WO2011065659A9

WO2011065659A9 - Transmission device using two control means and a gear assembly

Info

Publication number: WO2011065659A9
Application number: PCT/KR2010/006758
Authority: WO
Inventors: 조재민; 강동헌; 한광희; 강성원
Original assignee: Cho Jae-Min; Kang Dong-Hun; Han Kwang-Heui; Kang Sung-Woon
Priority date: 2009-11-26
Filing date: 2010-10-04
Publication date: 2011-07-21
Also published as: WO2011065659A3; KR20090130218A; KR100965102B1; WO2011065659A2

Abstract

The present invention relates to a transmission device comprising at least one control means and a gear assembly, which are coupled with each other. More particularly, the present invention relates to a transmission device using two control means and a gear assembly, in which a transmission is configured such that the rotational frequency of a main power source, transmitted from a driving input shaft, is shifted into the gear ratio of planetary gear units or differential gear units, and transmitted to the driving means, and the gear assembly is formed by combining at least one planetary gear unit and at least one differential gear unit into a double or triple structure through a parallel axial combination, and a transmission ratio for the rotational frequency of a rotational power source is controlled by the two control means in accordance with the multiple gear ratios of the gear assembly. Thus, the rotational power source in an operation may expand the range of shift for the rotational frequency of a driving output shaft, from the rotational frequency set as a minimum input level.

Description

【Specification】

[Name of invention]

Transmission using two control means and gear combination

Technical Field of the Invention

The present invention relates to a transmission using two control means and a gear assembly, and more particularly, a transmission using two rotational power sources and a gear combination, which is filed by the applicant of the present invention (application number: 10_2009 ~ 0107694). As a continuous invention, when the number of revolutions of the main power source transmitted from the drive input shaft constitutes a transmission in which the gear ratio of the planetary gear unit or the differential gear unit is transmitted to the drive means, at least one planetary gear unit and After constructing a gear assembly by combining at least one differential gear unit in double or triple by parallel to the shaft, the ratio of the gear ratio to the rotational speed of the rotating power source is determined by the multiple gear ratio of the gear assembly. By controlling through the speed, the speed of the drive output shaft is changed from the speed at which the drive rotational power source is set to the lowest input. The above relates to a speed change device with two control means and the gear combination which can optionally variously expanded.

Background of the Invention

Generally, in various industrial sites, there are various places such as industrial machines, hoists, conveyors for transferring goods, raw materials, elevators and escalators, depending on the purpose.

Correction Paper (Rule Article 91) Various types of stepped transmissions and continuously variable transmissions, which transmit the output rotational speed to the drive means of the drive shaft by shifting the input rotational speed of the main motive power through the gear ratio, are widely used.

In the case of the stepped transmission, in which the output rotational speed must be sequentially shifted at a certain interval, the engine efficiency is increased when the stepped transmissions, such as L and L, in which a manual transmission and an automatic transmission are widely used for a vehicle, are applied. There was a hassle for the driver to manipulate the transmissions according to the situation.

Therefore, the continuously variable transmissions that can improve the fuel efficiency and maintain the optimum driving conditions for automobiles and industrial use by eliminating the high power transmission efficiency and eliminating the shift stratification during driving without automatically manipulating the transmissions. 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 stepless transmission is performed according to the power transmission form of the power transmission means. It can be divided into transmission, hydraulic continuously variable transmission and gearless continuously variable transmission.

However, in the case of a belt continuously variable transmission, there is a problem in that a large range of transmission cannot be transmitted due to limited size of the belt. Therefore, the hydraulic continuously variable transmission has a large shear force of lubricant due to rolling contact of the rotating body. Power can be transmitted, but as a separate hydraulic device for controlling the power transmission means requires weight and price due to a complicated structure and fuel consumption

Correction Paper (Rule Article 91) There were many problems such as high cost.

Due to the above problems, recently, various types of transmission devices using a planetary gear unit capable of transmitting large power 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 center sun gear, an outer ring gear, and a planetary gear carrier connecting the planetary gears therebetween as one is a sun gear. These three elements, which consist of gears, ring gears and planetary gear carriers, use two elements as input / output shafts and the other one connects a separate power control mechanism such as a clutch to change the rotational force of the entire shaft. It is.

However, the conventional stepped transmission or continuously variable transmissions using the planetary gear units as described above are provided at the designated gear ratios of the respective components of the planetary gear unit (sun gear (S), ring gear (R), planetary gear carrier (C)). There is a problem in that the output rotation speed is limited, the shift of the output rotation speed is made only within a certain range, in particular, due to the characteristics of the planetary gear unit composed of a combination of the sun gear and the ring gear planetary gear carrier Since the size is relatively limited to a certain ratio, the transmission range of the output rotation speed using the gear ratio of each component to the planetary gear unit exceeds the range of 3: 1 to 6: 1. Due to the difficult structure, the conventional continuously variable transmission using a single or a plurality of planetary gear units has a very limited range of speed of output rotation. With fundamentally limited underlying issues

Correction Paper (Rule Article 91) It was.

[Brief Description of Drawings]

La, lb, and lc are embodiments showing the coupling relationship of each planetary gear assembly constituting the gear assembly of the present invention;

Figure 2a, 2b, 2c is an embodiment showing the coupling relationship of each differential gear coupling constituting the gear coupling of the present invention

Figures 3a, 3b, 3c, 3d is an embodiment showing the coupling relationship of each composite gear assembly constituting the gear assembly of the present invention

4A, 4B, and 4C are other examples of the actual view showing the coupling relationship of the composite gear coupling bodies constituting the gear coupling body according to the present invention;

<Description of symbols for main parts in the drawing> A: Gear assembly

100, 100 ^' ： Planetary gear assembly 110, 110' 110 ^* ： Planetary gear unit

200,200 ^' ： Differential Gear Assembly 210,210 ^' 210 ^" ： Differential Gear Unit

300300 ^': complex gear assemblies

10,40,70: Spindle 20,50,80: First minor shaft

11,41,71: Drive input rotation part 21,51,81: Input rotation part of the 1st sub-shaft

12, 42, 72: Shift control rotation 22, 52, 82: Shift control rotation of the first sub-shaft

^■ a

丁

Correction Paper (Rule Article 91) 13,43,73: Drive output rotation part 23,53,83: Output rotation part of the 1st sub-shaft

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

33,63,93: Output rotation part of 2nd sub-shaft 14,44,74: Gear

Fl, F2 ： Control means

[Detailed Description of the Invention]

The first object of the present invention is any one of any one gear unit that constitutes a gear assembly in which the gear ratio is extended by a combination of at least one planetary gear unit and at least one differential gear unit and is used as a main shaft of the gear assembly. Adds a rotational power source to the component, adds a first control means to one component of the other gear unit used as the first sub-shaft, and adds a second control means to the other component respectively to rotate the output of the drive output shaft. It is to provide a transmission using two control means and a gear combination that can be variously extended the transmission range for the number.

The second object of the present invention is to arbitrarily desire the initial output rotational speed of the drive output shaft from the stationary output (0 RPM) by means of multiple gear ratios by the sum of the components for each gear unit constituting the gear assembly. To provide a transmission using two control means and a gear combination that can be adjusted by the electrolyzed water.

The third object of the present invention is the main power of the engine as the drive input rotation of the main shaft while being connected to any one component of the planetary gear unit or differential gear unit used as the main shaft

Correction Paper (Rule Article 91) First control means having a function of shifting to a shift control rotating part of the first sub-shaft while being connected to a rotational driving force (P) through which a circle is transmitted and a planetary gear unit or a car synchronous gear unit used as the first sub-shaft. (F1) and the second control means F2 having another shifting function as the output rotation part of the first sub-shaft, respectively, so that the drive output rotation part of the main shaft is independent of the variation of the input rotational speed of the rotational driving force P. It provides a transmission using two gears and a gear combination that can always maintain a stationary output (0 RPM).

The purpose of the present invention is that each component of the planetary gear unit or the differential gear unit of each gear assembly can arbitrarily expand the 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 transmission using two control means and a gear assembly.

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

The gear combination of the transmission using the two control means and the gear combination according to the present invention (A) is a component of each of the at least one planetary gear unit (110K110 ^' ) (110') [sun gear (SKS ^' ) ( S ^' ), ring gears (R) (R ^' ) (R ^' ), planetary gear carriers (C) (C) (C)] are geared to each planetary gear unit (110) (110 ^' ) (110 ^" ) Planetary gear assembly (100) (100 ^' ), which is a parallel combination of the two axes in parallel with each other; and each component of the at least one differential gear unit (210) (210 ^' ) (210 ^" ) [differential A Axis (DAKDA ^' ) (DA ^" ), Differential B-axis (DB) (DB ^' ) (DB ^" ), Pinion Gear Housing

Correction Paper (Rule Article 91) (DP) (DP ^' ) (DP ";)] is a differential gear assembly (200K200') in which the differential gear units 210, 210 'and 210" are combined in parallel so as to be parallel to each other by gear gears. Wow;

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 :)] and each component for the at least one differential gear unit (210K210 ^' ) (210 ^' ; [differential A-axis (DAKDA ') (DA "), At least one planetary gear unit (110X110 ') (110') by differential gearing of the differential B-axis (DB) (DB ^' ) (DB ^' ), pinion gear housing (DP) (DP ^' ) (DP ^" ;) ) And at least one differential gear unit (210) (210 ') (210') is composed of a composite gear assembly 300 (30 0 '), which is a parallel combination of parallel to each other axis.

And the rotational driving force (P) of the transmission using the two control means and the gear combination according to the present invention becomes the main power source of the engine, the fixed power source (FP) and the variable power source in which the rotational speed is changed in sequence VP).

The planetary gear assembly (100K100 ') of the present invention comprises at least one planetary gear unit (110K110') (11 (Γ) is composed of a parallel combination by parallel to each other, two planetary gear units (110K110) The planetary gear assembly 100 composed of mutually parallel combinations of the two components includes any of the components of the planetary gear unit 110 used as the main shaft 10 (sun gear (S), ring gear (R), Planetary gear carrier (C)]

Correction Paper (Rule Article 91) The other components [sun gear (S), ring gear (R), planetary gear carrier (C)] are used as the control rotation part 12 for shifting, and another component [sun gear (S), ring gear (R), the planetary gear carrier (C)] consists of the drive output rotation part 13, and any component of the other planetary gear unit 110 'used as the first sub-shaft 20 [gear S ^' ), Ring gear (R '), planetary gear carrier (;)] as the first sub-axis (20) input rotation part 21, and other components [sun gear (S ^' _. ), Ring gear (R '), The planetary gear carrier ()] is the first sub-axis 20, the shift control rotation part 22, and any other component [sun gear (S ^' ), ring gear (R ^' ), planetary gear carrier (;)]. It consists of a first sub-axis output rotation unit 23, the main shaft () driving input rotation unit 11 is given a rotational driving force (Ρ) and the input rotational unit 21 of the first sub-shaft (20) a rotational driving force ( Ρ) the mouth of the main shaft 10 It is given by the engagement of the rotating gear 11 and the different gears 1 AX14B having a constant gear ratio, and the shift control rotating part 22 of the first subshaft 20 has a first control means F1 having a control function. Are coupled to each other, and the output rotation part 23 of the first subshaft 20 has a control rotation part 12 for driving shift of the main shaft 10 with the addition of a second control means F2 having another control function. And different gears 14E and 14D having a constant gear ratio.

In addition, the other planetary gear assembly (100 ':) of the present invention in three rows has another planetary gear unit (110): used as the second shaft 30 in the two-plane planetary gear assembly (100). One component of another planetary gear unit 110 · used as the second sub-axis 30 as a parallel combination by parallel between axes [sun gear (S ^' ), ring gear (R ^" ), planetary gear carrier ((;)] As the input rotation part 31 of the second sub-shaft 30, and the other

Correction Paper (Rule Article 91) The component [sun gear (S-), ring gear (ΙΓ), planetary gear carrier (;)] is the variable speed control rotation part 32 of the second subshaft 30, and any other component [sun gear S -), Ring gear (R "), planetary gear carrier ()] is composed of the output rotation part 33 of the second sub-axis (30), the main shaft ( 10) The gear shifting control part of the secondary shaft 30 is coupled to the gear of different gears 14A, 14B, 14G, 14G 'with a constant gear ratio from the driving input rotation part 11; 32 is provided with the first control means F1 having a control function by the engagement of different gears 14C 'and 14K' with a constant gear ratio, and the output rotation part 33 of the second sub-shaft 30. In addition to the second control means (F2) having another control function is added to the engagement of the gear shift control rotary part 22 of the first sub-shaft 20 and the different gear 14JK14H having a constant gear ratio. In the transmission using the two control means and the gear assembly according to the present invention, the rotational driving force (P) of the fixed power source (FP) and the variable power source (VP) is a planetary gear assembly (ΙΟΟΚΙΟΟ ') And the main shaft (10) (40) (70) of the gear unit constituting the gear assembly of any one of the differential gear assembly (200) (200') and the composite gear assembly (300) (30 0 ^' ). Combined with any one of

The differential gear assembly 200K200 'of the present invention includes at least one difference synchronizing gear unit 210K210' or 210 "in a parallel combination by parallelism between two axes, and two differential gear units 210 The differential gear assembly 200 in parallel combination by interaxial parallel of the 210 'is used as the main shaft 40.

