiment of the present invention and the transmission using the compound gear assembly 300 will be described.

After setting the following conditions [Table 13] as a prerequisite for explaining the shifting process according to the seventh embodiment using the composite gear assembly 300 of the present invention, the shifting speed of the output rotation speed was examined.

Table 13

The sun gear S of the planetary gear unit 110 of the main shaft 70 drives the main shaft 70 through which the first variable power source VP1, in which the rotation speed of the first rotational power source P1 is varied, is transmitted through the main shaft 70. It is used as the input rotation unit 71 and is coupled to the gear 74A having a constant gear ratio, the planetary gear carrier (C) is used as the shift control rotation unit 72 of the main shaft 70, the gear 74E having a constant gear ratio It is coupled with, the ring gear (R) is used as the output rotation portion 73 of the main shaft (70).

The differential A-axis DA ′ of the differential gear unit 210 ′ of the first sub-shaft 80 is used as an input rotation part 81 of the first sub-shaft 80 and is coupled with a gear 74B having a constant gear ratio. The pinion gear housing DP ′ receives the first sub-axis while receiving a second fixed power source FP2 having a constant rotational speed of the second rotational power source P2 by engagement of

different gears

74C and 74K having a constant gear ratio. 80 is used as the shift control rotation part 82, the differential B-axis (DB ') is used as the output rotation portion 83 of the first sub-shaft 80 is coupled to the gear 74D having a constant gear ratio.

Here, the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 has a different gear 74A having a constant gear ratio with the input rotation part 81 of the differential gear unit 210 'of the first sub-axis 80. Coupled to each other by 74B, the shift control rotation unit 72 of the planetary gear unit 110 of the main shaft 70 and the output rotation unit 83 of the differential gear unit 210 'of the first sub-axis 80 are formed. The gears are engaged by the engagement of

different gears

74E and 74D with a constant gear ratio.

At this time, the rotation ratio of each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft 70 planetary gear unit 110 is set to 5: 1: 1 and the first sub-shaft (80) The rotation ratio of each component of the differential gear unit 210 '(differential A-axis DA', differential B-axis DB ', pinion gear housing DP') is determined by [pinion gear housing DP '. 2 = differential A-axis DA '+ differential B-axis DB', and thereafter, the gear 74A and the first sub-shaft built in the drive input rotation part 71 of the main shaft 70 are formed. The gear 74B built in the input rotation part 81 of the 80 has a gear ratio of 1: 1, and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the differential gear unit of the first sub-shaft 80. The gear ratio 74E and the first subshaft 80, which are set in the speed change control rotation part 72 of the main shaft 70, are set at a rotation ratio of the differential A axis DA 'of 210' to 1: 1. The gear 74D built in the output rotation part 83 of the main shaft 70 has a gear ratio of 1: 1.4. The rotation rate of the planetary gear carrier of the control unit (100), (C) and a first minor axis 80 'of the differential axis B (DB differential gear unit 210 ") of 1.4: 1 was set to.

In addition, after setting the rotational speed of the second fixed power source FP2 that rotates in the same direction as the rotation of the input rotation part differential A-axis DA 'of the first auxiliary shaft 80 differential gear unit 210' to 300 RPM, the main shaft ( As a result of varying the initial minimum input rotational speed of the first variable power source (VP1) transmitted to the drive input rotation unit 71 of the 70 from 700RPM to 4,000RPM, as shown in Table 14, the output rotation unit of the main shaft 70 ( The change in rotation speed shown in 73) is shifted from '0' RPM to '3,960' RPM.

Table 14

※ Example of speed conversion

Component	RPM (RPM)
74A	700	800	900	1000	1500	2000	2500	3000	3500	4000
74B	700	800	900	1000	1500	2000	2500	3000	3500	4000
74K	300	300	300	300	300	300	300	300	300	300
74D	140	200	300	400	900	1400	1900	2400	2900	3400
74E	140	160	180	200	300	400	500	600	700	800
73	0	120	240	360	960	1560	2160	2760	3360	3960

In Table 14, the component 74E represents the theoretical value of the rotation ratio of the planetary gear unit 110 with respect to the input rotation unit 71.

That is, the transmission device according to the seventh embodiment of the present invention, each component of any one planetary gear unit 110 used as the main shaft 70, and any one differential gear used as the first sub-axis (80) Parallel combinations of gears that allow the components of the unit 210 'to be in parallel with each other are parallel to each other, thereby allowing the speed range of the output rotational speed to the input rotational speed to be arbitrarily expanded.

At this time, not limited to the above-described setting example of the present invention, if the structure of the coupling form and the number of rotations other than the P2, each gear ratio arbitrarily changed so that the speed ratio corresponding to the corresponding combination conditions appear, without departing from the technical spirit of the present invention Of course, it can be variously performed within the range.

Next, as shown in Figure 8, after setting the following conditions [Table 15] as a prerequisite for explaining the shifting process according to the eighth embodiment using the composite gear assembly 300 of the present invention, the output rotation speed We looked at the shifting process of.

Table 15

The pinion gear housing DP ′ of the differential gear unit 210 ′ of the first sub-shaft 80 is used as an input rotation part 81 of the first sub-shaft 80 and is coupled with a gear 74B having a constant gear ratio. The differential A-axis DA ′ receives the first sub-shaft (FP2) while receiving a second fixed power source FP2 having a constant rotational speed of the second rotational power source P2 by engagement of

different gears

74E and 74D with a constant gear ratio.

At this time, the rotation ratio of each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft 70 planetary gear unit 110 is set to 5: 1: 1 and the first sub-shaft (80) The rotation ratio of each component of the differential gear unit 210 '(differential A-axis DA', differential B-axis DB ', pinion gear housing DP') is determined by [pinion gear housing DP '. 2 = differential A-axis DA '+ differential B-axis DB', and thereafter, the gear 74A and the first sub-shaft built in the drive input rotation part 71 of the main shaft 70 are formed. The gear 74B built in the input rotation part 81 of the 80 has a gear ratio of 1: 5, and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the differential gear unit 1 of the first sub-shaft 80. 210 ') of the pinion gear housing DP' is set to 5: 1, and the gear 74E and the first sub-shaft 80 of the gear control shaft 72 of the main shaft 70 are installed. The gear 74D built in the output rotation part 83 has a gear ratio of 1: 1.4. 70, the rotation ratio of 1.4 for the planetary gear carrier (C) and a first minor axis 80 'of the differential axis B (DB differential gear unit 210 ") of the planetary gear unit (100) was set to one.

