KR100965101B1 - Two reply power source speed change gear using gear corporate bady - Google Patents

Abstract

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 .

Planetary gear unit, differential gear unit, rotating power source, gear coupling

Description

Transmission using two rotating power sources and gear assembly {Two reply power source speed change gear using gear corporate bady}

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 .

Generally, in various industrial sites, the input rotational speed of main motive power is shifted through gear ratio in various places such as industrial machinery, hoist, conveyor for transferring goods, winch, elevator and escalator according to the use, and the driving means of the drive shaft. Various types of stepped transmissions and continuously variable transmissions that transmit output speeds that are shifted to a wider range 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 a belt continuously variable transmission, a large power cannot be transmitted due to the limited size of the belt. Therefore, the range of the transmission is limited to a certain section. The hydraulic continuously variable transmission has 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. We had a fundamental problem in that process.

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 extend the use of the transmission, such as a stepper 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 the transmission ratio of any one gear unit of the first rotational driving force P1 and the gear coupling body (A) serving as the main power sources 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 power source power (P1) to the drive input rotation part 11 of the main shaft (10) ) And a first rotational driving force P1 is engaged with the main shaft 10, the input rotational portion 11, and 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 is coupled to the drive gear control rotation part 12 of the main shaft 10 by engagement of different gears 14E and 14D having a constant gear ratio. Become .

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 2nd axle 30 is engaged by the engagement of the shift control rotation part 22 of the 1st subshaft 20 with the other gear 14J, 14H which has a fixed gear ratio, and is operated by a sensor. It has a structure in which 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 rotating 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 second sub-shaft 60 is used to remove one of the other components (differential A-axis DA ″, differential B-axis DB ", and pinion gear housing DP "). Comprising an output rotation part 63 of the two sub-shaft 60, the input rotation part 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 part 41 By 44B, 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 a drive output rotation part 73 of the main shaft 70, and any other planetary gear unit 110 'or differential gear unit 210' used as the first sub-shaft 80. Components of sun gear (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 input rotation part 81 of the first sub-shaft 80, 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 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', or differential A axis DA ', differential B axis DB', pinion gear housing DP '] 83), a first rotational driving force (P1) is applied to the drive input rotation unit 71 of the main shaft 70 and the input of the first sub-axis 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 another planetary gear unit 110 ″ or 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 great effect that can be applied to various types of transmissions including gearboxes, and also for vehicles and industrial applications.

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.

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.

Of the transmission using planetary gear assembly 100 (100 ') and two rotational driving forces. Example >

Figure 1a is a coupling cross-sectional view showing a coupling relationship according to the first embodiment of the planetary gear assembly (100) consisting of two planetary planetary gear units 110 (110 ') coupled to the gear assembly (a) of the present invention, Figure 1b is a cross-sectional view showing a coupling relationship according to the second embodiment consisting of the planetary gear assembly 100 of the present invention, Figure 1c is a gear assembly (a) of three rows of planetary gear units 110 (110 ') Fig. 1 is a cross sectional view showing a coupling relationship according to the third embodiment of the planetary gear assembly 100 'coupled with (110 ").

First, as shown in FIG. 1A, 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 a transmission device using the planetary gear assembly 100 will be described.

After setting the following <Setting Example 1> as a precondition for explaining the shifting process according to the first embodiment using the planetary gear assembly 100 of the present invention, look at the shifting process of the output rotation speed when the vehicle saw.

<Setting example 1>

1.Lower rotation speed of P1 → 700rpm
2. Rotational speed of P2 → same direction of rotation of 14B
1400 rpm fixed speed
3. Turn ratio of each part of each planetary gear unit (S: C: R)
→ 5: 1: 1
4. Gear ratio of 14A: 14B → 5: 1
5. 14C: gear rotation ratio of 14K → 1: 1
6. 14E: Gear rotation ratio of 14D → 1: 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' The ratio was set to 1: 1.

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 <Table 1>, the amount of change in the number of revolutions appearing in the output rotating part 13 of the main shaft 10 was changed 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, and each gear ratio is arbitrarily changed, the speed ratio corresponding to the corresponding combination conditions will appear, without departing from the technical spirit of the present invention. Of course, it can be variously performed as long as it does.