Correction Paper (Rule Article 91) One of the components 210 (differential A-axis DA, differential B-axis DB, pinion gear housing DP) is a drive input rotation part 41 of the main shaft 40, and another component [ Differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)] as the control rotation part 42 for shifting the main shaft 40, and any other component [differential A-axis (DA) , Differential B-axis (DB), pinion gear housing (DP)] is composed of the drive output rotation part 43 of the main shaft 40, the other differential gear unit (210 ^' ) used as the first sub-shaft (50); One component (differential A-axis (DA ^' ), differential B-axis (DB ^' ), pinion gear housing (DF;) as the input rotation part 51 of the first sub-shaft 50, and the other configuration Element [differential A-axis (DA ^' ), differential B-axis (DB'), pinion gear housing (DF :)] as the shift control rotation part 52 of the first sub-shaft 50, and any other component [ Gear A-axis (DA '), differential B-axis (DB ^' ), pinion gear housing (D;) ] Is constituted by the output rotation part 53 of the first sub-shaft 50, the rotational driving force (P) is applied to the drive input rotation part 41 of the main shaft 40, the input rotation part ( 51, a rotational driving force P is applied by the engagement of the main shaft 40 drive input rotational portion 41 and the different gears 44AK44B having a constant gear ratio, and the shift control rotation portion (1) of the first subshaft 50. 52 is coupled to the first control means (F1) having a control function is added, the output rotation part 53 of the first sub-shaft 50 is added to the second control means (F2) having another control function While being coupled to the drive gear control rotation part 42 of the main shaft 40 and the engagement of the different gear 44EX44D having a constant gear ratio.

Another differential gear assembly 200 'of the present invention in three rows is another differential gear unit which is used as the second sub-axis 60 in the two-gear differential gear assembly 200.

Correction Paper (Rule Article 91) (210 ') is a parallel combination by mutual axis parallelism, and one component of another differential gear unit 2 Γ used as the second sub-axis 60 (differential A-axis DA-, differential B-axis ( DB ") and the 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-) , The pinion gear housing (D :)] is the shift control rotation part 62 of the second sub-shaft 60, and any other component [differential A-axis (DA ^' ), differential B-axis (DB ^' ), pinion Gear housing (D :)] as an output rotating part (63) of the second sub-shaft (60), and the input rotating part (61) of the second sub-shaft (60) from the main shaft (40) driving input rotating part (41). The gears of the second sub-shaft 60 are coupled to the gears of different gears 4A, 44B, 44G, and 4G 'with a constant gear ratio, and the shift control rotary part 62 of the second subshaft 60 has different gear ratios. To engage the gear 44C '(44K') The first control means (F1) having a control function is provided, and the second control means (F2) having another control function is added to the output rotating portion (63) of the second sub-shaft (60), the first sub-shaft 50 is composed of a combination of the transmission control rotation part 52 and the gear of the different gears 44J 44H having a constant gear ratio.

The composite gear assembly 300 (300 ') of the present invention includes at least one planetary gear unit (ΙΙθΧΐΙό') 110- and at least one differential gear unit 210 (21 0 ') (210-). ) Are composed of parallel combinations of parallel axes, and the two-column composite gear assembly 300 is composed of 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 each component of any one differential gear unit (differential A-axis (Μ), differential B-axis (DB), pinion gear)

Correction Paper (Article 91) One component of the housing (DP) is the drive input rotation part 71 of the main shaft 70, and the other component (sun gear (S), ring gear (R), planetary gear carrier (C), or differential A). Shaft (DA), differential B-axis (DB), pinion gear housing (DP)] as control rotation part 72 for shifting 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 gear housing (DP)] as drive output rotation part 73 of main shaft 70, Any one of the other planetary gear units 11 0 ′ or differential gear units 210 ′ used as the first sub-axis 80 (sun gear S ^' , ring gear R ^' , planetary gear carrier ( ), Or differential A-axis (DA '), differential B-axis (DB'), pinion gear housing (DP ') as the input rotation part 81 of the first sub-axis (80), and the other component [sun gear ( S ^' ), ring gear (R'), planetary gear carrier (), or differential A-axis (DA ^' ), Differential B-axis (DB ^' ), pinion gear housing (DF)] 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';)]. Rotational driving force (P) is applied to the drive input rotational portion 71 of the main shaft 70, and the rotational driving force (P) is applied to the input rotational portion 81 of the first sub-axis (80) It is given by the engagement of the input gear 71 and the different gear 74AK74B having a constant gear ratio, the shift control rotary part 82 of the first sub-shaft 80 is the first control means (F1) having a control function Is added and coupled, and the output rotation part 83 of the first sub-shaft 80 is a control rotation part 72 for driving shift of the main shaft 70 with the addition of the second control means F2 having another control function. Wow Teeth of different gears (74EK74D) with constant gear ratio

Correction Paper (Article 91) It is a structure joined by a sum.

And another compound gear assembly 300 'of the present invention in three rows is another planetary gear unit (11 0') or differential gear unit used as the second sub-axis 90 in the two-gear composite gear assembly (300) Another planetary gear unit 11 (Γ) or a differential gear unit used as the second sub-axis 90, in which (2ΚΓ) is a parallel combination by parallel to each other.

One component of (210 ^' ) (sun gear (S ^* ), ring gear or), planetary gear carrier (cr), or differential A-axis (DA-), differential B-axis (DB-), pinion gear housing (DP ^' :)] as the input rotation part 91 of the second sub-axis 90, and the other components [sun gear (S'), ring gear (ΙΓ), planetary gear carrier (), or differential A-axis (DA ' ), Differential B-axis (DB ^' ), pinion gear housing (D :)] are the variable speed control rotation part 92 of the second sub-axis 90, and any other component [sun gear (S-), ring gear (ΙΓ), planetary gear carrier ((T), or differential A-axis (DA ^' ), differential B-axis (D B-), pinion gear housing (D)], the output rotation part 93 of the second sub-axis 90 In the input rotation part 91 of the second sub-shaft 90 is composed of a different gear (74A) (74B) (74G) (74G ') having a constant gear ratio from the main shaft 70 drive input rotation part (71). Coupled to a gear of rotation, and the control shift of the second auxiliary shaft (90) 92, the output rotating unit (93 different gear (74C ^{^') (7')} a first control means (F1) is be given, and the second minor axis 90, with the control by the engagement of with a constant gear ratio The second control means (F2) with another control function is added to the structure coupled to the engagement of the gear shifting control part 82 of the first sub-axis 80 and the different gear (74JK74H) having a constant gear ratio. It is.

Correction paper (rule 91) Exemplary embodiments of the present invention clearly showing the above configuration will be described in more detail based on the accompanying drawings.

<Example of a transmission using planetary gear assembly (ιοο) αοο ':) and two control means> Fig. La shows the gear assembly (a) of the present invention in two rows of planetary gear units (110) (110';). Is a cross-sectional view showing a coupling relationship according to the first embodiment of the planetary gear assembly (100) coupled to, Figure lb shows a coupling relationship according to the second embodiment of the planetary gear assembly (100) of the present invention. 1 is a cross-sectional view, and FIG. Lc shows a gear assembly (A) according to the third embodiment, which is formed of a planetary gear assembly 100 'coupled to three planetary gear units 110, 110' and 110 '. It is a cross-sectional view showing the coupling relationship.

First, as shown in FIG. La, the shift process of the transmission device using the planetary gear assembly 100 and two control means consisting of the planetary gear assembly 100 according to the first embodiment of the present invention will be described.

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

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, the rotation ratio (S: C: R) of each planetary gear unit is 5: 1: 1, the gear rotation ratio of 14A: 14B is 5: 1, and the 14C: 14K

Correction paper (rule 91) The gear rotation ratio is 1: 1, the gear rotation ratio of 14D: 14E is 1: 1, and the control ratio of F1 is a value for the rotational speeds of the first minor planetary gear and the sun gear, and the control ratio of F2 is the first minor planetary The numerical value of the rotation speed of a gear and a ring gear is shown. The main gear 10 of the planetary gear unit 110 has a drive input rotating part 11 of the main shaft 10 through which the variable power source VP, in which the rotational speed of the rotational power source P is varied, is transmitted through the main shaft 10. ) And the planetary gear carrier (C) is used as the shift control rotation part 12 of the main shaft 10 and the outer circumferential surface is geared with a constant gear ratio (14D). ), The ring gear (R) is used as the output rotation portion 13 of the main shaft (10).

The sun gear S 'of the first subshaft 20 and the planetary gear unit 110': is used as the input rotating portion 21 of the first subshaft 20, and is coupled to the gear 14B having a constant gear ratio. The planetary gear carrier () is used as the shift control rotary part 22 of the first subshaft 20 while receiving a control function from the first control means F1 by the engagement of the gears 14CX14K having different outer circumferential surfaces. , The ring gear R ': is received as another control function from the second control means F2 and used as the output rotation part 23 of the first subshaft 20, and is coupled with the gear 14E having a constant gear ratio. have.

Herein, the driving input rotation part 11 of the planetary gear unit 110 of the main shaft 10 may have different gears 14AX14B having a constant gear ratio with the input rotation part 21 of the planetary gear unit 110 ′ of the first subshaft 20. Is coupled by the teeth of the main shaft 10 planetary group

Correction Paper (Rule Article 91) The shift control rotation part 12 of the gear unit 110 is engaged with the output rotation part 23 of the planetary gear unit 110 'of the first subshaft 20 and the engagement of different gears 14D and 14E having a constant gear ratio. It is joined by.

At this time, the rotation ratio of each component of the main shaft (10) planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] and the first sub-axis (20) planetary gear unit (110 ^') The rotation ratio of each of the components [sun gear (S ^' ), ring gear (R ^' ), planetary gear carrier ()] is set to 5: 1: 1, and then the drive input rotation part of the main shaft 10 is rotated. The gear 14A built into the gear 11 and the gear 14B built into the input rotary part 21 of the first sub-shaft 20 have a gear ratio of 1: 1 and have a planetary gear unit 100 having a gear ratio of 1: 1. Set 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' at 1: 1, and the shaft is installed in the shift control rotation part 12 of the main shaft 10. The gear 14E built in the gear 14D and the output rotation part 23 of the first subshaft 20 has a gear ratio of 1: 1, and a planetary gear of the planetary gear unit 100 of the main shaft 10. Carrier (C) and First Shaft (20) The gear ratio with respect to the ring gear R 'of the planetary gear unit 100 ^' was set to 1: 1.

In addition, the first control means (F1) and the second control means (F2) to operate by receiving the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the spindle 10 ( 11) As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted from 700RPM to 3,500RPM, as shown in the following <Table 1>, the amount of change of rotational speed appearing in the output rotation part 13 of the main shaft 10 The result is a shift from '0' RPM to '700, RPM.

Correction Paper (Rule Article 91) That is, the transmission according to the first embodiment of the present invention rotates the input by a combination of gears in which at least one of the planetary gear units 110 (110 ':) of each of the components are parallel to each other in parallel. The speed range of the output rotational speed can be arbitrarily expanded, and the engine brake can be operated through two control means (stop mode) when a sudden braking is required, so that safety can be achieved during operation.

At this time, not limited to the above-described setting example of the present invention, if the structure of the coupling type, the control ratio of each control means, 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 within the scope.

※ Example of speed conversion (RPM)

Component 14D in Table 1 shows the theoretical value of the rotation ratio of the planetary gear unit 110 with respect to the input shaft 11 of the main shaft 10.

Correction Paper (Rule Article 91) Next, as shown in FIG. Lb, after setting the following <Setting Example 2> as a precondition 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.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpn, the rotational ratio (S: C: R) of each planetary gear unit is 5: 1: 1, and the gear rotation ratio of 14A: 1 ^ is 5: 1, and 14C: 14K. The gear rotation ratio of is 1: 1, the gear rotation ratio of 14D: 14E is 1: 1, and the control ratio of F1 is the number of revolutions of the first minor planetary gear and the sun gear, and the control ratio of F2 is the first minor axis. The number of revolutions of the planetary gear and the ring gear is shown. The main gear 10 of the planetary gear unit 110 includes a drive input rotating part 11 of the main shaft 10 through which the variable power source VP, in which the rotational speed of the rotational power source P is varied, is transmitted through the main shaft 10. ) Is combined with a gear 14A having a constant gear ratio, and the planetary gear carrier C is used as a shift control rotation part 12 of the main shaft 10, and the outer peripheral surface of the gear has a constant gear ratio 14D. ), The ring gear (R) is used as the output rotation portion 13 of the main shaft (10).

And the carrier gear (σ) of the first minor shaft 20 planetary gear unit (no ') is the first minor shaft

It is used as the input rotation part 21 of (20) and is combined with the gear 14B having a constant gear ratio, and the planetary gear sun gear S 'is formed by the engagement of different gears 14DK14K.

Correction Paper (Rule Article 91) It is used as the entire shift control assembly 22 of the first subshaft 20 while receiving a control function from the first control means Fl, and the ring gear R 'is another controller from the second control means F2. It is used as the output rotation part 23 of the first sub-shaft 20 by receiving the function.

Herein, the drive input rotation part 11 of the planetary gear unit 110 of the main shaft 10 may have different gears 14AK14B having a constant gear ratio with the input rotation part 21 of the planetary gear unit 110 ′ of the first subshaft 20. Coupled to each other, the shift control rotation part 12 of the planetary gear unit 110 of the main shaft 10 is a shift control rotation part 22 of the first part shaft of the planetary gear unit 110 'of the first sub shaft 20. ) And other gears (14EK14D) with a constant gear ratio are joined together.

At this time, the rotation ratio of each component of the main shaft (10) planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] and the first sub-axis (20) planetary gear unit (110 ^') ), The rotation ratio of each of the components [sun gear (S '), ring gear (R'), planetary gear carrier (;) is set to 5: 1: 1, and then 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 and the main shaft 10 of the planetary gear unit 100. Set the rotation ratio of the sun gear S and the first subshaft 20 to the carrier gear 100 of the planetary gear unit 100 'at 5: 1, The gear 14E built in the gear 14D and the output rotation part 23 of the 1st sub-shaft 20 set each gear ratio to 1: 1. In addition, after the first control means (F1) and the second control means (F2) to operate by the sense composed of clutch, disk plate and drum-type clutch, hydraulic internal gear pump,

Correction Paper (Rule Article 91) As a result of varying the initial minimum input rotation speed of the variable power source (VP) transmitted to the drive input rotation part 11 of the main shaft 10 from 700 RPM to 3,500 RPM, the output rotation part of the main shaft 10 as shown in Table 2 below ( The change in rotation speed shown in 13) is shifted from '0' RPM to '700' RPM.