In addition, after setting the rotational speed of the second fixed power source FP2 rotating in the opposite direction to the rotation of the input rotational portion pinion gear housing DP 'of the first sub-axis 80 of the differential gear unit 210', the main shaft ( As a result of varying the initial minimum input rotational speed of the first variable power source VP1 transmitted to the drive input rotation unit 71 of the 70 from 700 RPM to 4,000 RPM, as shown in Table 16, the output rotation unit of the main shaft 70 ( The change in rotation speed shown in 73) is shifted from '0' RPM to '1,188' RPM.

Table 16

※ Example of speed conversion

Component	RPM (RPM)
74A	700	800	900	1000	1500	2000	2500	3000	3500	4000
74B	140	160	180	200	300	400	500	600	700	800
74K	180	180	180	180	180	180	180	180	180	180
74D	100	140	180	220	420	620	820	1020	1220	1420
74E	140	160	180	200	300	400	500	600	700	800
73	0	36	72	108	288	468	648	828	1008	1188

In Table 16, the component 74E represents the theoretical value of the rotation ratio of the planetary gear unit 110 with respect to the input rotation unit 71.

That is, the transmission device according to the eighth embodiment of the present invention, each component of any one planetary gear unit 110 used as the main shaft 70, and any one differential gear used as the first sub-shaft 80 Parallel combinations of gears that allow the components of the unit 210 'to be in parallel with each other are parallel to each other, thereby allowing the speed range of the output rotational speed to the input rotational speed to be arbitrarily expanded.

At this time, it is not limited to the above-described setting example of the present invention, and if the gear ratio of the coupling type and the number of P2 and the gear ratio are changed arbitrarily, the gear ratio will be shown to meet the corresponding combination conditions. Of course, it can be variously performed within the range.

Next, as shown in Figure 9, after setting the following conditions [Table 17] to set the prerequisites for explaining the shifting process according to the ninth embodiment using the composite gear assembly 300 of the present invention, the output rotation speed We looked at the shifting process of.

Table 17

The differential A-axis DA of the differential gear unit 210 has a main shaft 70 through which the first variable power source VP1, in which the rotation speed of the first rotational power source P1 is varied, is transmitted through the main shaft 70. It is used as a drive input rotation part 71 of the gear is coupled to the gear (74A) having a constant gear ratio, the pinion gear housing (DP) is used as a shift control rotation part 72 of the main shaft 70 while having a constant gear ratio ( 74E), the differential B-axis (DB) is used as the output rotation portion 73 of the main shaft (70).

The sun gear S ′ of the planetary gear unit 110 ′ of the first sub-shaft 80 is used as an input rotation part 81 of the first sub-shaft 80 and is coupled with a gear 74B having a constant gear ratio. The carrier C ′ receives the first fixed shaft 80 while receiving a second fixed power source FP2 having a constant rotational speed of the second rotary power source P2 by engagement of

different gears

74C and 74K having a constant gear ratio. It is used as the shift control rotation part 82 of, the ring gear (R ') is used as the output rotation part 83 of the first sub-shaft 80 is coupled to the gear (74D) having a constant gear ratio.

Here, the driving input rotation part 71 of the differential gear unit 210 of the main shaft 70 has a different gear 74A having a constant gear ratio with the input rotation part 81 of the planetary gear unit 110 ′ of the first sub shaft 80. Coupled to each other by 74B, the shift control rotation part 72 of the main gear 70 differential gear unit 210 is coupled to the output rotation part 83 of the planetary gear unit 110 'of the first sub-axis 80. The gears are engaged by the engagement of

different gears

74E and 74D with a constant gear ratio.

At this time, the rotation ratio of each component (differential A-axis DA, differential B-axis DB, pinion gear housing DP) of the main gear 70 differential gear unit 210 [pinion gear housing (DP) × 2 = Differential A-axis (DA) + differential B-axis (DB)] and each component of the first sub-axis 80 planetary gear unit 110 '(sun gear S', ring gear R '). , And the rotation ratio of the planetary gear carrier C ′] is set to 5: 1: 1, and then the gear 74A and the first subshaft 80 of the gear 74A built in the driving input rotation part 71 of the main shaft 70 are rotated. The gear 74B built into the planetary gear unit 110 'input rotation part 81 has a gear ratio of 1: 1, and the differential A axis DA and the first sub shaft of the differential gear unit 210 of the main shaft 70 are formed. 80) The rotation ratio of the planetary gear unit 110 'to the sun gear S' is set to 1: 1, and the gear 74E and the first subshaft which are built up in the shift control rotation part 72 of the main shaft 70 are rotated. (80) The gear 74D built in the planetary gear unit 110 'output rotation part 83 is a gear. 1: 1, the rotation ratio of the pinion gear housing DP of the main shaft 70 differential gear unit 210 and the ring gear R ′ of the planetary gear unit 110 'of the first sub-axis 80 is 1:: Set to 1.

In addition, after setting the rotation speed of the second fixed power source (FP2) that rotates in the opposite direction to the rotation of the input gear sun gear (S ') of the first sub-axis 80 planetary gear unit (110'), the main shaft 70 As a result of varying the initial minimum input rotational speed of the first variable power source (VP1) transmitted to the drive input rotation unit 71 of from 700RPM to 4,000RPM as shown in [Table 18], the output rotation unit 73 of the main shaft 70 The variation in the number of revolutions shown in the results is shifted from '0' RPM to '1,980' RPM.

Table 18

※ Example of speed conversion

Component	RPM (RPM)
74A	700	800	900	1000	1500	2000	2500	3000	3500	4000
74B	700	800	900	1000	1500	2000	2500	3000	3500	4000
74K	210	210	210	210	210	210	210	210	210	210
74D	350	370	390	410	510	610	710	810	910	1010
74E	350	400	450	500	750	1000	1250	1500	1750	2000
73	0	60	120	180	480	780	1080	1380	1680	1980

In Table 18, the component 74E represents the theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation unit 71.