<Table 1>

※ 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

In Table 1, the element 14E represents 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 1b, after setting the following <Setting Example 2> as a prerequisite for explaining the shifting process according to the second embodiment using the planetary gear assembly 100 of the present invention, the output rotation We looked at the number shifting process.

<Setting example 2>

1.rotation speed of P1 → 700rpm
2. Rotational speed of P2 → same direction of rotation of 14B
70 rpm fixed speed
3. Turn ratio of each part of each planetary gear unit (S: C: R)
→ 5: 1: 1
4. Gear rotation ratio of 14A: 14B → 1: 1.5
5. 14C: gear rotation ratio of 14K → 1: 1
6. 14E: Gear rotation ratio of 14D → 1: 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).

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.

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 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 the result, the amount of change in the number of revolutions appearing in the output rotation part 13 of the main shaft 10 is shifted from '0' RPM to '330' RPM as shown in Table 2 below.

<Table 2>

※ 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

In Table 2, the element 14E represents 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 conditions will appear. Of course, it can be variously performed as long as it does not.

Next, as shown in Figure 1c, after setting the following <Setting Example 3> as a prerequisite for explaining the shifting process according to the third embodiment using the planetary gear assembly 100 'of the present invention, the output We looked at the speed change process.

<Setting example 3>

1.Lower rotation speed of P1 → 700rpm
2. Rotational speed of P2 → same direction of rotation of 14G ′
175 rpm fixed speed
3. Turn ratio of each part of each planetary gear unit (S: C: R)
→ 4: 1: 1
4. 14A: Gear rotation ratio of 14B → 1: 1
5. 14G: Gear rotation ratio of 14G ′ → 1: 1
6. 14C ′: Gear rotation ratio of 14K ′ → 1: 1
7. 14J: Gear rotation ratio of 14H → 1: 1
8. 14E: Gear rotation ratio of 14D → 1: 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).

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.

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.

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 rotational 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 3 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 3>

※ 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 3, the elements 14E and 14C ′ represent theoretical values of rotational ratios of the planetary gear units 110 and 110 ′ with respect to the input rotation units 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 &quot; 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.

< Differential gear assembly (200) (200 ') and  Of the transmission using two rotational driving forces Example >

Figure 2a is a cross-sectional view showing a coupling relationship according to the fourth embodiment of the gear assembly (A) of the present invention consists of a differential gear assembly (200) coupled to two rows of differential gear units (210, 210 '), Figure 2b is a cross-sectional view showing a coupling relationship according to a fifth embodiment of the differential gear assembly 200 of the present invention, Figure 2c 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 &quot;).

First, as shown in FIG. 2A, the coupling relationship between two rotational driving forces consisting of the differential gear assembly 200 according to the fourth embodiment of the present invention and a transmission using the differential gear assembly 200 will be described.

After setting the following <Setting Example 4> 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 process of the output rotation speed was examined.

<Setting example 4>

1.Lower rotation speed of P1 → 700rpm
2. P2 rotation speed → 44B rotation same direction
175 rpm fixed speed
3. Turn ratio of each part of each differential gear unit →
DP X 2 = DA + DB
4. Gear rotation ratio of 44A: 44B → 1: 1
5. 44C: Gear rotation ratio of 44K → 1: 1
6. 44E: Gear rotation ratio of 44D → 1: 1

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 of the first part shaft 50 ( The rotation ratio of the differential A-axis DA 'of the 210') is set to 1: 1, and the gear 44E and the first sub-shaft 50 of the gear 44E built in the shift control rotation part 42 of the main shaft 40 are set to 1: 1. The gear 44D built in the output rotation part 53 has a gear ratio of 1: 1 and the differential B axis DB of the differential gear unit 210 of the main shaft 40 and the differential gear unit 210 of the first subshaft 50. Rotation ratio of the pinion gear housing (DP ') to 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 shown in the output rotation part 43 of the main shaft 40 is shifted from '0' RPM to '3,300' RPM as shown in Table 4 below.

<Table 4>

※ 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 4, the component 44E represents a 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 2b, after setting the following <Setting Example 5> 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 We looked at the number shifting process.