That is, the transmission according to the second embodiment of the present invention rotates the input by a combination of gears in which at least one planetary gear unit 110 (110 ^' :) of the components are parallel to each other in parallel. The speed range of the output rotational speed can be arbitrarily extended, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.

The second embodiment is also not limited to the above configuration example, the structure of the combined form. If the control ratio of each control means, each gear ratio is arbitrarily changed, the transmission ratio corresponding to the corresponding combination conditions will appear, so that it can be variously implemented within the scope not departing from the technical spirit of the present invention.

«Example of Speed Conversion (RPM)

Correction Paper (Rule Article 91) Component S Transmission (RPM)

14A 700 800 900 1000 1500 2000 2500 3000 35∞

14B 140 160 180 200 300 400 500 600 700

14C 0 80 270 ∞ 825 1400 2250 3000 3500 Control

100% 90% 70% 60% 45% 30% 10% 0% 0% Fl

14E 140 144 126 120 135 120 50 0 0 Control rate

0% 10% 30% 40% 55% 70% 90% 100% 100% F2

14D 140 160 180 200 300 400 500 600 700

13 0 16 54 80 165 280 450 600 700 In Table 2, the element 14C represents the theoretical value of the rotation ratio of each planetary gear unit 110 with respect to the input electric charger 11.

Next, as shown in FIG. Lc, after setting the following <Preparation Example 3> as a precondition for explaining the shifting process according to the third embodiment using the planetary gear assembly 100 'of the present invention, The process of shifting the output rotation speed was examined.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700 rpm, and the rotation ratio (S: C: R) of each planetary gear unit is 4: 1: 1. The gear rotation ratio of 14A: 14B is 1: 1, the gear rotation ratio of 14G: 14G ^' is 1: 1, the gear rotation ratio of 14C ^' : 14K ^' is 1: 1, and the gear rotation ratio of 14J: 14H is 1. 1: 1, 14E: 14D gear ratio is 1: 1, the control ratio of F1 is the number of revolutions of the first minor planetary gear and the sun gear, the control ratio of F2 is the first minor planetary gear and the ring The numerical value of the rotation speed of a gear is shown. The sun gear S of the main shaft 10 and the planetary gear unit 110 has a rotational speed of the rotational power source P.

Correction Paper (Rule Article 91) Variable variable power source (VP) is used as the drive input rotating part 11 of the main shaft 10 transmitted through the main shaft 10, 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, the outer peripheral surface is coupled to the gear 14D having a constant gear ratio with the gear, the ring gear (R) is used as the output rotation portion 13 of the main shaft 10 do. The sun gear S 'of the first subshaft 20 and the planetary gear unit 110' is used as the input rotation part 21 of the system 1 subshaft 20 and is coupled with a gear 14BK14G having a constant gear ratio. The gear carrier C is used as the shift control rotation part 22 of the first subshaft 20, and the outer circumferential surface thereof is coupled to the gear 14J having a constant gear ratio, and the ring gear R ^' is the first subshaft. It is used as the output rotation part 23 of the 20 and is coupled with the gear 14E having a constant gear ratio.

On the other hand, the sun gear S 'of the second subshaft 30 planetary gear unit 11 (Γ :) is used as an 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 is shifted on the second subshaft 30 while receiving a control function from the first control means F1 by the engagement of the gears 14C (14Κ ^' ) with different peripheral surfaces. It is used as the control rotation part 32, the ring gear 0Γ is received as another control function from the second control means (F2) is used as the output rotation part 33 of the second sub-shaft 30, the gear having a constant gear ratio It is combined with 14H.

Here, the drive input rotation part 11 of the main shaft 10 planetary gear unit 110 is a low U

Correction paper (rule 91) The shaft 20 is coupled to the input rotation part 21 of the planetary gear unit 110 'by the engagement of different gears 14AK14B having a constant gear ratio, and the shift control of the planetary gear unit 110 of the main shaft 10 is carried out. The rotating part 12 is coupled by engagement of the output rotating part 23 of the planetary gear unit 110 'of the first subshaft 20 with different gears 14EK14D having a constant gear ratio.

The input rotating part 21 of the first gear shaft 20 and the planetary gear unit 110 'has a different gear 14G having a constant gear ratio from the input rotating part 31 of the planetary gear unit 1ΚΓ. 14G ') is coupled to each other, and the shift control rotation part 22 of the first subshaft 20 and the planetary gear unit 110' is the output rotation part of the planetary gear unit 110 'of the second subshaft 30. 33) and the other gears (14JK14H) with a constant gear ratio are engaged.

At this time, the rotation ratio of each component of the main shaft (10) planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] and the first sub-axis (20) planetary gear unit (110 ^') Of each component [sun gear (S '), ring gear (R'), planetary gear carrier (;) and each component of planetary gear unit ai (r :) S ^' ), the planetary gear carrier (C ") and the ring gear (ΙΓ)] are all set to 4: 1: 1, and then the gears built up on the drive input rotation part 11 of the main shaft 10 ( 14A) and gears 14A and 14B built into the input rotating part 21 of the first subshaft 20 and the input rotating part 31 of the second subshaft 30. 14G) and 14G 'are all gear ratios of 1: 1 to 1: 1, and the sun gear S of the main shaft 10 planetary gear unit 110 and the first minor shaft 20 planetary gear unit 110 ^'

Correction paper (rule 91) The gear ratio of the gear S 'and the second subshaft 30 to the sun gear s- of the planetary gear unit ii (r) is set to 1: 1: 1, and the shift control rotation part of the main shaft 10 is set. The gear 14D built into the gear 12D and the gear 14E built into the output rotating part 23 of the first subshaft 20 set the gear ratio to 1: 1, and the gear 14D of the first subshaft 20 The gear 14H built in the speed change control rotating section 22 and the gear 14H built in the output rotating section 33 of the second sub shaft 30 set the gear ratio to 1: 1.

In addition, after the first control means (F1) and the second control means (F2) all clutches, disc plate and drum-type clutch, hydraulic internal gear pump round, the drive input rotation part of the main shaft (10) As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted from (11) from 700RPM to 4,000RPM, as shown in Table 3 below, the rotational speed of the output rotation part 13 of the main shaft 10 The change resulted in a shift from '0' RPM to '1,000' RPM.

«Example of Speed Conversion (RPM)

Correction paper (rule 91) In Table 3, the component 14D is geared to the driving input rotation part 11.

The theoretical value with respect to the rotation ratio of 14D is shown, and the control ratio of the 1st control means F1 is a theoretical value rotation ratio of the gear 14C 'with respect to the rotation ratio of the input rotation part 31 of the 2nd sub-axis 110'. The control ratio of the second control means F2 represents the control ratio with respect to the theoretical value rotation ratio of the gear 14J with respect to the rotation ratio of the entire input rotation 21 of the first sub-axis 110 '.

That is, the transmission in accordance with the third embodiment of the present invention is a parallel combination by engaging each gear such that each component of at least three or more planetary gear units 110K110 'and 110 ": is parallel to each other. The range of shift of the output rotational speed to the input rotational speed can be arbitrarily extended, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.

At this time, the present invention is not limited to the above-described setting examples, and if the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear, without departing from the technical spirit of the present invention. Of course, it can be variously performed within the scope.

<Embodiment of Transmission Device Using Differential Gear Coupler 200 (200 ') and Two Control Means> FIG. 2A shows that the gear combiner (A) of the present invention comprises two rows of differential gear units 210 (210 ^' ).

Correction Paper (Rule Article 91) A coupling cross-sectional view showing a coupling relationship according to a fourth embodiment of the differential gear coupling body 200 coupled to FIG. 2b shows a coupling relationship according to a fifth embodiment of the differential gear coupling body 200 of the present invention. Fig. 2C shows a sixth embodiment in which the gear assembly (A) consists of a differential gear assembly (200 ^' :) in which three gear arrays (210) (210') and 210 "are coupled to each other. Is a cross-sectional view showing the coupling relationship according to

First, as shown in FIG. 2A, a shift process of a transmission apparatus using two control means and a differential gear assembly 200 including a differential gear assembly 200 according to a fourth embodiment of the present invention 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.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, the rotational ratio of each part of each differential gear unit is DP X 2 = DA + DB, the gear rotation ratio of 4A: 44B is 2: 1, and the gear rotation ratio of 44C: is 1: 1. , 44D: The gear rotation ratio of 44E is 1: 1, the control ratio of F1 is the value for the first sub-axis differential gear and the pinion housing rotation speed, and the control ratio of F2 is the rotational speed of the first sub-axis differential gear and the differential B axis The numerical value is shown. The differential A axis (DA) of the main shaft (40) and the differential gear unit (210) has

Correction Paper (Rule Article 91) Variable variable power source (VP) is used as the drive input rotation part 41 of the main shaft 40 transmitted through the main shaft 40, and is coupled with the gear 44A having a constant gear ratio, and the pinion gear housing (DP) Is used as the shift control rotation part 42 of the main shaft 40, and is coupled with the gear 44D having a constant gear ratio, and the differential B axis DB is used as the output rotation part 43 of the main shaft 40. do.

The differential A-axis DA 'of the differential gear unit 210 ^' of the first sub-shaft 50 is used as the input rotation part 51 of the first sub-shaft 50 and is coupled with 44B having a constant air ratio. And the pinion gear housing D is used as the entire shift control assembly 52 of the first sub-shaft 50 while receiving a control function from the first control means F1 by the engagement of the different gears 44CK44K. , The axle shaft DB '> receives another control function from the second control means F2 and is used as the output rotation part 53 of the first subshaft 50, and is coupled with the gear 44E having a constant gear ratio. Here, the drive input rotational portion 41 of the differential gear unit 210 of the main shaft 40 has a different gear 44AK4 having a constant gear ratio with the input rotational portion 51 of the differential gear unit 210 'of the first sub-axis 50. B) coupled to each other, the shift control rotary part 42 of the main shaft 40 differential gear unit 210 is the first Shaft 50 is coupled over thing by the coupling of the differential gear unit (210 ') the output rotation part 53 and the different gear (44DK44E) with a constant gear ratio.

At this time, each component of each differential gear unit (210K210 ^' ) [differential A-axis (DA, D

Correction paper (rule 91) Α ^' ), differential B-axis (DB, DB'), pinion gear housing (DP, DF)] to [pinion housing (DP) X2 = differential A-axis (DA) + differential B-axis (DB)] After setting so that the gear 44A and the gear 44B built into the drive input rotating part 41 of the main shaft 40 and the input rotating part 51 of the first subshaft 50 are With a gear ratio of 1: 2, the rotation ratio of the differential A-axis DA of the primary synchronous gear unit 210 of the main shaft 40 and the differential A-axis DA ^' of the differential gear unit 210 ^{' of} the first sub-axis 50 is fixed. Is set to 2: 1, and the gear 44E built in the speed change control rotating part 42 of the main shaft 40 and the gear 44E built in the output rotating part 53 of the first subshaft 50 are The gear ratio was 1: 1 and the rotation ratio was set to 1: 1.

In addition, the first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (40). As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted to (41) from 700RPM to 3,500RP, the variation in the rotational speed appearing in the output rotation part 43 of the main shaft 40 as shown in Table 4 below. The result is a shift from the '0' RPM to the '3,500' RPM. That is, the transmission according to the fourth embodiment of the present invention has an input rotational speed in parallel combination by engaging each gear such that each component of at least one or more differential gear units 210, 210 ^' is parallel to each other. It is possible to arbitrarily expand the speed range of the output rotational speed of the engine, and the engine brake is operated through two control means (stop mode) to ensure safety during operation.

Correction Paper (Rule Article 91) All.

The fourth embodiment is also not limited to the above-described setting example, and if the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously performed as long as it does not deviate.

«Example of Speed Conversion (RPM)

Component 44D in Table 4 shows the theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation part 41.

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, We looked at the transmission process of the train.

Here, the preconditions are as follows.

The rotation speed of P1 is 700rpm, the rotation ratio of each part of each differential gear unit is DP X 2 = DA + DB, the gear reduction ratio of 4A: 44B is 4: 1, and the gear rotation ratio of 44D: 44E is fixed paper. (Rule 91) It is 1: 1, and the control ratio of Fl is the numerical value for the electromagnetism of the first sub-axis differential gear and the differential A axis, and the control ratio of F2 is the numerical value for the rotational speed of the first sub-axis differential gear and the differential B axis. The differential A-axis DA of the differential gear unit 210 of the main shaft 40 has a drive input rotation of the main shaft 40 through which the variable power source VP whose rotational speed of the rotational power source P1 is varied is transmitted through the main shaft 40. It is used as part 41 and is coupled to the gear 44A having a constant gear ratio, and the pinion gear housing DP is used as the shift control rotation part 42 of the main shaft 40 and the gear 44D having a constant gear ratio. The differential B axis DB is used as the output rotation part 43 of the main shaft 40.

The pinion gear housing <DP 'of the first subshaft 50 and the differential gear unit 210': is used as the input rotation part 51 of the first subshaft 50, and is coupled with the gear 44B having a constant gear ratio. The differential A-axis DA ^' is used as the shift control rotation part 52 of the first sub-shaft 50 while receiving a control function from the first control means F1. Another control function is transmitted from the second control means (F2) is used as the output rotation portion 53 of the first sub-shaft 50 is coupled to the gear 44E having a constant gear ratio. Here, the drive input rotation part 41 of the main shaft 40 differential gear unit 210 may have different gears 44AK44B having a constant gear ratio with the input rotation part 51 of the first sub-shaft 50 differential gear unit 210 '. The main shaft 40 differential is coupled by the

Correction Paper (Rule Article 91) The shift control rotation part 42 of the gear unit 210 is coupled to the output rotation part 53 of the first sub-shaft 50 differential gear unit 210 ^' by engagement of different gears 44DK44E having a constant gear ratio. have.