That is, the transmission device according to the ninth embodiment of the present invention, each of the components of any one differential gear unit 210 used as the main shaft 70, and any one planetary gear used as the first sub-axis (80) Parallel combination by engagement of the gears to make each component of the unit 110 'parallel to each other is able to arbitrarily expand the range of shift of the output rotational speed with respect to the input rotational speed.

Next, as shown in Figure 10, after setting the following conditions [Table 19] as a prerequisite for explaining the shifting process according to the tenth embodiment using the composite gear assembly 300 of the present invention, the output rotation speed We looked at the shifting process of.

Table 19

The sun gear S ′ of the planetary gear unit 110 ′ of the first sub-axis 80 is used as an input rotation part 81 of the planetary gear unit 110 ′ of the first sub-shaft 80 and has a constant gear ratio 74B. And the ring gear R 'receives a second fixed power source FP2 having a constant rotational speed of the second rotating power source P2 by engagement of

different gears

74C and 74K having a constant gear ratio. It is used as the shift control rotation part 82 of the first sub-axis 80, the planetary gear unit 110 ', the planetary gear carrier (C') is the output rotation portion 83 of the first sub-axis 80, the planetary gear unit 110 '. It is combined with the gear 74D having a constant gear ratio.

different gears

74E and 74D with a constant gear ratio.

At this time, the rotation ratio of each component (differential A-axis DA, differential B-axis DB, pinion gear housing DP) of the main gear 70 differential gear unit 210 [pinion gear housing (DP) × 2 = Differential A-axis (DA) + differential B-axis (DB)] and each component of the first sub-axis 80 planetary gear unit 110 '(sun gear S', ring gear R '). , And the rotation ratio of the planetary gear carrier C ′] is set to 5: 1: 1, and then the gear 74A and the first subshaft 80 of the gear 74A built in the driving input rotation part 71 of the main shaft 70 are rotated. The gear 74B built in the drive input rotation part 81 has a gear ratio of 1: 1 and the differential A axis DA of the differential gear unit 210 of the main shaft 70 and the planetary gear unit of the first sub-axis 80 ( 110 ') and the rotation ratio of the sun gear (S') to 1: 1, the gear 74E and the first sub-axis (80) planetary gear unit built in the shift control rotation portion 72 of the main shaft (70) The gear 74D built in the output rotation part 83 of 110 'has a gear ratio of 1: 1. The rotation ratio of the pinion gear housing DP of the main gear 70 differential gear unit 210 and the planetary gear carrier C ′ of the planetary gear unit 110 'of the first sub-shaft 80 was set to 1: 1. .

In addition, after setting the rotational speed of the second fixed power source (FP2) to rotate in the same direction as the rotation of the input gear sun gear (S ') of the first sub-axis 80 planetary gear unit 110', the main shaft 70 As a result of varying the initial minimum input rotational speed of the first variable power source (VP1) transmitted to the drive input rotation unit 71 of from 700RPM to 3,500RPM as shown in [Table 20], the output rotation unit 73 of the main shaft 70 The variation in the number of revolutions shown in the results is changed from '0' RPM to '1,680' RPM.

Table 20

※ Example of speed conversion

Component	RPM (RPM)
74A	700	800	900	1000	1500	2000	2500	3000	3500
74B	700	800	900	1000	1500	2000	2500	3000	3500
74C	210	210	210	210	210	210	210	210	210
74K	210	210	210	210	210	210	210	210	210
74D	350	370	390	410	510	610	710	810	910
74E	350	400	450	500	750	1000	1250	1500	1750
73	0	60	120	180	480	780	1080	1380	1680

In Table 20, the component 74E represents the theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation unit 71.

That is, the transmission device according to the tenth embodiment of the present invention, each of the components of any one differential gear unit 210 used as the main shaft 70, and any one planetary gear used as the first sub-shaft 80 Parallel combination by engagement of the gears to make each component of the unit 110 'parallel to each other is able to arbitrarily expand the range of shift of the output rotational speed with respect to the input rotational speed.

Next, as shown in Figure 11, after setting the prerequisites for explaining the shifting process according to the eleventh embodiment using the composite gear assembly 300 'of the present invention as shown in Table 21, the output rotation We looked at the number shifting process.

Table 21

The differential A axis DA ′ of the differential gear unit 210 ′ of the first subshaft 80 is used as an input rotation part 81 of the first subshaft 80 and has a

gear ratio

74B and 74G having a constant gear ratio. The pinion gear housing DP ′ is coupled to the gear 74J having a constant gear ratio while being used as the shift control rotation part 82 of the first subshaft 80, and the differential B axis DB ′ It is used as the output rotation portion 83 of the one sub-shaft 80 is coupled to the gear 74D having a constant gear ratio.

Meanwhile, the differential A-axis DA ″ of the differential gear unit 210 ″ of the second sub-axis 90 is used as an input rotation part 91 of the second sub-axis 90 and is coupled with a gear 74G ′ having a constant gear ratio. The pinion gear housing DP ″ receives a second fixed power source FP2 having a constant rotational speed of the second rotational power source P2 by engagement of different gears 74C ′ and 74K ′. 90 is used as the shift control rotation part 92, and the differential B-axis DB ″ is used as the output rotation part 93 of the second sub-shaft 90, and is coupled with a gear 74H having a constant gear ratio to the sensor. There is a separate clutch means 94 that is actuated by.

different gears

74E and 74D with a constant gear ratio.

The input rotation part 81 of the differential gear unit 210 'of the first sub-shaft 80 has a different gear 74G having a constant gear ratio with the input rotation part 91 of the differential gear unit 210 ″ of the second sub-shaft 90. And the shift control rotation part 82 of the first sub-axis 80 and the differential gear unit 210 'of the first sub-axis 80, and the output rotation part of the differential gear unit 210 " 93 is engaged by engagement of different gears 74J and 74H with a constant gear ratio.