<Setting example 5>

1.Lower rotation speed of P1 → 700rpm
2. Rotational speed of P2 → opposite rotation of 44B
350 rpm fixed speed
3. Turn ratio of each part of each differential gear unit
→ DP X 2 = DA + DB
4. Gear rotation ratio of 44A: 44B → 2: 1
5. 44C: Gear rotation ratio of 44K → 1: 1
6. 44E: Gear rotation ratio of 44D → 1: 1

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 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.

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 [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, the variation in the number of revolutions shown in the output rotation part 43 of the main shaft 40 is shifted from '0' RPM to '3,300' RPM as shown in Table 5 below.

<Table 5>

※ 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

Component 44E in Table 5 shows 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.

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 2c, after setting the following <Setting Example 6> as a prerequisite for explaining the shifting process according to the sixth embodiment using the differential gear assembly 200 'of the present invention, the output We looked at the speed change process.

<Example 6>

1. Minimum rotation speed of P1 → 700rpm
2. Rotational speed of P2 → same direction of rotation of 44G ′
350 rpm fixed speed
3. Turn ratio of each part of each differential gear unit
→ DP X 2 = DA + DB
4. Gear rotation ratio of 44A: 44B → 1: 1
5. 44G: Gear rotation ratio of 44G ′ → 1: 1
6. 44C ′: Gear rotation ratio of 44K ′ → 1: 1
7.44J: Gear rotation ratio of 44H → 1: 1
8. 44E: Gear rotation ratio of 44D → 1: 1

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 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.

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.

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 &quot; 53 and the gears of the other gears 44J and 44H having a constant gear ratio are engaged.

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 &quot; 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 to rotate in the same direction as the rotation of the differential A axis DA ″ of the second sub-shaft 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 6, the output rotation unit of the main shaft 40 The variation in the number of revolutions shown in (43) is shifted from '0' RPM to '2,800' RPM.

<Table 6>

※ 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 6, 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 &quot; 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 at the time of sudden braking or stopping due to the failure of the second rotational power source P2 used as an auxiliary power source, a foot brake abnormality or an unexpected situation is 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.

Of the gearbox using the combined gear assembly 300 (300 ') and two rotational driving forces. Example >

Figure 3a is a combination of any one of the planetary gear unit (110) is used as the main shaft 70 and the differential gear unit (210 ') is used as the main shaft 70 of the gear assembly (a) of the present invention. 3 is a cross-sectional view showing a coupling relationship according to the eighth embodiment of the composite gear coupling body 300 of the present invention. 3C is a combination 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. 3 is a cross-sectional view illustrating a coupling relationship according to a tenth embodiment of the composite gear coupling member 300 according to the present invention.

First, as shown in FIG. 3A, the coupling relationship between two rotational driving forces including the compound gear assembly 300 according to the seventh embodiment of the present invention and the transmission device using the compound gear assembly 300 will be described.

After setting the following <Setting Example 7> as a precondition for explaining the shifting process according to the seventh embodiment using the composite gear assembly 300 of the present invention, the shifting process of the output rotation speed was examined.

<Setting example 7>

1.Lower rotation speed of P1 → 700rpm
2. P2 rotation speed → 74B rotation same direction
300rpm fixed speed
3. Turn ratio of each part of the planetary gear unit (S: C: R)
→ 5: 1: 1
4. Turn ratio of each part of differential gear unit
→ DP X 2 = DA + DB
5. 74A: 74B gear rotation ratio → 1: 1
6. 74C: Gear rotation ratio of 74K → 1: 1
7. 74E: 74D gear rotation ratio → 1.4: 1

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 driving input rotation part 71 of the 70 from 700 RPM to 4,000 RPM, as shown in Table 7, the output rotation part of the main shaft 70 ( The change in rotation speed shown in 73) is shifted from '0' RPM to '3,960' RPM.

<Table 7>

※ 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 7, 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, 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 3b, after setting the following <Setting Example 8> 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 We looked at the number shifting process.