In this case, the rotation ratio of each component of the differential gear units 210 and 210 ^' (the teeth "A-axis (DA.DA'), the differential B-axis (DB, DB ') and the pinion gear housing (DP, DP')] is determined. After setting the pinion housing (DP) X2 = differential A-axis (DA) + differential B-axis (DB)], the gear 44A built in the drive input rotation part 41 of the main shaft 40 is mounted. ) And the gear 44B arranged on the input rotation part 51 of the first subshaft 50 have a gear ratio of 1: 4 and the differential A axis DA of the main synchronous unit 210 of the main shaft 40. The rotation ratio with respect to the pinion gear housing DP ^'of the first sub-shaft 50 differential gear unit 210 ^' is set to 4: 1, and is built up in the shift control rotation section 42 of the main shaft 40. The gear 44E built in the gear 44D and the output rotation part 53 of the first sub-shaft 50 has a gear ratio of 1: 1 so that the pinion gear housing (DP) of the differential shaft unit 210 of the main shaft (40). And first auxiliary shaft (50) differential gear unit (210 ') Was set to one: the rotation rate of the differential axis B (DB ^') 1.

In addition, the first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump and the like, and then the drive input rotation part of the main shaft (40). As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted from (41) from 700 RPM to 3,500 RPM, as shown in the following <Table 5>, the amount of change in the rotation speed appearing in the output rotation part 43 of the main shaft 40 The result is a shift from the '0' RPM to the '3,500' RPM.

Correction Paper (Rule Article 91) That is, the transmission device according to the fifth embodiment of the present invention outputs the input rotational speed by a combination of gears in which at least one of the components of the at least one differential gear unit 210K210 'is parallel to each other. The speed range of rotation can be arbitrarily extended, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.

The fifth embodiment is also not limited to the above-described setting example. If the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously performed as long as it does not deviate.

«Example of Speed Conversion (RPM)

In Table 5, the component 44D represents a theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation part 41.

Next, as shown in Figure 2c, the precondition for explaining the shifting process according to the sixth embodiment using the differential gear assembly 200 'of the present invention is the following correction paper (rule 91) After setting <Example 6>, the shift process of the output rotation speed was examined.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, the rotational ratio of each of the differential gear units is DP X 2 = DA + DB, the gear rotation ratio of 44A: 44B is 1: 1, and the gear rotation ratio of 44G: 4G ^' is 1: 1, the gear rotation ratio of 44C ^' : 44K ^' is 1: 1, the gear rotation ratio of 44J: 44H is 1: 1, and the gear rotation ratio of 4E: 44D is 1: 1. In addition, the control value of F1 represents the value for the rotational speed of the first sub-axis differential gear and the pinion housing, and the control rate of F2 represents the value for the rotational speed of the first sub-axis differential gear and the differential B-axis. The differential A-axis DA of the differential gear unit 210 of the main shaft 40 has a drive input rotating part of the main shaft 40 through which the variable power source VP, in which the rotational speed of the rotational power source P is varied, is transmitted through the main shaft 40. It is used as (41) and is coupled to the gear (44A) having a constant gear ratio, the pinion gear housing (DP) is used as the shift control rotation part 42 of the main shaft (40), and has a constant gear ratio (44D) The differential B-axis (DB) is used as the output rotation portion 43 of the main shaft (40).

And the differential A-axis (DA ^' :) of the differential gear unit (210') of the first sub-shaft (50) is used as the input rotation part 51 of the first sub-shaft (50) and is coupled with the gear (44BK44G) 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 D

Correction Paper (Rule Article 91) P ^' ：) is used as the output rotation part 53 of the first sub-shaft 50 and has a constant gear ratio.

It is coupled with (44E). On the other hand, the differential A-axis DA ^'of the second sub-axis 60 differential gear unit 2ΚΓ is coupled with the gear 44G ^' having a constant gear ratio, and the pinion gear housing D has different gears (D). 44C) is used as the shift control rotation part 62 of the second sub-shaft 60 while receiving the control function from the first control means F1 by the engagement of the 44 ^' ), and the differential B-axis D is the second It receives another control function from the control means F2 and 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.

Here, the drive input rotational portion 41 of the main shaft 40 differential gear unit 210 may have different gears 44AK44B having a constant gear ratio from the input rotational portion 51 of the first minor shaft 50 differential gear unit 210 '; ), And the shift control rotation part 42 of the main shaft 40 differential gear unit 210 is connected to 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 (44EX4 D) with a constant gear ratio.

The input rotational portion 51 of the differential gear unit 210 'of the first subshaft 50 has a different gear 44GK44 having a constant gear ratio with the input rotational portion 61 of the differential gear unit 2 Γ of the second subshaft 60. The shift control rotation part 52 of the first sub-shaft 50 differential gear unit 210 ^' is coupled by a coupling of G ^' :), and the output of the second sub-shaft 60 differential gear unit (2 Γ;) It is coupled by the engagement of the rotating part 53 and the different gears 44JX44H having a constant gear ratio.

Correction Paper (Rule Article 91) At this time, the rotation ratio of the components [differential A-axis DA, differential B-axis, pinion gear housing DP] of the main gear 40 differential gear unit 210 and the first sub-shaft 50 differential gear Components of the unit 21 0 ^' [differential A-axis (DA ^' ), differential B-axis (DB '), pinion gear housing (D :)] Stone rotation ratio and second sub-axis (60) differential gear unit (210 The rotation ratios for each of the components [Differential A-axis (DA), Differential B-axis (DB-), Pinion gear housing (D :)] are all [Pinion gear housing (DP) X2 = Differential A-axis ( DA) + differential B-axis (DB)], and then to the input rotation part 51 of the gear 44A and the first sub-shaft 50 built in the drive input rotation part 41 of the main shaft 40. The gear 44G 'built on the input rotation part 61 of the gear 44BK44G and the second subshaft 60 both have the gear ratio of 1: 1: 1 and the primary synchronous unit 210 of the main shaft 40 Differential A-axis (DA) and first sub-axis (50) differential gear unit 210 ^'(and type 2, a minor axis 60, the differential all the rotation rate of the differential Α axes ^(DA') of the gear unit (21 (Γ) 1 differential A axis DA) of the "1: 1 set, and the The gear 44D built into the speed control rotation part 42 of the main shaft 40 and the gear 44E built into the output rotation part 53 of the first subshaft 50 set the gear ratio to 1: 1. The gear 44J built on the shift control rotation part 52 of the first subshaft 50 and the gear 44H built on the output rotation part 63 of the second subshaft 60 have a gear ratio of 1: 1. Set to.

In addition, the first control means (F1) and the second control means (F2) are operated by the clutch disk plate, the drum-type clutch, the hydraulic internal gear pump and the like, and then the drive input rotating part ( 41), the initial minimum input rotation speed of the variable power source (VP) transmitted to the variable from 700 RPM to 3,500 RPM, as shown in Table 6, the main shaft (40)

Correction Paper (Rule Article 91) The amount of change in the number of revolutions appearing on the output rotation part 43 of the range from 0 to 3,500

The result is a shift to RPM.

»Speed Conversion Example (RPM)

In Table 6, the component 44D represents a theoretical value of the rotational ratio of the gear 44D to the drive input rotational unit (4DDML rotational speed), and the control rate of the first control means F1 is the second sub-axis 210. Is the control rate with respect to the theoretical value rotation ratio of the gear 44C ^' with respect to the rotation speed of the input rotation part 61 of';^' , and the control rate of the 2nd control means F2 is the input rotation of the 1st subshaft 210 ^' ; The control ratio with respect to the theoretical value rotation ratio of the gear 44J with respect to the rotation speed of the whole 51 is shown.

That is, in the transmission according to the sixth embodiment of the present invention, at least three or more differential gear units 210, 210 ^′ , 210 ′ are paralleled by the engagement of respective gears such that the respective axes are parallel to each other. Combination can extend the speed range of output rotation to input speed arbitrarily, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made. Paper (rule 91) will be.

In this case, the sixth embodiment is also not limited to the above-described setting example, and when the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the gear ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously performed as long as it does not deviate from the idea.

<Embodiment of Transmission Device Using Combined Gear Combiner 300 (300 ') and Two Control Means> Fig. 3A shows a planetary gear unit in which the gear combiner (A) of the present invention is used as the main shaft 70 ( 110 is a coupling stage diagram showing a coupling relationship according to the seventh embodiment of the composite gear coupling body 300 in which any one differential gear unit 210 ^' used as the first auxiliary shaft 80 is coupled. 3B is a cross-sectional view showing a coupling relationship according to the eighth embodiment of the composite gear assembly 300 of the present invention, and FIG. 3C shows a first differential gear unit 210 and a first differential gear unit 210 used as the main shaft 70. 3 is a cross-sectional view showing a coupling relationship according to the ninth embodiment of the composite gear assembly 300 in which any one planetary gear unit 110 ^′ used as the minor axis 80 is coupled. Coupling cross section showing a coupling relationship according to the tenth embodiment of the coupling body 300 A.

First, as shown in FIG. 3A, a shift process of a transmission apparatus using two control means and a compound gear assembly 300 according to the seventh embodiment of the present invention will be described.

Correction Paper (Rule Article 91) After setting the following <Setting Example 7> as a prerequisite for explaining the shifting process according to the seventh embodiment using the composite gear assembly 300 of the present invention, the shifting process of the output rotation speed was examined.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, and the rotational ratio (S: C: R) of the planetary gear unit is 5: 1: 1, and the rotation ratio of each of the differential gear unit is DP X .2 = DA + DB, 74A : The gear rotation ratio of 74B is 5: 1, the gear rotation ratio of 74E: 74D is 1: 1, and the gear rotation ratio of 74C: 74K is 1: 1. In addition, the control rate of F1 represents a numerical value for the rotational speed of the first sub-axis pinion gear and the housing, and the control rate of F2 represents a numerical value for the first sub-axis difference synchronizing gear and the differential B-axis rotational speed. The sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70. And the planetary gear carrier (C) is combined with the gear 74D having the constant gear ratio while being used as the shift control rotation part 72 of the main shaft 70. 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-axis 80 is used as the input dropping portion 81 of the first sub-axis 80 and is coupled with a gear 74B having a constant gear ratio. ,

Correction Paper (Rule Article 91) The pinion gear housing D is used as the shift control rotary part 82 of the first sub-shaft 80 while receiving a control function from the first control means F1 by engagement of different gears 74CK74K having a constant gear ratio. The differential B-axis DB 'receives another control function from the second control means F2 and is used as the output rotation part 83 of the first sub-shaft 80 and has a constant gear ratio 74E. Are combined. Herein, the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 7 AX74B having a constant gear ratio from the input rotation part 81 of the differential gear unit 210 'of the first sub-axis 80. ), And the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 is fixed to the output rotation part 83 of the differential gear unit 210 'of the first sub-axis 80. The gears are engaged by the engagement of the different gears 74DK74E.

At this time, the rotation ratio of each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] is set to 5: 1: 1 and the first sub-shaft (80) The rotation ratio of each component [differential A-axis (DA '), differential B-axis (DB'), and pinion gear housing (DF;) of the differential gear unit (210 ') is represented by [Pinion gear housing]. 2 = differential A-axis (DA ^' ) + differential B-axis (DB ^' )], and then the gear 74A and the first sub-axis (80A) built in the drive input rotation part 71 of the main shaft 70. The gear 74B built in the input rotation part 81 of the main shaft (81) 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 210 of the first sub-axis 80. the rotation rate of the ^"a differential shaft ^(DA's)") of 5:

Correction Paper (Rule Article 91) It is set to 1, and the gear 74E built in the speed control rotation part 72 of the main shaft 70 and the gear 74E built in the output rotation part 83 of the first subshaft 80 have a gear ratio of 1. The rotation ratio of the planetary gear carrier C of the main shaft 70 planetary gear unit 110 and the differential B-axis (DB ^' :) of the first sub-axis 80 and the differential gear unit 210 ^' is 1 :. Set to 1.

In addition, the first control means (F1) and the second control means (F2) are operated by the clutch, the disk tube and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70). As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted from (71) from 700RPM to 3,500RPM, as shown in Table 7 below, the amount of change of rotational speed appearing in the output rotation part 73 of the main shaft 70 The result is a shift from the '0' RPM to the '700' RPM.

That is, the transmission device according to the seventh embodiment of the present invention is a component of any one planetary gear unit 110 used as the main shaft 70, and any one used as the first auxiliary shaft 80 Parallel combinations of gears that allow each component of the differential gear unit (210 ':) to be parallel to each other to make it possible to arbitrarily expand the transmission range of the output speed to the input speed as well The engine brake is operated through two control means (stop mode) to ensure safety during operation.

The seventh embodiment is also not limited to the above-described setting example, and if the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Get out

Correction Paper (Rule Article 91) Of course, it can be variously performed as long as it does not.

※ Example of speed conversion (RP)

Component 74D in Table 7 shows the theoretical value of the rotation ratio of the planetary gear unit 110 with respect to the input rotation part 71.

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.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is TOOrpm, and the rotational ratio (S: C: R) of the planetary gear unit is 5: 1: 1, and the rotational ratio of each of the differential gear unit is DP X 2 = DA + DB, 74A ： The gear rotation ratio of the 74B is 10: 1, and the gear rotation ratio of the 74E: 74D is 1: 1. In addition, the control rate of F1 represents the number of revolutions of the first sub-differential gear and the differential A-axis, and the control rate of F2 represents the number of revolutions of the first sub-differential gear and the differential B-axis.

Correction Paper (Rule Article 91) Indicates. The sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70. And the planetary gear carrier (C) is combined with the gear 74D having the constant gear ratio while being used as the shift control rotation part 72 of the main shaft 70. The ring gear R is used as the output rotation portion 73 of the main shaft 70. The pinion gear housing (DF :) of the first sub-axis (80) of the differential gear unit (210 ^' ) is used as the input rotating portion (81) of the first sub-axis (80) and is coupled with a gear (74B) having a constant gear ratio. The differential A-axis DA 'is used as the shift control rotation part 82 of the first sub-axis 80 while receiving the control function from the first control means F1, and the differential B-axis DB ^' is the second control. It receives another control function from the means F2 and is used as the output rotation part 83 of the first sub-shaft 80 and is coupled with a gear 74E having a constant gear ratio.