At this time, the rotation ratio of each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft 70 planetary gear unit 110 is set to 6: 1: 1 and the first sub-shaft ( 80) Rotation ratio of each component (differential A-axis DA ', differential B-axis DB', pinion gear housing DP ') of the differential gear unit 210' and the second differential gear unit 210 ". Rotation ratio for each component of [Differential A-axis (DA ″), Differential B-axis (DB ″), Pinion gear housing (DP ″)] [Pinion gear housing (DP) × 2 = Differential A-axis (DA) ) + Differential B-axis (DB)], and then the gear 74A and the input rotation part 81 of the first sub-shaft 80 are installed in the drive input rotation part 71 of the main shaft 70. The gear ratio of the gear 74B is set to 1: 6, and the gear 74A and the second subshaft 90 differential gear unit 210 ″ built in the drive input rotation part 71 of the main shaft 70. The gear ratio of the gear 74G ′ built in the input rotation part 91 of The rotation ratio of the sun gear S of the planetary gear unit 110 of the main shaft 70 and the differential A axis DA ′ of the differential gear unit 210 'of the first sub-axis 80 is set to 6: 1, (70) The rotation ratio of the sun gear S of the planetary gear unit 110 and the differential A-axis DA ″ of the differential gear unit 210 ″ of the second sub-shaft 90 is set to 1: 1.4, and the main shaft ( The gear 74E built in the speed change control rotating part 72 of 70 and the gear 74D built in the output rotating part 83 of the first subshaft 80 set the gear ratio to 1: 1. The gear 74H built in the shift control rotation part 82 of the first sub-shaft 80 and the gear 74H built in the output rotation part 93 of the second sub-shaft 90 set the gear ratio to 1: 1. .

In addition, after setting the rotational speed of the second fixed power source FP2 rotating in the same direction as the rotation of the differential A-axis DA ″ of the second auxiliary shaft 90 differential gear unit 210 ″ to 490 RPM, the main shaft ( As a result of varying the initial minimum input rotational speed of the first variable power source (VP1) transmitted to the drive input rotation unit 71 of 70) from 700 RPM to 4,000 RPM, as shown in Table 22 below, the output rotation unit of the main shaft 70 The change in rotation speed shown in (73) is shifted from '0' RPM to '7,906.8' RPM.

Table 22

※ Example of speed conversion (RPM)

Component	RPM (RPM)
74A	700	800	900	1000	1500	2000	2500	3000	3500	4000
74B	116.6	133.3	150	166.6	250	333.3	416.6	500	583.3	666.6
74G ′	980	1120	1260	1400	2100	2800	3500	4200	4900	5600
74K ′	490	490	490	490	490	490	490	490	490	490
74H	0	140	280	420	1120	1820	2520	3220	3920	4620
74D	116.6	146.7	410	673.4	1990	3306.7	4623.4	5940	7256.7	8573.4
74E	116.6	133.3	150	166.6	250	333.3	416.6	500	583.3	666.6
73	0	13.4	260	506.8	1740	2973.4	4206.8	5440	6673.4	7906.8

In Table 22, the component 74E represents a theoretical value of the rotation ratio of the planetary gear unit 110 with respect to the input rotation unit 71.

That is, in the transmission apparatus according to the eleventh embodiment of the present invention, each component of any one planetary gear unit 110 used as the main shaft 70 and any one first used as the first sub-axis 80 is provided. The parallel rotation by the combination of the gears which make the components of the second differential gear unit 210 ″ used as the differential gear unit 210 'and the second sub-axis 90 to be parallel to each other is applied to the input rotational speed. It is possible to arbitrarily expand the transmission range of the output rotation speed with respect to.

On the other hand, the clutch 94 added to the output rotation part 63 of the second sub-shaft 91 at the time of non-operation of the second rotational power source P2 used as an auxiliary power source and sudden braking or stopping due to abnormal foot brake or sudden situation is Under the above condition, the output rotating part is controlled at the combined rotation ratio of the main shaft 70 and the first subshaft 80 by controlling the control rotating part 82 of the first subshaft by cutting off the rotation of the output part of the second subshaft 90 by the sense operation. At 73 rpm for an arbitrary low speed rotation to serve as an automatic engine brake, and at the same time for the various operating devices connected to the output rotation part 73 of the main shaft 70 by the operation of the main rotary power source (P1). The electrical function becomes effective, and in industrial use, the output is stopped to secure secondary accident prevention and safety.

Next, as shown in Figure 12, after setting the prerequisites for explaining the shifting process according to the twelfth embodiment using the composite gear assembly 300 'of the present invention as shown in Table 23, the output rotation We looked at the number shifting process.

Table 23

gear ratio

Meanwhile, the pinion gear housing DP ″ of the differential gear unit 210 ″ of the second sub-shaft 90 is used as an input rotation part 91 of the second sub-shaft 90 and is coupled with a gear 74G ′ having a constant gear ratio. The differential A-axis DA ″ receives a second fixed power source FP2 with a constant rotation speed of the second rotary power source P2 due to the engagement of the different gears 74C ′ and 74K ′. 90 is used as the shift control rotation part 92, and the differential B-axis DB ″ is used as the output rotation part 93 of the second sub-shaft 90, and is coupled with a gear 74H having a constant gear ratio to the sensor. There is a separate clutch means 94 that is actuated by.

different gears

74E and 74D with a constant gear ratio.

At this time, the rotation ratio of each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft 70 planetary gear unit 110 is set to 6: 1: 1 and the first sub-shaft ( 80) Rotation ratio of each component of the differential gear unit 210 '(differential A-axis DA', differential B-axis DB ', pinion gear housing DP') and the second sub-axis 90 differential gear unit [Pinion gear housing (DP) × 2 = differential for all components of (210 ″) [differential A axis (DA ″), differential B axis (DB ″), pinion gear housing (DP ″)] A-axis (DA) + differential-B-axis (DB)], and the input rotation portion (74A) and the first sub-shaft (80A) of the gears and the first sub-shaft (80) built in the drive input rotation portion 71 of the main shaft (70) The gear 74B and the

gear

74G and 74G 'built in the input rotation part 91 of the second subshaft 90 and the gear 74B built in 81 are both set at a gear ratio of 6: 1: 1. The sun gear S of the planetary gear unit 110 and the differential A-axis DA ′ and the second of the differential gear unit 210 'of the first sub-axis 80 and the second sub-axis 80. The gear ratio of the shaft 90 to the pinion gear housing DP ″ of the differential gear unit 210 ″ is set to 6: 1: 1, and is built up in the shift control rotation part 72 of the main shaft 70. 74E) and the gear 74D built in the output rotation part 83 of the 1st subshaft 80 set the gear ratio to 1: 1, and are built in the gear shift control rotation part 82 of the said 1st subshaft 80. The gears 74H built on the output gears 93 of the second gear shaft 90 and the second gear 74J set the gear ratio to 1: 1.