<Setting example 8>

1.Lower rotation speed of P1 → 700rpm
2. Rotational speed of P2 → opposite rotation of 74B
180 rpm fixed speed
3. Turn ratio of each part of the planetary gear unit (S: C: R)
→ 5: 1: 1
4. Turn ratio of each part of each differential gear unit
→ DP X 2 = DA + DB
5.74A: 74B gear turn ratio → 5: 1
6. 74C: Gear rotation ratio of 74K → 1: 1
7. 74E: 74D gear rotation ratio → 1.4: 1

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 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 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: 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. The gear ratio 74E and the first sub-shaft 80, which are set in the shift control rotation part 72 of the main shaft 70, are set at a rotation ratio of the pinion gear housing DP 'of 210'). The gear 74D built in the output rotation part 83 of the main body 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 rotation 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 8, 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 8>

※ 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 8, 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, 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 3c, after setting the following <Setting Example 9> as a prerequisite for explaining the shifting process according to the ninth embodiment using the composite gear assembly 300 of the present invention, the output rotation We looked at the number shifting process.

<Example 9>

1.Lower rotation speed of P1 → 700rpm
2. Rotational speed of P2 → opposite rotation of 74B
210 rpm fixed speed
3. Turn ratio of each part of the planetary gear unit (S: C: R)
→ 5: 1: 1
4. Turn ratio of each part of differential gear unit
→ DP X 2 = DA + DB
5. 74A: 74B gear rotation ratio → 1: 1
6. 74C: Gear rotation ratio of 74K → 1: 1
7. 74E: Gear rotation ratio of 74D → 1: 1

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 9, 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 9

※ 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 9, the component 74E represents the theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation part 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.

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 3d, after setting the following <Setting Example 10> 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 We looked at the number shifting process.

<Setting example 10>

1.Lower rotation speed of P1 → 700rpm
2. P2 rotation speed → 74B rotation same direction
210 rpm fixed speed
3. Turn ratio of each part of the planetary gear unit (S: C: R)
→ 5: 1: 1
4. Turn ratio of each part of differential gear unit
→ DP X 2 = DA + DB
5. 74A: 74B gear rotation ratio → 1: 1
6. 74C: Gear rotation ratio of 74K → 1: 1
7. 74E: Gear rotation ratio of 74D → 1: 1

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-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.

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 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 10, 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 10

※ 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 10, the component 74E represents a 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.

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 4a, after setting the following <Setting Example 11> as a prerequisite for explaining the shifting process according to the eleventh embodiment using the composite gear assembly 300 'of the present invention, the output We looked at the speed change process.

<Setting example 11>

1.Lower rotation speed of P1 → 700rpm
2. Rotational speed of P2 → same direction of rotation of 74G ′
490rpm fixed speed
3. Turn ratio of each part of the planetary gear unit (S: C: R)
→ 6: 1: 1
4. Turn ratio of each part of each differential gear unit
→ DP X 2 = DA + DB
5.74A: 74B gear turn ratio → 6: 1
6. 74A: Gear rotation ratio of 74G ′ → 1: 1.4
7. 74C ′: Gear turn ratio of 74K ′ → 1: 1
8. 74J: 74H gear rotation ratio → 1: 1
9.74E: Gear rotation ratio of 74D → 1: 1

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 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 part 83 of the one sub-shaft 80 and is coupled with 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.

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.

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 &quot; 93 is engaged by the 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 11 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 11

※ 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 11, 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.

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 4b, after setting the following <Setting Example 12> as a prerequisite for explaining the shifting process according to the twelfth embodiment using the composite gear assembly 300 'of the present invention, the output We looked at the speed change process.

<Setting example 12>

1.Lower rotation speed of P1 → 700rpm
2. Rotational speed of P2 → same direction of rotation of 74G ′
232.2rpm fixed speed
3. Turn ratio of each part of the planetary gear unit (S: C: R)
→ 6: 1: 1
4. Turn ratio of each part of each differential gear unit
→ DP X 2 = DA + DB
5.74A: 74B gear turn ratio → 6: 1
6. 74G: Gear rotation ratio of 74G ′ → 1: 1
7. 74C ′: Gear turn ratio of 74K ′ → 1: 1
8. 74J: 74H gear rotation ratio → 1: 1
9.74E: Gear rotation ratio of 74D → 1: 1

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 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 part 83 of the one sub-shaft 80 and is coupled with the gear 74D having a constant 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.

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.

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 &quot; 93 is engaged by the 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 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 rotating in the same direction as the rotation of the input rotational unit pinion gear housing DP ″ of the second auxiliary shaft 90 differential gear unit 210 ″ to 232.2 RPM, As a result of varying the initial minimum input rotational speed of the first variable power source VP1 transmitted to the drive input rotation part 71 of the 70 from 700 RPM to 4,000 RPM, the output of the main shaft 70 is as shown in Table 12 below. 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 12

※ 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

In Table 12, 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, 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. It is possible to arbitrarily extend the shift 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.