Here, the drive input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 74AX74B having a constant gear ratio from the input rotation part 81 of the differential gear unit 210 ': of the first sub-axis 80. ), And the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 has a constant gear ratio with the output rotation part 83 of the differential gear unit 210 ^′ of the first sub-shaft 80. By engagement of different gears (74DX74E) with

Correction Paper (Rule Article 91) Are combined.

At this time, the rotation ratio of each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] is set to 5: 1: 1 and the first sub-shaft (80) Set the rotation ratio of each component [differential A-axis (DA '), differential B-axis (DB' :), pinion gear housing (DF) of the differential gear unit (210 ';) to [pinion gear housing (DF). ) X 2 = Differential A-axis (DA ^' ) + Differential B-axis (DB' :)], and then the gear 74A and the first gear 74 which are built up in the drive input rotation part 71 of the main shaft 70. The gear 74B built in the input rotation part 81 of the subordinate shaft 80 has a gear ratio of 1:10 so that the sun gear S of the planetary gear unit 110 of the main shaft 70 and the first subordinate shaft 80 are differential. The rotation ratio of the gear unit 210 ': to the pinion gear housing (DF) is set to 10: 1, and the gear 74D and the first gear set in the shift control rotation part 72 of the main shaft 70 are rotated. It is built in the output rotation part 83 of the sub-shaft 80 The gear 74E has a gear ratio of 1: 1, and the differential B-axis of the planetary gear carrier C of the main shaft 70 and the planetary gear unit 100 and the differential gear unit 210 'of the first sub-axis 80. The rotation ratio for (DB ^' ) was set to 1: 1.

In addition, the first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70). As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted from (71) from 700RPM to 3,500RPM, as shown in <Table 8>, the change amount of rotational speed appearing in the output rotation part 73 of the main shaft 70 as shown in Table 8 below. The result is a shift from the '0' RPM to the '700' RPM.

Correction Paper (Rule Article 91) That is, the transmission device according to the eighth embodiment of the present invention is a component of any one planetary gear unit 110 used as the main shaft 70, and any one used as the first auxiliary shaft 80 Parallel combinations of gears, which allow the components of the differential gear unit 210 'to be parallel to each other, make it possible to arbitrarily expand the shift range of the output rotational speed to the input rotational speed, as well as to request sudden braking. The engine brake is activated through two control means (stop mode) to ensure safety during operation.

The eighth embodiment is not limited to the above-described setting example, but if the structure of the coupling type, the shift control ratio of each shifting means, and the gear ratio are arbitrarily changed, the shift ratio corresponding to the corresponding coupling condition will appear. Of course, it can be variously performed as long as it does not deviate from the idea. <Table 8>

※ Example of speed conversion (RPM)

In Table 8, the component 74D represents a theoretical value of the rotation ratio of the planetary gear unit 110 to the input rotation unit 71.

Next, as shown in Fig. 3b-1, the composite gear assembly 300 of the present invention is fixed (Article 91). After setting <setting example 9> as a prerequisite for explaining the shifting process according to the ninth embodiment using the following, the shifting process of the output rotation speed was examined.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpffl, and the rotation ratio (S: C: R) of the planetary gear unit is 5: 1: 1, and the rotation ratio of each unit of the differential gear unit is DP X 2 = DA + DB, 74A ： The gear rotation ratio of the 74B is 2.5: 1, and the gear rotation ratio of the 74D: 74E is 1.4: 1. In addition, the control rate of F1 represents the number of revolutions of the first sub-axis differential gear and the differential A-axis, and the control rate of F2 represents the number of revolutions of the first sub-axis differential gear and the differential B-axis. The sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70. And the planetary gear carrier (C) is combined with the gear 74D having the constant gear ratio while being used as the shift control rotation part 72 of the main shaft 70. The ring gear R is used as the output rotation portion 73 of the main shaft 70.

The pinion gear housing DP 'of the first subshaft 80 differential gear unit 210 ^' is used as the input rotation part 81 of the first subshaft 80 and is coupled with a gear 74B having a constant gear ratio. And the differential A-axis DA ^' receives the control function from the first control means F1.

Correction Paper (Rule Article 91) Used as the shift control rotation part 82 of the first sub-shaft 80, the differential B-axis (DB ':) receives another control function from the second control means (F2) output shaft of the first sub-shaft (80) It is used as (83) and is coupled with a gear (74E) with a constant gear ratio.

Herein, the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 74AK74B 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, the shift control rotation part 72 of the main shaft 70 planetary gear unit 110 has a constant gear ratio with the output rotation part 83 of the differential gear unit 210 ': of the first sub-shaft 80. The gears are coupled by the engagement of the different gears (74DX74E).

At this time, the rotation ratio of each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] is set to 5: 1: 1 and the first sub-shaft (80) The rotation ratios of the components [differential A-axis (DA ^' ), differential B-axis (DB ^' ), and pinion gear housing (D) of the differential gear unit 210 'are determined as [pinion gear housing (D). X 2 = differential A-axis (DA ^' ) + differential B-axis (DB ^' ;)], and the gear 74A and the first sub-shaft built into the drive input rotation part 71 of the main shaft 70. The gear 74B built in the input rotation part 81 of the 80 has a gear ratio of 1: 2.5 and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the differential gear of the first subshaft 80. The rotation ratio of the pinion gear housing DF of the unit 210 ^' is set to 2.5: 1, and the gear 74D and the first subshaft 80, which are built up in the shift control rotation part 72 of the main shaft 70, are rotated. In the output rotation part 83 of And the planetary gear carrier (C) of 1.4 and a main shaft 70, the planetary gear unit 100 includes: a gear (74E) has a gear ratio 1

Correction Paper (Rule Article 91) The rotation ratio with respect to the differential B-axis DB ^' of the 1st sub-axis 80 differential gear unit 210' was set to 1.4: 1.

In addition, the first control means (F1) and the second control means (F2) to operate by receiving the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump and the like, and then the first control means (F1) The initial minimum input rotational speed of the variable equal power source (VP) transmitted to the drive input rotation part 71 of the main shaft 70 with a specific rotational speed of 75% at the initial control rate was changed from 700RPM to 3,500RPM. As shown in Table 9, the variation in the number of revolutions appearing in the output rotation part 73 of the main shaft 70 is shifted from '0' RPM to '1,680' RPM.

In other words, the transmission in accordance with the ninth embodiment of the present invention is any one differential used as each of the components of one planetary gear unit ₁₁₀ used as the main shaft 70 and the first sub-axis (80) Parallel combinations of gears that allow each component of the gear unit 2 T to be parallel to each other can be arbitrarily extended to shift the output rotational speed to the input rotational speed. The engine brake is activated through the control means (stop mode) to ensure safety during operation.

The ninth embodiment is also not limited to the above-described setting example, and when the structure of the coupling type, the shift control ratio of each shifting means, and each gear ratio are arbitrarily changed, the shift ratio corresponding to the corresponding coupling condition will appear. Of course, it can be variously performed as long as it does not deviate from the idea.

Jeong, Jeong-Won (Regulation Article 91) TABLE 9

Speed Conversion Example (RPM)

In Table 9, the component 74D represents the theoretical value of the rotation ratio of the gear 74D to the rotational speed of the drive input rotation part 71 of the main shaft 110, and the first control means F1 The control rate shows the control rate with respect to the theoretical value rotation ratio of the differential A-axis with respect to the rotation speed of the input rotation part 81 of the 1st sub-axis 210 '.

Next, as shown in Figure 3c, after setting the following <Setting Example 10> as a prerequisite for explaining the shifting process according to the seventh embodiment using the composite gear assembly 300 of the present invention, the output rotation We looked at the number shifting process.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpn, the rotational ratio (S: C: R) of the planetary gear unit is 4: 1: 1, and the rotational ratio of the differential gear unit is DP X 2 = M + DB, 7 A : The gear rotation ratio of 74B shall be 1: 1, and the gear rotation ratio of 74D: 74E shall be 2: 1.

Correction Paper (Rule Article 91) The gear rotation ratio of 74C: 74K is 1: 1. In addition, the control ratio of F1 represents the numerical value for the rotational speed of the first minor shaft planetary gear and the carrier gear, and the control ratio of F2 represents the numerical value of the rotational speed of the first minor shaft planetary gear and the ring gear. The differential A-axis DA of the differential gear unit 210 of the main shaft 70 has a drive input rotating part of the main shaft 70 through which the variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70. It is used as a 71 and is coupled with a gear 74A having a constant gear ratio, and the pinion gear housing DP is used as a shift control rotation part 72 of the main shaft 70 and has a constant gear ratio 74D. The differential B-axis (DB) is used as the output rotation portion 73 of the main shaft (70).

The sun gear S ^′ of the first subshaft 80 and the planetary gear unit 110 ^′ is used as the input arm portion 81 of the first subshaft 80 and is coupled with a gear 74B having a constant gear ratio. The gearbox carrier () is used as the shift control rotary part 82 of the first sub-shaft 80 while receiving a control function from the first control means pi by the engagement of different gears 74CK74K having a constant gear ratio. The ring gear R 'receives another control function from the second control means F2 and is used as the output rotation part 83 of the first sub-shaft 80, and is coupled with the gear 74E having a constant gear ratio. .

Herein, the driving input rotation part 71 of the differential gear unit 210 of the main shaft 70 has different gears 74AX74B having a constant gear ratio with the input rotation part 81 of the planetary gear unit 110 ^′ of the first sub-axis 80. The main shaft 70 differential

Correction Paper (Rule Article 91) The shift control rotation part 72 of the gear unit 210 is engaged by engaging the output rotation part 83 of the planetary gear unit 110 ^′ of the first subshaft 80 with different gears 74DK74E having a constant gear ratio. It is.

At this time, the ratio of each component [differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)] of the differential gear unit 210 of the main shaft (70) is [pinion gear housing (DP) X 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 carriers (=) is set to 4: 1: 1, and the gear 74A and the first subshaft 80, which are built up in the drive input rotation part 71 of the main shaft 70, respectively. The gear 74B built in the planetary gear unit 110 'input rotation part 81 of the differential gear unit 210 has a gear ratio of 1: 1 and the differential A-axis DA and the first sub-axis of the differential gear unit 210 of the main shaft 70. (80) The gear 74D built in the shift control rotation part 72 of the main shaft 70 by setting the rotation ratio with respect to the sun gear S ^' : of the planetary gear unit 1 T :. Rotation of output of planetary gear unit 110 'with first subshaft 80 The gear 74E built in the portion 83 has a gear ratio of 1: 2 and the pinion gear housing DP of the differential gear unit 210 of the main shaft 70 and the planetary gear unit 110 'of the first subshaft 80. The rotation ratio with respect to the ring gear R 'of;) was set to 2: 1.

In addition, the first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, and the like. As a result of varying the initial minimum input mission number of the variable power source (VP) transmitted to all 71 from TOORPM to 3,500 RPM, as shown in <Table 10>

Correction Paper (Rule Article 91) The change in the number of revolutions appearing in the output rotation unit 73 of 70 resulted in a shift from '0' RPM to '3,500' RPM.

That is, the transmission device according to the tenth embodiment of the present invention is a component of any one differential gear unit 210 used as the main shaft 70, any one used as the first sub-axis (80) Parallel combinations of gears that make the components of the planetary gear unit 110 ^' make parallel to each other are able to arbitrarily expand the speed range of the output rotational speed to the input rotational speed, as well as demanding braking. The engine brake is activated through the main control means (stop mode) to ensure stability during operation.

The tenth embodiment is also not limited to the above configuration example, the structure of the combined form. If the control ratio of each control means, each gear ratio is arbitrarily changed, the speed ratio corresponding to the corresponding combination conditions will appear, so that various modifications can be made within the scope without departing from the technical spirit of the present invention.

Table 10

»Speed conversion example (RB0

Correction Paper (Rule Article 91) Component 74D in Table 10 shows the theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation unit 71.

Next, as shown in Figure 3d, after setting the following <Setting Example 11> 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.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, the rotational ratio (S: C: R) of the planetary gear unit is 3: 1: 1, and the rotational ratio of each of the differential gear unit is DP X 2 = DA + DB, 7 A : The gear rotation ratio of 74B is 2: 1, the gear rotation ratio of 74E: 74D is 1: 1, and the gear rotation ratio of 74C: 74K is 1: 1. In addition, the control ratio of F1 represents a numerical value based on the first minor shaft planetary gear and the sun gear rotational speed, and the control ratio of F2 represents a numerical value for the first minor shaft planetary gear and the ring gear rotational speed. The differential A-axis (M) of the differential gear unit (210) of the main shaft (70) has a drive input rotating part of the main shaft (70) through which a variable power source (VP) whose rotational speed of the rotating power source (P) is varied is transmitted through the main shaft (70). It is used as a 71 and is coupled with a gear 74A having a constant gear ratio, and the pinion gear housing DP is used as a shift control rotation part 72 of the main shaft 70 and has a constant gear ratio 74D. The differential B-axis (DB) is used as the output rotation portion 73 of the main shaft (70).

Correction Paper (Rule Article 91) A first minor axis 80, the planetary gear unit (110; group control with a constant gear ratio as used to ^") the planetary gear carrier () has a first minor axis 80, the planetary gear unit (110 of" input rotation part 81 of) ( 74B), the sun gear (S ^' :) is coupled to the gear (74C) having a constant gear ratio and the transmission control rotary part of the first sub-axis (80) while receiving a control function from the first control means (F1) Ring gear (R ^' ) is coupled to the gear (74E) having a constant gear ratio and receives the control function from the second control means (F2) (82), the output rotation part 83 of the first sub-shaft (80) Is used.

Herein, the drive input rotation part 71 of the differential gear unit 210 of the main shaft 70 may have different gears 7 AX74B having a constant gear ratio with the input rotation part 81 of the planetary gear unit 110 ′ of the first sub-axis 80. ) Is coupled to each other, and the shift control rotation part 72 of the main gear 70 differential gear unit 210 is constant with the output rotation part 83 of the planetary gear unit 110 'of the first sub-shaft 80. The gears are coupled by the engagement of different gears 74E and 74D with gear ratios.