In addition, after setting the rotational speed of the second fixed power source FP2 to rotate in the same direction as the rotation of the input pinion gear housing DP ″ of the second sub-axis 90 differential gear unit 210 ″ to 232.2 RPM, the main shaft As a result of varying the initial minimum input rotational speed of the first variable power source (VP1) transmitted to the drive input rotation unit 71 of the 70 from 700RPM to 4,000RPM as shown in Table 24 below, the output of the main shaft 70 The amount of change in the number of revolutions appearing in the rotating unit 73 was obtained to shift from '0' RPM to '2,200' RPM.

Table 24

※ Example of speed conversion (RPM)

Component	RPM (RPM)
74A	700	800	900	1000	1500	2000	2500	3000	3500	4000
74B	116.6	133.3	150	166.6	250	333.3	416.6	500	583.3	666.6
74G ′	116.6	133.3	150	166.6	250	333.3	416.6	500	583.3	666.6
74K ′	233.2	233.2	233.2	233.2	233.2	233.2	233.2	233.2	233.2	233.2
74H	0	33.4	66.8	100.2	266.8	433.4	600	766.8	933.4	1100
74D	116.6	200.1	283.6	367	783.6	1199.9	1616.6	2033.6	2450.1	2866.6
74E	116.6	133.3	150	166.6	250	333.3	416.6	500	583.3	666.6
73	0	66.8	133.6	200.4	533.6	866.6	1200	1533.6	1866.8	2200

Component 74E in Table 24 shows the theoretical value of the rotation ratio of the planetary gear unit 110 to the input rotation unit 71.

That is, the transmission device according to the twelfth embodiment of the present invention, each component of any one planetary gear unit 110 used as the main shaft 70, and any one differential gear used as the first sub-axis (80) Output rotational speed with respect to the input rotational speed by the combination of the gears which make the components of the differential gear unit 210 ″ used as the unit 210 'and the second sub-axis 90 parallel to each other. Will be able to arbitrarily expand the transmission range of.

On the other hand, the clutch 94 added to the output rotation part 63 of the second sub-shaft 90 when the second rotational power source P2, which is used as an auxiliary power source, is not operated and the brake is suddenly stopped or stopped due to abnormal foot brakes. Under the above condition, the output rotating part is controlled at the combined rotation ratio of the main shaft 70 and the first subshaft 80 by controlling the control rotating part 82 of the first subshaft by cutting off the rotation of the output part of the second subshaft 90 by the sense operation. At 73 rpm for an arbitrary low speed rotation to serve as an automatic engine brake, and at the same time for the various operating devices connected to the output rotation part 73 of the main shaft 70 by the operation of the main rotary power source (P1). The electrical function becomes effective, and in industrial use, the output is stopped to secure secondary accident prevention and safety.

Next, as shown in FIG. 13, after setting the following conditions [Table 25] as a prerequisite for explaining the shifting process according to the thirteenth embodiment using the composite gear assembly 300 'of the present invention, the output rotation We looked at the number shifting process.

Table 25

In addition, the sun gear S ′ of the planetary gear unit 110 ′ of the first sub-shaft 80 is used as an input rotation part 81 of the first sub-shaft 80 and is coupled with the

gears

74B and 74G having a constant gear ratio. The planetary gear carrier C ′ is used as the shift control rotation part 82 of the first sub-shaft 80, and the outer circumferential surface thereof is coupled to the gear 74J having a constant gear ratio, and the ring gear R ′ is It is used as the output rotation part 83 of the first sub-shaft 80 and is coupled to the gear 74D having a constant gear ratio.

Here, the drive input rotation part 71 of the planetary gear unit 110 of the main shaft 70 has a different gear 74A having a constant gear ratio with the input rotation part 81 of the planetary gear unit 110 ′ of the first subshaft 80. Coupled to each other by 74B, the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 and the output rotation part 83 of the planetary gear unit 110 'of the first sub-axis 80 are formed. The gears are engaged by the engagement of

different gears

74E and 74D with a constant gear ratio.

The input rotation part 81 of the planetary gear unit 110 ′ of the first subshaft 80 has a different gear 74G having a constant gear ratio from the input rotation part 91 of the differential gear unit 210 ″ of the second subshaft 90. And the shift control rotation part 82 of the first subshaft 80 and the planetary gear unit 110 'of the first subshaft 80 and the output rotation part of the differential gear unit 210 ″ of the second subshaft 90. 93 is engaged by engagement of different gears 74J and 74H with a constant gear ratio.

At this time, each component of the main shaft 70 planetary gear unit 110 (sun gear (S), ring gear (R), planetary gear carrier (C)) and the first sub-axis (80) of the planetary gear unit (110 ') The rotation ratio of each component (sun gear S ', ring gear R', planetary gear carrier C ') is set to 5: 1: 1 and the second sub-axis 90 differential gear unit 210 " Rotation ratio for each component (differential A-axis (DA ″), differential B-axis (DB ″), pinion gear housing (DP ″)] of [pinion gear housing (DP) × 2 = differential A-axis (DA) + Differential B-axis (DB)], and the gear 74A and the input rotation part 81 of the bent sub-shaft 80 are installed on the drive input rotation part 71 of the main shaft 70. Both the gear 74B and the gear 74G (74G ') arranged in the input rotation part 91 of the second gear shaft 90 have a gear ratio of 1: 1: 1 and the planetary gear unit 110 of the main shaft 70. Sun gear S and the first sub-axis 80, sun gear S 'and the second sub-axis 90 of the planetary gear unit 110' The gear ratio 74E and the first subshaft (20 ") built in the shift control rotation part 72 of the main shaft 70 are set with a rotation ratio of the differential A axis DA " of 210 " (74D) built in the output rotation part 83 of 80 sets the gear ratio to 1: 1, and the gear 74J and the second built in the shift control rotation part 82 of the first sub-shaft 80 are formed. The gear 74H built in the output rotation part 93 of the subshaft 90 set the gear ratio to 1: 1.