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 4c, after setting the following <Setting Example 13> 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 We looked at the speed change process.

<Example 13>

1.Lower rotation speed of P1 → 700rpm
2. Rotational speed of P2 → same direction of rotation of 74G ′
350 rpm fixed speed
3. Turn ratio of each part of each planetary gear unit (S: C: R)
→ 5: 1: 1
4. Turn ratio of each part of differential gear unit
→ DP X 2 = DA + DB
5. 74A: 74B gear rotation ratio → 1: 1
6. 74G: Gear rotation ratio of 74G ′ → 1: 1
7. 74C ′: Gear turn ratio of 74K ′ → 1: 1
8. 74J: 74H gear rotation ratio → 1: 1
9.74E: Gear rotation ratio of 74D → 1: 1

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).

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.

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.

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 the 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 &quot; 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 &quot;) 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 &quot; of 210 &quot; (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 driving input rotation part 71 of the 70 from 700 RPM to 4,000 RPM, the output of the main shaft 70 is as shown in Table 13 below. The amount of change in the number of revolutions appearing in the rotating unit 73 was obtained to shift from '0' RPM to '3,300' RPM.

TABLE 13

※ 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 13, 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, and the component 74C 'is differential with respect to the input rotation unit 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 rotation with respect to the input rotational speed by the combination of the gears that make the components of the differential gear unit 210 ″ used as the unit 110 'and the second sub-axis 90 parallel to each other. It is possible to arbitrarily expand the range of numbers.

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.

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.

Figures 1a, 1b, 1c constitute the gear assembly of the present invention

                  Each embodiment showing the coupling relationship of each planetary gear assembly

2a, 2b, 2c constitute a gear assembly of the present invention

                  Each embodiment showing the coupling relationship of each differential gear assembly

3A, 3B, 3C, and 3D constitute a gear assembly of the present invention.

                  Each embodiment showing the coupling relationship of each compound gear assembly

4a, 4b, 4c constitute a gear assembly of the present invention

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

<Description of the symbols for the main parts of the drawings>

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

Claims (14)