At this time, the ratio of each component [differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)] of the differential gear unit 210, [pinion gear housing (DP)] X 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 planetary gear carriers ()] are set to 3: 1: 1, and then the gear 74A and the first subshaft 80 which are arranged on the drive input rotation part 71 of the main shaft 70 are rotated. The gear 74B built in the drive input rotation part 81 of the main shaft 70 has a gear ratio of 1: 2 and is equal to the differential A axis DA of the differential gear unit 210 of the main shaft 70.

Correction Paper (Rule Article 91) The gear 74D which is built up in the shift control rotation part 72 of the main shaft 70 by setting the rotation ratio with respect to the sun gear S ^' of the first sub-axis 80 and the planetary gear unit 110 ^' at 2: 1. And the gear 74E built in the output rotation portion 83 of the first gear shaft 80 and the planetary gear unit 110 ': have a gear ratio of 1: 1. The rotation ratio with respect to the ring gear R ^' of the pinion gear housing DP and the 1st shaft 80 planetary gear unit 110' was set to 1: 1.

In addition, the first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70). As a result of varying the initial minimum input rotation speed of the variable power source (VP) transmitted from (71) from 700 RPM to 3,500 RPM, the change amount of rotation speed displayed on the output rotation part 73 of the main shaft 70 as shown in Table 11 below. The result is a shift from the '0' RPM to the '3,500' RPM.

That is, the transmission device according to the eleventh embodiment of the present invention is a component of any one differential gear unit 210 used as the main shaft 70, any one used as the first sub-axis (80) Parallel combinations of gears that make the components of the planetary gear unit 110 'make parallel to each other are able to arbitrarily extend the shift range of the output electromagnetism with respect to the input rotational speed, as well as when braking is required. The engine brake is activated through two control means (stop mode) to ensure safety during operation.

The eleventh embodiment is also not limited to the above configuration example, the structure of the coupling form ，

Correction Paper (Rule Article 91) If the control ratio and each gear ratio of each control means is arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear, so that various modifications can be made within the scope without departing from the technical spirit of the present invention.

TABLE 11

«Example of speed change (RP)

In Table 11, the component 74D represents a theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation unit 71.

Next, as shown in Figure 4a, 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 process of shifting the output rotation speed was examined.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, the ratio of the gears of the planetary gear units (S: C: R) is 5: 1: 1, and the rotation ratio of each gear of the differential gear units is DP X 2 = DA + DB. , 74A: The gear rotation ratio of 74B is 5: 1, and the gear rotation ratio of 74G: 7G ^' is 1: 1.

Correction Paper (Rule Article 91) The gear rotation ratio of 74C ': 74K' is 1: 1, the gear rotation ratio of 7 J: 74H is 1: 1, and the gear rotation ratio of 74E: 74D is 1: 1. In addition, the control rate of F1 represents the number of revolutions of the first sub-axis differential gear and the pinion housing, and the control rate of F2 represents the number of revolutions of the first sub-axis differential gear and the differential B-axis. The sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70. And the planetary gear carrier (C) is combined with the gear (74D) having a constant gear ratio while being used as the shift control rotary part (72) of the main shaft (70). 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-axis 80 is used as the input rotation part 81 of the first sub-axis 80 and is coupled with a gear 74BX74G having a constant gear ratio. ， The pinion gear housing DF is used as the shift control rotation part 82 of the first subshaft 80 and is coupled with the gear 74J having a constant gear ratio, and the differential B axis DB ^′ is the first subshaft 80. It is used as the output rotation part 83 of the) and is coupled with the gear 74E having a constant gear ratio.

On the other hand, the differential A-axis DA 'of the second sub-axis 90 and the differential gear unit 210-: is used as the input rotation part 91 of the second sub-axis 90 and is coupled with the gear 74G ^' having a constant gear ratio. And the pinion gear housing (DP-) is driven by the engagement of the different gears (74C ^' ) (74Κ ^' ).

Correction Paper (Rule Article 91) It is used as the shift control rotation part 92 of the second sub-shaft 90 while receiving the control function from the female 1 control means F1, and the differential B-axis D: is made from the second control means F2. Received the fish function is used as the output rotation part 93 of the second sub-shaft 90 is coupled to the gear (74H) having a constant gear ratio.

Here, the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 7 AK74B having a constant gear ratio with the input rotation part 81 of the differential gear unit 210 ^′ of the first sub-axis 80. ), And the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 has a constant gear ratio with the output rotation part 83 of the differential gear unit 210 ^′ of the first sub-shaft 80. The gears are coupled by the engagement of the different gears (74EX74D).

The input rotational portion 81 of the differential gear unit 210 'of the first sub-axis 80 has a different gear 74G having a constant gear ratio with the input rotational portion 91 of the differential gear unit 210' of the second sub-axis 90. (7 G ^' ) is coupled by the coupling, the shift control rotary portion 82 of the first sub-axis (80) differential gear unit (21 0 ^' ) is the output of the second sub-axis (90) differential gear unit 210 ' It is coupled by the engagement of the rotary part 93 and the different gears 74JK74H having a constant gear ratio.

At this time, the rotation ratio of each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] is set to 5: 1: ί and the first sub-shaft ( 80) Components of the differential synchronous unit 210 ': [Differential A-axis (DA'), Differential B-axis (DB ') 니 Pinion gear housing (DF)] Stone rotation ratio and second differential gear unit ( Each component of 210 ·) [Differential A-axis (D

Correction Paper (Rule Article 91) A ^" ), differential B axis (DB-), and pinion gear housing (D :)] are all [pinion gear housing (DP) X 2 = differential A axis (DA) + differential B axis (DB) ] To the gear 74B built in the drive input rotation part 71 of the said main shaft 70, and the gear 74B built in the input rotation part 81 of the 1st subshaft 80. The input gear part 91 of the gear 74G and the second sub-shaft 90 differential gear unit 210 ^' , which are arranged on the input rotation part 81 of the first sub-shaft 80, with a gear ratio of 1: 5. The gear ratio of the gear (74G ^' ) built into the gear set to 1: 1, and the sun gear (S) and the first sub-axis (80) of the planetary gear unit (110) of the main shaft (70) and the differential gear unit (210'). Set the rotation ratio of the differential A-axis (DA ^' ) to 5: 1 and set the differential A-axis (DA') and the second sub-axis (90) of the differential gear unit (210) of the secondary shaft (80) to the differential gear unit (210). Set the rotation ratio for the differential A-axis (DA ') of The gear 74E built in the shift control rotation part 72 of the main shaft 70 and the gear 74E built in the output rotation part 83 of the first subshaft 80 have a gear ratio of 1: 1. The gear 74H set in the gear 74J and the output circuit 93 of the second subshaft 90 and the gear 74J arranged in the shift control rotation part 82 of the first subshaft 80 set the gear ratio. 2: 1 was set.

In addition, the first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70). As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted to (71) from 700 RPM to 3,500 RPM, as shown in Table 12, the rotation speed of the rotational speed appearing in the output rotation portion 73 of the main shaft (70) The amount of change was shifted from '0' RPM to '700' RPM.

Correction Paper (Rule Article 91) <Table 12>

Speed Conversion Example (RPM)

In Table 12, the component 74D represents a theoretical value of the rotation ratio of the gear 74D to the rotation speed of the drive input rotation part 71 of the main shaft 110, and the first control means F1 The control rate is the control rate with respect to the theoretical value rotation ratio of the gear 74C with respect to the rotation speed of the input rotation part 91 of the 2nd sub-axis 210 ': The control rate of the 2nd control means F2 is 1st.

The control ratio with respect to the theoretical value rotation ratio of the gear 74J with respect to the rotation speed of the input rotation part 81 of the sub-axis 210 ': is shown.

That is, the transmission device according to the twelfth embodiment of the present invention is a component of any one planetary gear unit 110 used as the main shaft 70, and any one used as the first sub-axis (80) Input rotational speed in parallel combination by meshing each gear such that the components of the second differential gear unit 2ΚΓ used as the first differential gear unit 210 'and the second secondary shaft 90 are parallel to each other. In addition, the speed range of output rotation can be arbitrarily expanded, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved. Correction Paper (Rule Article 91) The twelfth embodiment is also not limited to the above-described setting examples, and when the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition is shown. Of course, it can be variously carried out within the scope not departing.

Next, as shown in Figure 4b, after setting the following <Setting Example 13> as a prerequisite for explaining the shifting process according to the twelfth embodiment using the composite gear assembly (300 ^' ) of the present invention, The process of shifting the output rotation speed was examined.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, the rotational ratio (S: C: R) of each planetary gear unit is 4: 1: 1, and the rotational ratio of each differential gear unit is DP X 2 = DA + DB, 74A : The gear rotation ratio of 74B is 4: 1, the gear rotation ratio of 74G: 74G ^' is 2: 1, the gear rotation ratio of 74C': 74K 'is 1: 1, and the gear rotation ratio of 74J: 74H is 1. The gear rotation ratio of 74E and 74D is 1: 1. In addition, the control rate of F1 represents the number of revolutions of the first sub-axis differential gear and the differential A-axis, and the control rate of F2 represents the number of revolutions of the first sub-axis differential gear and the differential B-axis. The sun gear S of the main shaft 70 of the planetary gear unit 110 includes a drive input arm portion of the main shaft 70 through which the variable power source VP whose rotational speed of the rotation power source P is varied is transmitted through the main shaft 70 ( 71), combined with a gear (74A) with a constant gear ratio,

Correction Paper (Rule Article 91) The gear gear carrier C is used as the shift control rotation part 72 of the main shaft 70 and is coupled with the gear 74D having a constant gear ratio, and the ring gear R is the output rotation part 73 of the main shaft 70. Used as

The differential A-axis DA 'of the first sub-axis 80 and the differential gear unit 210' is used as an input rotation part 81 of the first sub-axis 80 and is coupled with a gear 74BK74G having a constant gear ratio. The pinion gear housing DF is used as the shift control rotation part 82 of the system 1 sub-axis 80 and is coupled with the gear 74J having a constant gear ratio, and the differential B-axis DB ^'is connected to the first sub-axis ( It is used as an output rotation part 83 of 80 and is coupled with a gear 74E having a constant gear ratio.

On the other hand, the pinion gear housing (D :) of the second sub-axis (90) differential gear unit 21 (Γ :) is used as the input rotation part 91 of the second sub-shaft 90 and has a gear 74G 'having a constant gear ratio. The differential A-axis DA ^* is coupled to the shift control of the second sub-axis 90 while receiving a control function from the first control means F1 by the engagement of the different gears 74C ^' and 74Κ ^' . It is used as the rotating part 92, the differential Β-axis (DB-) is received as another control function from the second control means (F2) and used as the output rotating part 93 of the second sub-shaft (90) while maintaining a constant gear ratio Coupled with an excitation gear (74Η).

Herein, the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 74ΑΚ74Β 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, and the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 outputs the differential gear unit 210 'of the first sub shaft 80.

Correction Paper (Rule Article 91) The rotation 83 is engaged by the engagement of the different gears 74EK74D with a constant gear ratio.

The input rotation part 81 of the first sub-shaft 80 differential gear unit 210 'is different from the input rotation part 91 of the second sub-axis 90 differential gear unit 210 · with a different gear 74G. (74G ';) coupled to each other, the shift control rotation portion 82 of the first sub-axis (80) differential gear unit (21 0 ^' i) is the output rotation of the second sub-axis (90) differential gear unit (2ΚΓ) And 93 are engaged by engagement of different gears 74J and 74H with a constant gear ratio.

At this time, the rotation ratio of each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] is set to 4: 1: 1: 1 and the first sub-shaft ( 80) Rotation ratio and second sub-axis 90 of each component [： lower A axis DA ', differential B axis DB', pinion gear housing DP ') of the differential synchronous unit 210'. Rotation ratios for each component of the differential gear unit 21 (Γ) [differential A-axis (DA-), differential B-axis (Ι) Β ·), pinion gear housing (D;)] (DP) X 2 = Differential A-axis (DA) + Differential B-axis (DB)], and the gear 74A and the first part built up in the drive input rotation part 71 of the main shaft 70. The gear 74B built in the input rotation part 81 of the shaft 80 has a gear ratio of 1: 4, and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the differential gear of the first sub-shaft 80. Set the rotation ratio with respect to the differential A axis DA 'of the unit 210' to 4: 1, The gear 74G built on the input rotating part 81 of the first subshaft 80 and the gear 74G 'built on the shift control rotating part 92 of the second subshaft 90 have a gear ratio of 1: 2. Differential shaft unit (80)

Correction paper (rule 91) Pinion gear housing of differential A-axis (DA ':) and second sub-axis (90)

The speed control rotation part of the main shaft 70 by setting the rotation ratio with respect to DP ';

The gear 74D built in the 72 and the gear 74D built in the output rotation part 83 of the first subshaft 80 set the gear ratio to 1: 1, and the speed change of the first subshaft 80. Control part

The gear 74H built in 82 and the gear 74H built in the output rotation part 93 of the 2nd sub-shaft 90 set the gear ratio to 1: 1. In addition, the first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70). As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted from (71) from 700 PM to 3,500 RPM, it appears in the output rotation portion 73 of the main shaft 70, as shown in Table 13 below. The result is that the amount of rotation changes from '0' RPM to '875' RPM.

Table 13

»Speed Conversion Example (RPM)

Correction Paper (Rule Article 91) In Table 13, the component 74D represents a theoretical value of the rotation ratio of the gear 74D to the rotational speed of the drive input dielectric unit 71 of the main shaft 110, and the first control step F1. ) Is a control rate with respect to the theoretical value rotation ratio of the gear 74C with respect to the rotation speed of the input rotation part 91 of the 2nd subshaft 210 '; The control rate of the 2nd control means F2 is a control rate of the 1st subshaft ( The control ratio with respect to the theoretical value rotation ratio of the gear 74J with respect to the rotation speed of the input rotation part 81 of 210 'is shown. That is, the transmission device according to the thirteenth embodiment of the present invention is a component of any one planetary gear unit 110 used as the main shaft 70, and any one used as the first auxiliary shaft 80 Compound parallelism by the engagement of the gears in which the components of the second differential gear unit 21 (Γ) used as the first differential gear unit 210 'and the second sub-axis 90 are parallel to each other. In addition, the speed range of the output rotation to the input rotation can be arbitrarily expanded by the combination, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety can be achieved during operation. The thirteenth embodiment of the present invention is also not limited to the above-described setting example, and when the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the gear ratio corresponding to the corresponding combination condition is shown. Of course, it can be variously performed as long as it does not deviate from the technical spirit of the.