In addition, after setting the rotation speed of the second fixed power source FP2 that rotates in the same direction as the rotation of the differential A-axis DA ″ of the second sub-axis 90 of the differential gear unit 210 ″ to 350 RPM, the main shaft ( As a result of varying the initial minimum input rotational speed of the first variable power source (VP1) transmitted to the drive input rotation unit 71 of 70) from 700 RPM to 4,000 RPM, as shown in Table 26 below, the output rotation unit of the main shaft 70 The change in the number of revolutions shown in (73) was changed from '0' RPM to '3,300' RPM.

Table 26

※ Example of speed conversion

Component	RPM (RPM)
74A	700	800	900	1000	1500	2000	2500	3000	3500	4000
74B	700	800	900	1000	1500	2000	2500	3000	3500	4000
74G ′	700	800	900	1000	1500	2000	2500	3000	3500	4000
74C ′	350	400	450	500	750	1000	1250	1500	1750	2000
74K ′	350	350	350	350	350	350	350	350	350	350
74H	0	100	200	300	800	1300	1800	2300	2800	3300
74J	0	100	200	300	800	1300	1800	2300	2800	3300
74D	140	260	380	500	1100	1700	2300	2900	3500	4100
74E	140	160	180	200	300	400	500	600	700	800
73	0	100	200	300	800	1300	1800	2300	2800	3300

In Table 26, the component 74E represents the theoretical value of the rotation ratio of the planetary gear unit 110 with respect to the input rotation part 71, and the component 74C 'is the differential with respect to the input rotation part 91. The theoretical value for the rotation ratio of the gear unit 210

All.

That is, in the transmission device according to the thirteenth embodiment of the present invention, each of the components of the planetary gear unit 110 used as the main shaft 70 and any one planetary gear used as the first sub-axis 80 Output rotational speed with respect to the input rotational speed by the combination of the gears which make the components of the differential gear unit 210 ″ used as the unit 110 'and the second sub-axis 90 parallel to each other. Will be able to arbitrarily expand the transmission range of.

On the other hand, the clutch 94 added to the output rotation part 63 of the second auxiliary shaft 90 at the time of sudden braking or stopping due to the failure of the second rotary power source P2 used as an auxiliary power source, a foot brake abnormality or an unexpected situation is Under the above conditions, the output rotary part is controlled at the combined rotation ratio of the main shaft 70 and the first sub-shaft 80 by controlling the control rotation part 82 of the first sub-shaft by cutting off the rotation of the output part of the second sub-shaft 90 by the sense operation. At 73 rpm for an arbitrary low speed rotation to serve as an automatic engine brake, and at the same time for the various operating devices connected to the output rotation part 73 of the main shaft 70 by the operation of the main rotary power source (P1). The electrical function becomes effective, and in industrial use, the output is stopped to secure secondary accident prevention and safety.

Claims

In a transmission using a gear unit, a gear combination with an extended gear ratio is formed by a parallel combination of mutually parallel axes of at least one planetary gear unit and at least one differential gear unit. First rotational power source and second auxiliary power source which are main power sources to any component of the planetary gear units 110, 110 ′, 110 ″ to differential gear units 210, 210 ′, 220 ″. 2. A transmission apparatus using two rotational power sources and a gear assembly, wherein the rotational power source can be added to each other so as to extend a shift range of the output rotation part of the main shaft.
The method of claim 1, wherein the gear assembly (a)

Each component for at least one planetary gear unit 110 (110 ') (110 ″) [sun gear (S) (S') (S ″), ring gear (R) (R ') (R ″ ), Planetary gear carriers (C) (C ') (C ″)] are planetary gear combinations in which the planetary gear units 110, 110' and 110 ″ are combined in parallel so as to be parallel to each other by gear meshing. 100 and 100 ';

Each component for at least one differential gear unit (210) (210 ') (210 ") (differential A-axis (DA) (DA') (DA"), differential B-axis (DB) (DB ') (DB ″), pinion gear housings (DP) (DP ′) (DP ″)] are formed by combining each differential gear unit 210 (210 ') (210 ″) in parallel to each other by means of gears. Differential gear assembly 200 (200 ');