In a transmission using a gear unit, each component of the 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 parallel to each other between the planetary gear units 110, 110 'and 110 "by gear meshing. Planetary gear assembly (100) (100 ') and combined in parallel so as to be; At least one differential gear unit Each component for at least one differential gear unit 210 (210 ') (220 ") [differential A-axis (DA) (DA') (DA"), differential B-axis (DB) (DB ') (DB ″), pinion gear housings (DP) (DP') (DP ″)], and the differential gear units 210, 210 'and 220 &quot; A differential gear assembly (200, 200 ') which is combined in parallel to be parallel; Each component for at least one planetary gear unit 110 (110 ') (110 ″) [sun gear (S) (S') (S ″), ring gear (R) (R ') (R ″) , Each component (differential A-axis DA) DA ′ for the planetary gear carrier C (C ′) (C ″) and at least one differential gear unit 210 (210 ′, 220 ″). ) (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 ', 220 ") of the combined gear assembly 300, 300' in parallel combination to be parallel to each other axis of the; One component of the planetary gear unit 110, which constitutes a gear assembly in which the gear ratio is expanded by a force combination by parallel to each other, wherein the planetary gear assembly 100 is used as the main shaft 10 [ Sun gear (S), ring gear (R), planetary gear carrier (C)] drive input rotation The other part (sun gear S, ring gear R, planetary gear carrier C) is the drive rotation control rotation part 12, and the other component (sun gear) (S), ring gear (R), planetary gear carrier (C)] by the drive output rotation part 13, and any of the other planetary gear units (100 ') used as the first sub-shaft (20). The element (sun gear S ', ring gear R', planetary gear carrier C ') is the first sub-shaft input rotation part 21, and the other components (sun gear S', ring gear R). ′), The planetary gear carrier C ′ is the first sub-shift control control part 22, and any other component (sun gear S ′, ring gear R ′, planetary gear carrier C ′). ) Is configured as an output rotation unit 23 of the first sub-shaft, wherein the drive input rotation unit 11 is provided with a first rotational driving force P1 and the first sub-axis input rotational unit 21 has a first rotational driving force P1. ) With the driving input rotation part 11 and a constant gear ratio It is given by the engagement of the other gear 14A, 14B, the shift control rotary part 22 of the first sub-shaft 20 has a different gear having a constant gear ratio and the second rotational driving force (P2) to which the auxiliary power source is transmitted. (14C) (14K) is coupled to each other, the output rotation part 23 of the first sub-shaft 20 is a different gear 14E having a constant gear ratio with the drive rotation control rotation part 12 of the main shaft (10). Two planetary gear units (110) (110 ') coupled by the engagement of the fourteen (14D) is a transmission device using two rotational power source and the gear assembly, characterized in that the parallel combination by the mutual axis parallel. delete delete delete delete delete delete delete delete 2. The planetary gear assembly 100 'of claim 1, wherein the other planetary gear assembly 100' is formed by two planetary gear assembly 100 having a second sub-axis 30 as a second sub-axis 30. In combination, 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 replaced. The input rotation part 31 of the 2nd sub-shaft 30 is made, and the other components (sun gear S ", ring gear R", and planetary gear carrier C ") are shifted of the 2nd sub-shaft 30. As shown in FIG. The control rotating section 32, and any other components (sun gear (S "), ring gear (R"), planetary gear carrier (C ") to the output rotating section 33 of the second sub-shaft (30). The input rotation part 31 of the second sub-shaft 30 includes a plurality of gears 14A, 14B, 14G 'and 14G' having a constant gear ratio from the main shaft 10 driving input rotation part 11. The first rotational driving force P1 is imparted by the engagement, A second rotational 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, and the second subshaft 30 Separate clutch means which is coupled to the output rotation part 33 of the first sub-shaft 20 by engagement of the shift control rotation part 22 of the first sub-shaft 20 and the different gears 14J and 14H having a constant gear ratio and operated by a sensor. At least three planetary gear units 110, 110 'and 110 &quot; to which 34 are added are composed of a planetary gear assembly 100' in parallel combination by parallel to each other. Transmission using power source and gear combination. 2. The differential gear assembly (200) according to claim 1, wherein the differential gear assembly (200) is any component of the differential gear unit (210) used as the main shaft (differential A-axis (DA), differential B-axis (DB), pinion gear). The housing DP as 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) as the main shaft 40; ), And any other component (differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)) of the output shaft (43) of the main shaft (40). And one of the other differential gear unit 210 'used as the first sub-shaft 50 (differential A-axis DA', differential B-axis DB ', pinion gear 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', pinion gear housing DP ') A variable speed control rotation part 52 of the sub-axis 50, and any other component (differential A-axis DA ', differential B-axis (DB') ), The pinion gear housing (DP ′)] is composed of the output rotation portion 53 of the first sub-shaft 50, the first rotation driving force (P1) is given to the main shaft 40 drive input rotation portion 41 and the The first rotational driving force P1 is applied to the input rotation part 51 of the first subshaft 50 by engagement of the main shaft 40 driving input rotation part 41 with different gears 44A and 44B having a constant gear ratio. The shift control rotation part 52 of the first sub-shaft 50 is coupled with a second rotational driving force P2 to which an auxiliary power source is transmitted and a gear of different gears 44C and 44K having a constant gear ratio. The output rotation part 53 of the first sub-shaft 50 is composed of two differential gear units 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. Two rotational power sources and gear joints, characterized in that they consist of a differential gear assembly 200 in parallel combination by parallel to each other. Transmission using a sieve. 