Next, as shown in Figure 4c, the preconditions for explaining the shifting process according to the thirteenth embodiment using the composite gear assembly (300 ^' ) of the present invention as follows:

Correction Paper (Rule Article 91) After setting <setting 14>, the shift process of the output rotation speed was examined.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, and the rotation ratio (S: C: R) of each planetary gear unit is 5: 1: 1, and the rotation ratio of each unit of the differential gear unit is Iff X 2 = DA + DB, 74A : The gear rotation ratio of 74B is 1: 1, the gear rotation ratio of 74G: 74G ^' is 5: 1, the gear rotation ratio of 74C': 74K 'is 1: 1, and the gear rotation ratio of 74J: 74H is 1. The gear rotation ratio of 74E: 74D is 1: 1. In addition, the control rate of F1 represents the number of revolutions of the second sub-axis differential gear and the pinion housing, and the control * of F2 represents the number of revolutions of the first sub-axis differential gear and the differential B-axis. The sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70. And the planetary gear carrier (C) is combined with the gear (74D) having a constant gear ratio while being used as the shift control rotary part (72) of the main shaft (70). The ring gear R is used as the output rotation portion 73 of the main shaft 70.

The sun gear S 'of the first subshaft 80 and the planetary gear unit 110' is used as an input rotation part 81 of the first subshaft 80 and is coupled with a gear 74BK74G having a constant gear ratio. The gear carrier () is used as the shift control portion 82 of the first sub-axis (80).

Correction Paper (Rule Article 91) The outer circumferential surface thereof is coupled to the gear 7 j having a constant gear ratio, and the ring gear R 'is used as the output rotation part 83 of the first sub-shaft 80 and has a constant gear ratio 74E. Combined with.

On the other hand, the differential A-axis DA- of the differential gear unit 21 (Γ) of the second sub-axis 90 is used as the input rotation part ₉₁ of the second sub-axis 90 and has a gear 74G 'having a constant gear ratio. And the pinion gear housing DP- is shifted on the second axle 90 while receiving a control function from the first control means F1 by engagement of different gears 74C ^' (74Κ ^' :). It is used as the control rotation unit 92, the differential Β-axis (DB-) is received as another control function from the second control means (F2) used as the output rotation portion 93 of the second sub-axis 90, the constant gear ratio Is combined with a gear (74Η).

Here, the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 74ΑΚ74Β having a constant gear ratio with the input rotation part 81 of the first sub-axis 80 planetary gear unit 110 '. Coupled to each other, the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 has a constant gear ratio with the output rotation part 83 of the planetary gear unit 110 'of the first sub-shaft 80. The different gears (74EK74D) with the teeth are engaged by the teeth.

The input rotation part 81 of the first sub-axis 80 planetary gear unit 110 'is different from the input rotation part 91 of the second sub-axis 90 differential gear unit 210': different gears having a constant gear ratio 74GK74G. Coupled to each other, and the shift control rotation part 82 of the first sub-axis 80 and the planetary gear unit 11 0 ^′ is the output of the second sub-axis 90 and the differential gear unit 210 ·.

Correction Paper (Rule Article 91) And 93 are engaged by engagement of different gears 74J and 74H with a constant gear ratio.

In this case, each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear 00, planetary gear carrier (C)] and each of the first sub-axis 80, planetary gear unit (110 ^' ) The ratio of the element [sun gear (S '), ring gear (R'), planetary gear carrier (：)] is set to 5: 1: 1, and each component of the second sub-axis 90 differential gear unit 21CT is constructed. Rotation ratio for the elements [Differential A-axis (DA ^* ), Differential B-axis (Ι Β ·), Pinion gear housing (D;)] [Pinion gear housing (DP) X 2 = Differential A-axis (DA) + Differential B-axis (DB)], and the gears are arranged in the gear 74A and the input rotation part 81 of the first sub-shaft 80 and the gear 74A built in the drive input rotation part 71 of the main shaft 70. 74B sets the gear ratio to 1: 1, and is built in the gear 74G and the input rotation part 91 of the 2nd subshaft 90 which are built in the input rotation part 81 of the 1st subshaft 80. As shown in FIG. gear (74G ^') has a gear ratio of 1: 5 to Sun gear S of the planetary gear unit 110 and the sun gear S of the planetary gear unit 110 'of the first sub-axis 80 and the second sub-axis 90 of the planetary gear unit 110 and the differential shaft unit 210-; Of the gear 74D and the first subshaft 80, which are set in the shift control rotation section 72 of the main shaft 70, with a rotation ratio of the differential A-axis (DA ^* ;) set to 5: 5: 1. 74E built on the output rotating unit 83 sets the gear ratio to 1: 1, and the gear 74J and the second subshaft 90 built on the shift control rotating unit 82 of the first sub-axis 80. The gear ratio 74H built in the output rotation part 93 of the wheel) is set at a gear ratio of 1: 1.

In addition, the first control means (F1) and the second control means (F2) are operated by receiving a sense.

Correction Paper (Rule Article 91) The initial minimum input speed of the variable power source (VP) transmitted to the drive input rotation part 71 of the main shaft 70 after being composed of a clutch, a disk plate and a drum type clutch, a hydraulic internal gear pump, and the like, is 700 RPM to 3,500 RPM. As a result of varying, as shown in Table 14 below, the amount of change in the number of revolutions appearing in the output rotation part 73 of the main shaft 70 is shifted from '0' RPM to '700' RPM.

«Speed conversion example

In Table 14, the component 74D represents a theoretical value of the rotation ratio of the gear 74D to the rotation speed of the drive input rotation part 71 of the main shaft 110, and the first control step F1. The control rate of is the control rate with respect to the theoretical value rotation ratio of the gear 74C ^' with respect to the rotation speed of the input rotation part 91 of the 2nd subshaft 21 (Γ;), and the control rate of the 2nd control means F2 is the 1st subshaft The control ratio with respect to the theoretical value elimination ratio of the gear 74J with respect to the rotation speed of the input rotation part 81 of (210 ^' :) is shown.

That is, the transmission device according to the fourteenth embodiment of the present invention is a fixed paper used as the main shaft 70 (rule 91) Each of the components of the first planetary gear unit 110 and any one of the second planetary gear unit 110 ′ used as the first sub-axis 80 and the second sub-axis 90. It is possible to arbitrarily extend the shift range of the output rotational speed with respect to the input rotational speed by the combination of the combinations of the gears which make each component of the differential gear unit 210 · be parallel to each other. Of course, when braking is required, the engine brake is operated through the two control means (stop mode) to ensure safety during operation.

The fourteenth embodiment is also not limited to the above-described setting examples. If the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously carried out within the scope not departing.

Next, as another embodiment of FIG. 4C, after setting the following <Setting Example 15>, the following prerequisites for explaining the shifting process according to the thirteenth embodiment using the composite gear assembly 300 'of the present invention are outputted. We looked at the speed change process.

Here, the preconditions are as follows.

The minimum rotational speed of P1 is 700rpm, the rotational ratio (S: C: R) of each planetary gear unit is 5: 1: 1, and the rotational ratio of each unit of the differential gear unit is DP X 2 = DA + DB, 74A : The gear rotation ratio of 74B is 1: 1, the gear rotation ratio of 74G: 74G ^' is 2: 1, the gear reduction ratio of 74C': 74K ^' is 1: 1, and the gear rotation ratio of 74J: 74H is 1. 1: 1

Correction Paper (Rule Article 91) 74E: The gear ratio of the 74D is 1: 1. In addition, the control rate of F1 represents a value for the rotational speed of the first sub-axis difference synchronizing gear and the pinion housing, and the control rate of F2 represents the rotational speed value for the first sub-axis differential gear and the differential B axis. The sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70. And the planetary gear carrier (C) is combined with the gear (74D) having a constant gear ratio while being used as the shift control rotary part (72) of the main shaft (70). The ring gear R is used as the output rotation portion 73 of the main shaft 70. And the sun gear (S ^' ) of the first sub-axis (80) planetary gear unit (110') is coupled to the gear (74BK74G) having a constant gear ratio when used as the input rotation portion 81 of the first sub-axis (80), The planetary gear carrier () 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 the first sub-shaft. It is used as the output rotation portion 83 of the 80 and is engaged with the gear 74E having a constant gear ratio.

Meanwhile, the differential A-axis DA- of the second sub-axis 90 and the differential gear unit 2ΚΓ is used as the input rotation part 91 of the second sub-axis 90, and is coupled with a gear 74G ^' having a constant gear ratio. And the pinion gear housing (DP ^* ) is driven by the engagement of different gears (74C ^' ) (74Κ ^' )

Correction Paper (Rule Article 91) By using the control function from the first control means (F1) is used as the shift control rotation part 92 of the second sub-axis 90, the differential B-axis) is another control function from the second control means (F2) Received and used as the output rotating part 93 of the second sub-shaft 90 is coupled to the gear (74H) having a constant gear ratio.

Here, the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 7 AK74B having a constant gear ratio from the input rotation part 81 of the first sub-axis 80 planetary gear unit 110 ^′ . ) Is coupled to each other, and the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 is fixed to the output rotation part 83 of the planetary gear unit 110 ': of the first sub-axis 80. The gears are coupled by the engagement of the different gears (7 EK74D).

The input rotation part 81 of the first sub-axis 80 planetary gear unit 110 'is different from the input rotation part 91 of the second sub-gear 90 90 differential gear unit 210. (74G ') is coupled by a coupling, and the shift control rotary part 82 of the first sub-axis 80 planetary gear unit (110' :) output of the second sub-axis (90) differential gear unit (2ΚΓ) It is coupled by the engagement of the rotary part 93 and the different gears 7 JK74H 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 of the components [sun gear (S ^' ), ring gear (R'), planetary gear carrier (;) is set to 5: 1: 1 and the second sub-axis 90 differential gear unit (210 ^* :) Each component of [Differential A-axis (DA-),

Correction Paper (Rule Article 91) [Pinion Gear Housing] can be used to set the rotation ratio for the differential B-axis (Dr) and pinion gear housings (Dr :)].

(DP) X 2 = Differential A-axis (DA) + Differential B-axis (Iffi)], and the gear 74A and the first sub-shaft built in the drive input rotation part 71 of the main shaft 70. The gear 74B built in the input rotation part 81 of the 80 sets the gear ratio to 1: 1, and the gear 74B built in the input rotation part 81 of the 1st subshaft 80 and the 2nd The gear 74G ^{′ installed} in the input rotation part 91 of the subordinate shaft 90 has a gear ratio of 1: 2, and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the planetary body of the first subordinate shaft 80 are formed. Set the rotation ratio of the sun gear S ^' of the gear unit 110 ^' and the differential A-axis DA ^* of the second sub-axis 90 and the differential gear unit 210 ': to 2: 2: 1, To the shift control rotation part 72 of (70). 74E built in the gear 74D and the output rotation part 83 of the 1st subshaft 80 set the gear ratio to 1: 1, and the shift control rotation part 82 of the said 1st subshaft 80 is established. ), The gear 74J built on the gear 74J and the gear 74H built on the output rotating part 93 of the second sub-shaft 90 set the gear ratio to 1: 1. Further, the first control answer F1 and the second control means F2, which are operated under the sense, are constituted by a clutch, a disk plate and a drum type clutch, a hydraulic internal gear pump, and the like. As a result of varying the initial minimum input rotational speed of the variable power source (VP) transmitted to the drive input rotation part 71 of the main shaft 70 from 700RPM to 3,500RPM with a specific rotational speed with an initial control rate of 75%. As shown in Table 9, the amount of change in the electrolyzed water appearing in the output rotation part 73 of the main shaft 70 is changed from '0' RPM to '1,300' RPM.

Correction Paper (Rule Article 91) The result is shifted to.

Table 15

»Speed conversion example

In Table 15, the component 74D represents a theoretical value of the rotation ratio of the gear 74D to the rotation speed of the drive input rotation part 71 of the main shaft 110, and the first control step F1. The control rate of is the control rate with respect to the theoretical value rotation ratio of the gear 7 C ': with respect to the rotation speed of the input rotation part 91 of the 2nd sub-axis (2Γ :), and the control rate of the 2nd control means F2 is 1st The control ratio with respect to the theoretical value rotation ratio of the gear 74J with respect to the rotation speed of the input rotation part 81 of the sub-axis 210 ': is shown.

That is, the transmission device according to the fifteenth embodiment of the present invention is any one used as each of the components of the first planetary gear unit 110 and the first sub-shaft 80 used as the main shaft (70). Compound parallel combination by engaging each gear such that the components of any one differential gear unit 210 · used as the second planetary gear unit 110 ′ and the second sub-axis 90 are parallel to each other. Paper of output rotational speed with respect to input rotational speed (Rule Article 91) The speed range can be arbitrarily extended, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.

The fifteenth embodiment is also not limited to the above-described setting example, and when the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously carried out within the scope not departing.

[Industrial availability]

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 speed range ranging from the low speed range and high speed range, various embodiments of the gear assembly Therefore, it is possible to easily realize a large reduction ratio with a simple structure, so that the field of application has a great effect that can be applied to various types of transmission including a gear reducer and also for automobile and industrial use.

In particular, in the case of a vehicle transmission, the engine power is transmitted to the gear assembly, thereby maximizing the engine efficiency in the power transmission process, thereby reducing the fuel cost, and achieving a very large reduction ratio with a simple structure and making the volume of the gear assembly compact. Since it can be manufactured, it is possible to reduce the manufacturing cost significantly, such as to have a very economical effect.