Each component for at least one planetary gear unit 110 (110 ') (110 ″) [sun gear (S) (S') (S ″), ring gear (R) (R ') (R ″) , Planetary gear carrier (C) (C ') (C ″)] and each component for the at least one differential gear unit (210) (210') (210 ″) [differential A-axis (DA) (DA ') ) (DA ″), differential B-axis (DB) (DB ′) (DB ″), pinion gear housing (DP) (DP ′) (DP ″)] by at least one planetary gear unit 110 due to gear teeth. 110 '(110') and at least one differential gear unit (210) (210 ', 210') are combined to form a composite gear assembly 300 (300 ') in parallel to each other parallel to each other Two rotational power source and a transmission using a gear assembly characterized in that separate configuration.
The method of claim 1, wherein the first rotational driving force (P1) is divided into a first fixed power source (FP1) and the first variable power source (PP1) in which the rotational speed is sequentially changed while the rotational speed is always the main power source of the engine The second rotational driving force P2 serves as an auxiliary power source for controlling the gear ratio of any one gear unit of the gear assembly A, and the second fixed power source FP2 and the rotational speed of which the rotational speed is always constant are sequentially changed. Transmission device using two rotational power source and the gear assembly characterized in that separated by a variable power source (VP2).
2. The planetary gear of claim 1, wherein at least three planetary gear units 110, 110 ′, 110 ″ are planetary in the second minor shaft 30 of the planetary gear assembly 100 ′ in which at least three planetary gear units 110, 110 ′, 110 ″ are coupled in parallel combination by interaxial parallelism. It characterized in that the double brake function is induced by adding the sensor operation clutch means 34 to the output rotation part 33 of the second sub shaft 30 and the planetary gear unit 110 ″ that constitute the gear unit 110 ″. Transmission using two rotating power sources and gear combination.
The third differential gear unit (210) of the differential gear assembly (200 ') according to claim 1, wherein at least three or more differential gear units (210) (210') (210 ") are coupled in parallel combination by parallel to each other. Two rotational power sources, characterized in that a double brake function is induced by adding a sensor operating clutch means 64 to the output rotation part 63 of the second sub-shaft 60 differential gear unit 210 " Transmission using gear combination.
The at least one planetary gear unit (110) (110 ') (110 ") and at least one differential gear unit (210) (210') (210") of at least three mutual axis. To the output rotation part 93 of any planetary gear unit 110 ″ or differential gear unit 210 ″ used as the second sub-axis 90 of the three-row compound gear assembly 300 'coupled in parallel by parallel combination. 2. A transmission apparatus using two rotational power sources and a gear assembly characterized by adding a sensor operating clutch means (94) to cause a double brake function.
The initial output rotational speed of the output rotation of the main shaft is a combination of the rotational speed of P2 and the multiple gear ratio due to the engagement of the gear units and the gear unit components constituting the gear assembly; By using the two rotational power source and the gear combination characterized in that it can be adjusted to the desired rotational speed from the stop output (0 RPM) arbitrarily.
The transmission device according to claim 1, wherein the transmission device can expand the use of the transmission device, such as a stepped transmission including a speed reducer, an industrial continuously variable transmission, and a continuously variable transmission for an automobile. .
The gear assembly of claim 1, wherein the gear assembly drives any component of the planetary gear unit 110 (sun gear (S), ring gear (R), planetary gear carrier (C)) used as the main shaft (10). The input rotation part 11 is used, and the other components (sun gear S, ring gear R, planetary gear carrier C) are shift control rotation parts 12, and another component (sun gear ( S), the ring gear (R), the planetary gear carrier (C)] is composed of any one drive component of the other planetary gear unit 110 'used as the first sub-shaft 20, consisting of a drive output rotation unit (13). [Sun gear (S '), ring gear (R'), planetary gear carrier (C ') are the first sub-axis (20) input rotation part (21), and other components (sun gear (S'), ring gear (R '), planetary gear carrier (C') is the first sub-axis (20) shift control rotation part 22, and any other component (sun gear (S '), ring gear (R'), planet Gear carrier C '] as an output rotating part 23 of the first sub-shaft 20, The first rotational driving force P1 is applied to the shaft 10 driving input rotation unit 11, and the first rotational driving force P1 is applied to the first rotational driving force P1 of the first auxiliary shaft 20. 11) and a gear of different gears 14A and 14B having a constant gear ratio, the shift control rotation part 22 of the first sub-shaft 20 is the second rotation driving force (P2) to which the auxiliary power source is transmitted. And the gears of the other gears 14C and 14K having a constant gear ratio are coupled to each other, and the output rotation part 23 of the first subshaft 20 is constant with the control rotation part 12 for driving shift of the main shaft 10. Two planetary gear units 110 and 110 'coupled to each other by gears of different gears 14E and 14D having gear ratios are formed of a planetary gear assembly 100 in parallel combination by parallelism between axes. Transmission using two rotary power source and gear combination.
10. The gear assembly according to claim 9, wherein another planetary gear unit (110 ″) used as the second sub-axis (30 ″) in the two-plane planetary gear assembly (100) is combined in parallel with each other in parallel. The second sub-axis 30 includes one component (sun gear S ″, ring gear R ″, planetary gear carrier C ″) of another planetary gear unit 110 ″ used as the sub-axis 30. The other input components (sun gear S ″, ring gear R ″, planetary gear carrier C ″) to the shift control rotation section 32 of the second sub-shaft 30. One of the other components (sun gear S ″, ring gear R ″, planetary gear carrier C ″) is composed of an output rotation part 33 of the second sub-axis 30, wherein the second The input rotation part 31 of the sub-shaft 30 is rotated first by the engagement of different gears 14A, 14B, 14G, 14G 'having a constant gear ratio from the main shaft 10 driving input rotation part 11. A motive force P1 is applied to the second auxiliary shaft 30 The speed control rotation part 32 is provided with the second rotational driving force P2 by the engagement of different gears 14C 'and 14K' having a constant gear ratio, and the output rotation part 33 of the second sub-shaft 30. Is coupled to the engagement of the shift control rotary section 22 of the first sub-shaft 20 and the different gears 14J and 14H having a constant gear ratio, and at least to which an additional clutch means 34 actuated by the sensor is added. Two or more planetary gear units 110, 110 'and 110 " are composed of a planetary gear assembly 100' in parallel combination by parallel to each other. Device.