12. The differential gear assembly (200 ') according to claim 11, wherein another differential gear assembly (200') is used in a two-column differential gear assembly (200) as a second sub-axis (60). In combination, any component of another differential gear unit 210 ″ used as the second sub-axis 60 (differential A axis DA ″, differential B axis DB ″, pinion gear housing DP). )] As the input rotation part 61 of the second sub-shaft 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 sub-shaft 60 is used, and any other component (differential A-axis DA ″, differential B-axis DB ″, pinion gear housing DP ″) is used as the second sub-shaft ( The output rotation part 63 of the 60, but the input rotation part 61 of the second sub-shaft 60 from the main shaft 40 drive input rotation part 41 having different gear ratio (44A) (44B) The first rotational driving force P1 by the engagement of 44G and 44G '. ) Is given to the shift control rotation part 62 of the second sub-shaft 60 is given a second rotational driving force (P2) by the engagement of different gears (44C ') (44K') having a constant gear ratio, The output rotation part 63 of the second sub-shaft 60 is coupled to the gear of the shift control rotation part 52 of the first sub-shaft 50 by different gears 44J and 44H having a constant gear ratio. At least three or more differential gear units 210 (210 ') (210 ") with the additional clutch means 64 actuated are composed of a differential gear assembly 200' in parallel combination by parallel to each other. A transmission using two rotating power sources and a gear assembly. The composite gear assembly 300 is any one component of any one planetary gear unit 110 used as the main shaft 70 (sun gear (S), ring gear (R), planetary gear carrier) (C)] or any component of the differential gear unit 210 (differential A-axis DA, differential B-axis DB, pinion gear housing DP) to the drive input rotation part of the main shaft 70 ( 71), and 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). Is the shift control rotation part 72 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). Shaft (DB), pinion gear housing (DP)] as the output rotation part 73 of the main shaft 70, and any other planetary gear unit (110 ') or differential gear unit used as the first sub-axis (80) Any component of 210 '(Sun gear (S'), ring gear (R '), planetary gear catch C 'or differential A-axis DA', differential B-axis DB ', and pinion gear housing DP' as the input rotation part 81 of the first sub-axis 80, and another configuration. Element (sun gear (S '), ring gear (R'), planetary gear carrier (C ') or differential A-axis (DA'), differential B-axis (DB '), pinion gear housing (DP'). A shift control rotation part 82 of one sub-axis 80, and any other component (sun gear S ', ring gear R', planetary gear carrier C ', or differential A axis DA' ), The differential B-axis (DB ′), the pinion gear housing (DP ′)] is composed of the output rotation portion 83 of the first sub-shaft 80, the first drive shaft rotation portion 71 of the main shaft 70 The rotational driving force P1 is applied, and the first rotational driving force P1 is different from the input rotational portion 81 of the first sub-axis 80 with a constant gear ratio with the gear 70A. (74B) is provided, the shift control rotation part 82 of the first sub-shaft 80 is the auxiliary power source is transmitted The second rotational driving force (P2) is coupled to the engagement of the different gears 74C (74K) having a constant gear ratio, the output rotation portion 83 of the first sub-axis 80 is the shift control rotation of the main shaft 70 At least one planetary gear unit (110) (110 ') and at least one differential gear unit (210) (210') coupled by engagement of 72 and different gears (74E) (74D) having a constant gear ratio. 2) a transmission device using two rotational power sources and a gear combination, characterized in that the combination gear 300 is made of a parallel combination by parallel to each other. The method of claim 1, wherein the other compound gear assembly (300 ') is another planetary gear unit (110 ″) or differential gear unit 210 used as the second sub-axis 90 in the two-row compound gear assembly (300) ″) Is a parallel combination by parallel to each other, and any component of another planetary gear unit 110 ″ or 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 rotating part 91, and other components (sun gear S ″, ring gear R ″, planetary gear carrier C ″, differential A axis DA ″, differential B axis DB ″, The pinion gear housing DP &quot; 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 gear housing ( DP ″)] as the output rotation part 93 of the second sub-shaft 90, and the input rotation part 91 of the second sub-shaft 90 has a constant gear ratio from the main shaft 70 driving input rotation part 71. The first rotational driving force P1 is applied by the engagement of the different gears 74A, 74B, 74G, 74G ', and the gear shift control unit 92 of the second sub-axis 90 has a constant gear ratio. The second rotational driving force P2 is applied by the engagement of the different gears 74C 'and 74K', and the speed change of the first subshaft 80 is applied to the output rotational portion 93 of the second subshaft 90. At least one planetary gear unit 110 coupled with a control rotation unit 82 and a gear of different gears 74J and 74H having a constant gear ratio and to which a separate clutch means 94 operated by a sensor is added. A combination of (110 ') (110 ") and at least one differential gear unit (210) (210') (210") in parallel combination by at least three mutual axes Transmission using two source of rotational power and gear combination, characterized by made of an sum gear assemblies 300 '.

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