Correction Paper (Rule Article 91)

Claims

[Claim]

[Claim 1]

In a transmission using a gear unit, each component of the at least one planetary gear unit (110) (110 ') (11 (Γ) [sun gear (S) (S') (S '), ring gear (R) (R ') (R ") and planetary gear carriers (C) () (C;)] are such that the planetary gear units 110K110 ^' (11 (Γ :) are parallel to each other by means of gear gears. Planetary gear assembly (ιοο) αοο ^' combined in parallel,

Each component [Differential A-axis (DAKDA ') (DA'), Differential B-axis (DB) (DB ^' ) (DB ^' ), Pinion for at least one differential gear unit (210X210 ') (210') Gear housing (DP) (DP ') (DP ")] is a differential gear assembly 200 in which each differential gear unit 210, 210 ^' , 210 ^" is combined in parallel so as to be parallel to each other by a gear tooth. (200 ^' ),

Each component for at least one planetary gear unit (110) (110 ') (110') [sun gear (S) (S ') (S "), ring gear (RKR ^' KR-), planetary gear carrier (C) () (C)] and each component [differential A-axis (DAKDA ^' ) (DA ") for the at least one differential gear unit (210) (210') (210 '), differential B-axis ( DBKDB ') (DB') and Pinion Gear Housings (DPKD F) (DP- :)] are at least one differential with at least one planetary gear unit 110, 110 ', 110' The gear assembly with the gear ratio extended by the parallel combination of the mutually parallel axes of the compound gear assembly 300 (300 ^' ) formed by combining the gear units 210, 210', and 210 "in parallel to each other. phrase

Correction paper (rule 91) The planetary gear assembly 100 of the gear assembly includes any one component of the planetary gear unit 110 used as the main shaft 10 (sun gear (S), ring gear (R), planetary gear carrier (C)). ) As the drive input rotation part 11, and other components [sun gear (S), ring gear (R), planetary gear carrier (C)] as the shift control rotation part (12). One planetary gear unit 110 ^′ composed of the components [sun gear S, ring gear R, planetary gear carrier C] with a drive output rotating part 13 and used as the first sub-shaft 20. ) [Sun gear (S '), ring gear (R'), planetary gear carrier ()] of the first sub-shaft (20) input rotating part (21), and other components (sun gear (S) '), Ring gear (R'), planetary gear carrier ()] are coupled to the first sub-axis (20) shift control rotating section (22) by the first control means (F1), and another component [sun gear ( S '), ring gear (R'), Planetary gear carrier (;)] is configured to receive a control function by combining the second control means (F2) to the output rotation unit 23 of the first sub-shaft 20 two control means characterized in that Transmission using gear and gear assembly.

[Claim 2]

2. The variable input power source (VP) according to claim 1, wherein, during the configuration of the planetary gear assembly (100) constituting the gear assembly, the drive input rotating portion (11) of the main shaft (10) is variable in the rotational speed of the rotational power source (P). Alternatively, a constant power source (FP) with a constant rotational speed is transmitted through the main shaft (10) and is coupled with a gear (14A) with a constant gear ratio, and the shift control rotation part (12) of the main shaft (10) has a gear with a constant gear ratio. 14D, the input rotational portion 21 of the first sub-shaft 20 is coupled to the gear 14B having a constant gear ratio.

Correction Paper (Rule Article 91) The shift control rotation part 22 of the first subshaft 20 receives a control function and is coupled to the first control means F1 by engagement of different gears 14C and 14K. The output rotation part 23 of the 20 is coupled to the gear 14E having a constant gear ratio while receiving another control function from the second control means F2, but the drive input rotation part of the main shaft 10 11) and the input rotation part 21 of the first sub-shaft 20 is coupled by the engagement of different gears 14AX14B having a constant gear ratio, and the shift control rotation part of the planetary gear unit 110 of the main shaft 10 The output rotating portion 23 of the planetary gear unit 110 ': and the first subshaft 20 are connected to two planetary gear units 110 engaged by engagement of different gears 14DK14E having a constant gear ratio. (110 ') consists of a planetary gear assembly (100) in parallel combination by parallel to each other. Transmission using two control means and gear assemblies of the gong.

[Claim 3]

The gear assembly according to claim 1, wherein another planetary gear unit (1ΚΓ), which is used as the second sub-axis (30), is formed in a two-plane planetary gear assembly (100) in parallel with each other in parallel. Another component of the other planetary gear unit 11 (Γ) used as the secondary shaft 30 (sun gear S ^' , ring gear (ΙΓ), planetary gear carrier ((Γ :)] 30, and the other components [sun gear (s-), ring gear (r), planetary gear carrier «:)] to the shift control rotation part 32 of the two secondary shafts 30. And second one of the other components (sun gear (s'), ¾ gear ar), planetary gear carrier).

Correction Paper (Rule Article 91) An output rotation unit 33 of 30, but the input rotation unit 31 of the second sub-shaft 30 has a different gear (14A) having a constant gear ratio from the main shaft (10) drive input rotation unit (11) ( 14B) (14G) (14G ') is engaged, the transmission gear rotation part 32 of the second sub-shaft 30 to the engagement of different gears (14C') (14 ') having a constant gear ratio. The first control means (F1) having a control function is provided by the second control means (F2) having another control function is added to the output rotation unit 33 of the second auxiliary shaft 30; At least three or more planetary gear units 110 (11 0 ') (110 ") coupled to each other by engagement of the shift control rotation part 22 of the subshaft 20 and different gears 14J 14H having a constant gear ratio are mutually connected. the parallel combination by the axis-to-axis parallel to the planetary gear assemblies (10, 0 ^';), two control means and gear assemblies, characterized by the yitu eojim Transmission yonghan.

[Claim 41]

2. The differential gear assembly 200 constituting the gear assembly is one of the components of the differential gear unit 210 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), pinion gear housing ( DP)] as the control rotation part 42 for shifting the main shaft 40, and any other component [differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)] Of the other differential gear unit 210 ^' , which is composed of a drive output rotation part 43 of 40),

Correction Paper (Rule Article 91) One component [differential A-axis (DA '), differential B-axis (DB'), pinion gear housing (DF;) is the input rotation part 51 of the first sub-shaft 50, and the other component [ Differential A-axis DA ', differential B-axis DB', and pinion gear housing DP 'are coupled to the first control means F1 by the shift control rotation part 52 of the first sub-shaft 50. , Any other component (differential A-axis (DA ^' ), differential B-axis (DB'), pinion gear housing (DP ';) to the output rotation part 53 of the first sub-shaft 50 The second control means (F2) is coupled to the structure consisting of a structure that receives the control function transmission device characterized in that the two control means and the gear combination.

[Claim 5]

According to claim 1, Of the configuration of the differential gear assembly 200 constituting the gear assembly, the main shaft 40 drive input rotation part 41 is a variable power source (VP) or the rotational speed of the rotational power source (P) or The rotational speed of the rotational power source is always coupled to the gear 44A having a constant gear ratio while the fixed power source F2 is transmitted through the main shaft 40, and the shift control rotation part 42 of the main shaft 40 has a constant gear ratio. Is coupled to the gear 44D, the input rotational portion 51 of the first sub-shaft 50 is coupled to the gear 44B having a constant gear ratio, the shift control rotation portion 52 of the first sub-shaft 50 Is coupled to the first control means (F1) having a control function, the output rotation part 53 of the first sub-shaft 50 is a constant gear ratio with the addition of a second control means (F2) with another control function Is engaged with the engagement of gears (44E) with The drive input and discharge portion 41 of the main shaft 40 and the input and discharge portion 51 of the first subshaft 50 are mutually have a constant gear ratio.

Correction Paper (Rule Article 91) The output rotations of the shift control rotation part 42 and the first sub-shaft 50 differential gear unit 210 'of the main shaft 40 differential gear unit 210 are coupled by engagement of the other gears 44AK44B. 53) is a differential gear assembly 200 in which two differential gear units 210 (210 ^' ) coupled by engagement of different gears 44DK44E with a constant gear ratio are in parallel combination by mutual axis parallelism. Transmission using two control means and gear combinations characterized by toothing.

[Claim 6]

2. The gear assembly as set forth in claim 1, wherein another differential gear unit (2ΚΓ :) used as the second sub-axis (60) is used in a two-column differential gear assembly (200) in parallel with each other in parallel. Another component of the differential gear unit 210 ^' used as the second sub-shaft 60 (differential A-axis DA', differential B-axis D, pinion gear housing DP ^* :) The input subassembly 61 of the two sub-shafts 60, and the other components [value "Dynamic A-axis (DA ^* ), the differential B-axis (D), the pinion gear housing (D)]] the 2nd sub-axis (60) ), And any other component (differential A-axis (DA ^* ), differential B-axis (DB-), pinion gear housing (D;)) is the second sub-axis (60). ) Is composed of an output rotation part (63) of the second sub-shaft (60), the input gear (61) having different gear ratio (44A) (44B) with a constant gear ratio from the main shaft (40) drive input rotation part (41) ) (44G) (44G ') The first control means F1 having a control function is coupled to the shift control rotation part 62 of the second sub-shaft 60 by engagement of different gears 44C 'and 44' having a constant gear ratio. Granted,

Correction Paper (Rule Article 91) The second control shaft F2 having another control function is added to the output rotation unit 63 of the second sub-shaft 60 and has a constant gear ratio with the shift control rotation unit 52 of the first sub-shaft 50. Differential gear assembly 200 in which at least three or more differential gear units 210, 210 '(210 ^* ;), coupled by engagement of different gears 44J, 44H, are in parallel combination by mutual axis parallelism. Transmission using two control means and gear combination, characterized in that consisting of.

[Claim 7]

2. The composite gear assembly 300 constituting the gear assembly is a component of any one of the planetary gear units 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)] 70, the drive input rotation part 71; and other components (sun gear S, ring gear R, planetary gear carrier C, or differential A axis DA, differential B axis DB, The pinion gear housing (DP)] as 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). Shaft DA, differential B-axis DB, pinion gear housing DP, which consists of the output rotation part 73 of the main shaft 70, and any other planetary gear unit used as the first sub-axis 80 ( 110 ') or differential gear unit (2 10 ') (Sun gear (S'), ring gear (R '), planetary gear carrier (), 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,

Correction Paper (Article 91) The other components (sun gear (S '), ring gear (R'), planetary gear carrier (), or differential A axis (DA '), differential B axis (DB'), pinion gear housing (DF;)) It is coupled to the first control means (F1) to the shift control rotation portion 82 of the first sub-shaft 80 receives the control function. Another component [sun gear (S '), ring gear (R'), planetary gear carrier (C), or differential A-axis (DA '), differential B-axis (DB'), pinion gear housing (DP ' )] To the output rotation part 83 of the first sub-shaft 80, the second control means (F2) is coupled to the transmission structure using the two control means and the gear assembly, characterized in that it is configured to receive a control function Device .

[Claim 8]

The variable input power source (VP) according to claim 1, wherein the drive input rotation part (71) of the main shaft (70) of the compound gear assembly (300) constituting the gear assembly has a variable rotation speed of the rotation power source (P). Alternatively, the rotational speed is always transmitted through a constant fixed power source (FP) spindle 70, and is coupled with a gear 74A having a constant gear ratio, and the shift control rotation part 72 of the spindle 70 has a gear having a constant gear ratio ( 74D), the input rotation portion 81 of the first sub-shaft 80 is coupled to the gear 74B having a constant gear ratio, the shift control rotation portion 82 of the first sub-shaft 80. Is coupled to the first control means F1 having a control function, and the output dimming part 83 of the first subshaft 80 is fixed while the second control means F2 having another control function is added. Coupled with a gear 74E having a gear ratio, the drive input of said spindle 70 All input rotary part 81 of the 71 and the first minor axis (80) depend on the engagement of the different gears (7 AX74B) with a constant gear ratio

Correction Paper (Rule Article 91) And the output control part 83 of the shift control rotation part 72 of the main shaft 70 and the planetary gear unit 110 and the differential gear unit 210 'of the first subshaft 80 have a constant gear ratio. Any one planetary gear unit 110 (110 ') and one differential gear unit (210) (210 ^' ) coupled by engagement of the Dalon gears (74DK74E) are combined gears in parallel combination by mutual axis parallelism. A transmission apparatus using two control means and a gear assembly, comprising a combination 300.

[Claim 9]

2. The planetary gear unit (ll (r)) or differential gear unit (210-) according to claim 1, wherein the gear assembly (300 ':) is used as the second sub-axis (90) in the two-row compound gear assembly (300). ) Is one of the components 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 ^* :)] and another component of the planetary gear unit 11 (Γ) [sun gear (S '), ring gear (IT), planetary gear carrier (Γ)]. 90 of the input rotation part 91, and the other components (differential A-axis (DA '), differential B-axis (DB-), pinion gear housing (D), sun gear (S'), ring gear (R '). ), The planetary gear carrier ()] is the shift control rotation part 92 of the second sub-axis 90, and any other component (differential A-axis (DA '), differential B-axis (D), pinion gear housing (DP '), sun gear (S'), ring gear (ΙΓ), The planetary gear carrier (CT :)] is composed of the output rotating part 93 of the second sub-shaft 90, and the input rotating part 91 of the second sub-shaft 90 has a main shaft 70 driving input dimming part 71. From a constant gear ratio

Correction Paper (Article 91) The gears 44A, 44B, 44G, 44G 'are coupled to each other, and the second control shaft 92 of the second sub-axis 90 has a constant gear ratio. The first control means F1 having a control function is provided by the engagement of the 44K ', and the second control means F2 having another control function is output to the output rotating part 93 of the second sub-axis 90. ) And at least one planetary gear unit (110) (110 ') (11) coupled by engagement of the shift control rotating portion (82) of the first subshaft (80) and the different gear (44JK44H) having a constant gear ratio. Combination of (Γ) and at least one differential gear unit (210) (210 ') (210 ^' ), consisting of a multiple gear assembly (300 ':) in parallel combination by at least three mutually parallel axes It uses two control means and gear combination.

Correction Paper (Rule Article 91)