The gear assembly of claim 1, wherein the gear assembly includes any one component of the differential gear unit 210 used as the main shaft 40 (differential A-axis DA, differential B-axis DB, pinion gear housing DP). ] Is the drive input rotation part 41 of the main shaft 40, and the other components (differential A-axis DA, differential B-axis DB, pinion gear housing DP) are shift-controlled of the main shaft 40. FIG. The rotating part 42, and any other component (differential A axis DA, differential B axis DB, pinion gear housing DP) is composed of the output rotating part 43 of the main shaft 40, Remove one component (differential A-axis DA ', differential B-axis DB', and pinion gear housing DP ') of the other differential gear unit 210' used as the first sub-axis 50. The first rotating shaft 51 is configured as an input rotating unit 51 of one sub-shaft 50, and other components (differential A-axis DA ', differential B-axis DB', and pinion gear housing DP ') are provided. The variable speed control rotation part 52, and any other component (differential A-axis (DA '), differential B-axis (DB'), pinion Gear housing DP ′] is configured as an output rotation part 53 of the first sub-shaft 50, and a first rotation driving force P1 is applied to the driving input rotation part 41 of the main shaft 40 and the first sub-shaft. The first rotational driving force P1 is applied to the input rotational portion 51 of the 50 by the engagement of the main shaft 40 driving input rotational portion 41 and the different gears 44A and 44B having a constant gear ratio. The shift control rotation part 52 of the first sub-shaft 50 is coupled by engagement of the second rotational driving force P2 to which the auxiliary power source is transmitted and different gears 44C and 44K having a constant gear ratio. The output rotation part 53 of the sub-shaft 50 is composed of two differential gear units 210 coupled by engagement of the shift control rotation part 42 of the main shaft 40 and the different gears 44E and 44D having a constant gear ratio ( 210 ') consists of two rotational power sources and a gear assembly, characterized in that they consist of a differential gear assembly 200 in parallel combination by parallel to each other. Gearshift.
12. The gear assembly as set forth in claim 11, wherein another differential gear unit (210 ") used as a second sub-axis (60 ") is used in a two-column differential gear assembly (200) in parallel with each other in parallel. The second sub-shaft of one component (differential A-axis DA, differential B-axis DB, pinion gear housing DP ") of another differential gear unit 210 " The input rotation part 61 of (60) is used, and the other components (differential A-axis DA ", differential B-axis DB", and pinion gear housing DP ") are shifted to the second sub-shaft 60. The control rotary part 62, and any other component (differential A-axis DA ″, differential B-axis DB ", pinion gear housing DP ") 63, but different gears 44A, 44B, 44G, 44G having a fixed gear ratio from the main shaft 40 driving input rotation part 41 to the input rotation part 61 of the second sub-shaft 60. The first rotational driving force (P1) is applied by the engagement of '), A second rotational driving force P2 is applied to the shift control rotation part 62 of the second subshaft 60 by engagement of different gears 44C 'and 44K' having a constant gear ratio. A separate clutch which is coupled to the output rotation part 63 of the 60 by engagement of the gear shift control rotation part 52 of the first subshaft 50 and the different gears 44J and 44H having a constant gear ratio and operated by a sensor. At least three differential gear units 210 (210 ') (210 ") with means 64 added are made up of a differential gear assembly 200' in parallel combination by interaxial parallelism. Transmission using rotational power source and gear combination.
The gear assembly according to claim 1, wherein the gear assembly is any component of the planetary gear unit 110, which is used as the main shaft 70 (sun gear (S), ring gear (R), planetary gear carrier (C)). Alternatively, any one component of the differential gear unit 210 (differential A axis DA, differential B axis DB, pinion gear housing DP) is used as the driving input rotation part 71 of the main shaft 70. , The other component (sun gear (S), ring gear (R), planetary gear carrier (C), or differential A axis (DA), differential B axis (DB), pinion gear housing (DP)) ), And any other component (sun gear (S), ring gear (R), planetary gear carrier (C), or differential A axis (DA), differential B axis (DB)). , The pinion gear housing (DP)] to the output rotation portion 73 of the main shaft 70, and any other planetary gear unit (110 ') or differential gear unit (210') used as the first sub-axis (80). Components of sun gear (sun gear (S '), ring gear (R'), planetary gear carrier (C '), Alternatively, the differential A-axis DA ', the differential B-axis DB', and the pinion gear housing DP 'are used as the input rotation part 81 of the first sub-axis 80, and the other component (sun gear S'). ), Ring gear (R '), planetary gear carrier (C') or differential A-axis (DA '), differential B-axis (DB'), pinion gear housing (DP ')] A variable speed control rotation part 82, and any other component (sun gear S ', ring gear R', planetary gear carrier C ', or differential A axis DA', differential B axis ( DB ') and pinion gear housing DP' as an output rotation part 83 of the first sub-shaft 80, and the first input of driving force P1 is applied to the drive input rotation part 71 of the main shaft 70. The first rotational driving force P1 is applied to the input rotational portion 81 of the first sub-axis 80 and the gears of the main shaft 70 drive input rotational portion 71 and the different gears 74A and 74B having a constant gear ratio. It is given by, the shift control rotary part 82 of the first sub-shaft 80 is the second rotation to which the auxiliary power source is transmitted The driving force P2 is coupled to the gears of different gears 74C and 74K having a constant gear ratio, and the output rotation part 83 of the first subshaft 80 is a shift control rotation part 72 of the main shaft 70. And at least one planetary gear unit 110, 110 ′ and at least one differential gear unit 210, 210 ′ coupled to each other by engagement of different gears 74E, 74D having a constant gear ratio with each other. A transmission device using two rotational power sources and a gear assembly, characterized by consisting of a compound gear assembly 300 in parallel combination by parallel between axes.
14. The gear assembly of claim 13, wherein another planetary gear unit 110 " or differential gear unit 210 ", which is used as the second sub-axis 90 in the two-gear composite gear assembly 300, is parallel to each other. In combination with one another of the other planetary gear unit 110 ″ or the differential gear unit 210 ″ (sun gear S ″, ring gear R ″ used as the second sub-shaft 90). ), Planetary gear carrier (C ″) or differential A axis (DA ″), differential B axis (DB ″), pinion gear housing (DP ″) as the input rotating part 91 of the second sub-shaft 90 , Other components [sun gear (S ″), ring gear (R ″), planetary gear carrier (C ″), or differential A axis (DA ″), differential B axis (DB ″), pinion gear housing (DP ″ )] As the shift control rotation part 92 of the second sub-shaft 90, and any other component (sun gear S ″, ring gear R ″, planetary gear carrier C ″, or differential A). Shaft (DA ″), differential B axis (DB ″), pinion gear housing (DP ″)] Comprising an output rotation portion 93 of the 90, the input rotation portion 91 of the second sub-shaft 90 from the main shaft 70 drive input rotation portion 71 has a different gear (74A) having a constant gear ratio ( The first rotational driving force P1 is applied by the engagement of 74B) 74G and 74G ', and the gear shift control rotation part 92 of the second sub-axis 90 has a different gear ratio 74C' with a constant gear ratio. The second rotational driving force P2 is imparted by the engagement of the 74K ′, and the output rotation part 93 of the second subshaft 90 has a constant gear ratio with the shift control rotation part 82 of the first subshaft 80. At least one planetary gear unit (110) (110 ') (110 ") coupled with the engagement of different gears (74J) (74H) with a separate clutch means (94) actuated by a sensor. And a combination of at least one differential gear unit (210) (210 ') (210 "), at least three of which are combined gears in parallel combination by parallel to each other axis ( 300 ′), a transmission using two rotational power sources and a gear assembly.