KR101002175B1 - One reply power source speed change gear using gear corporate bady - Google Patents

One reply power source speed change gear using gear corporate bady Download PDF

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KR101002175B1
KR101002175B1 KR1020100084504A KR20100084504A KR101002175B1 KR 101002175 B1 KR101002175 B1 KR 101002175B1 KR 1020100084504 A KR1020100084504 A KR 1020100084504A KR 20100084504 A KR20100084504 A KR 20100084504A KR 101002175 B1 KR101002175 B1 KR 101002175B1
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South Korea
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gear
differential
power source
axis
rotation part
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KR1020100084504A
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Korean (ko)
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KR20100102082A (en
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강성원
한광희
강동헌
조재민
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강성원
조재민
강동헌
한광희
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Priority to KR1020100084504A priority Critical patent/KR101002175B1/en
Publication of KR20100102082A publication Critical patent/KR20100102082A/en
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Publication of KR101002175B1 publication Critical patent/KR101002175B1/en
Priority to PCT/KR2011/006026 priority patent/WO2012030083A2/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The present invention relates to a transmission using a single type of rotational power source and a gear assembly, and more particularly, a transmission using two control means and a gear assembly registered in advance by the applicant of the present invention (application number: 10 -2009-0115229), wherein the rotational speed of the rotational power source transmitted from the drive input shaft is shifted to the gear ratio of the planetary gear unit or the differential gear unit to constitute a transmission transmitted to the drive means. After the gear assembly is formed by the combination of the gear unit and the at least one differential gear unit, a transmission device using a single type of rotational power source and the gear assembly that can arbitrarily and variously extend the transmission range with respect to the rotational speed of the drive output shaft. It is about.

Description

Transmission using a single type of power source and gear assembly {One reply power source speed change gear using gear corporate bady}

The present invention relates to a transmission using a single type of rotational power source and a gear assembly, and more particularly, a transmission using two control means and a gear assembly registered in advance by the applicant of the present invention (application number: 10 -2009-0115229), wherein the rotational speed of the rotational power source transmitted from the drive input shaft is shifted to the gear ratio of the planetary gear unit or the differential gear unit to constitute a transmission transmitted to the drive means. After the gear assembly is formed by the combination of the gear unit and the at least one differential gear unit, a transmission device using a single type of rotational power source and the gear assembly that can arbitrarily and variously extend the transmission range with respect to the rotational speed of the drive output shaft. It is about.

In general, in various industrial sites, the input rotational speed of main motive power is shifted through gear ratios in various places such as industrial machines, reducers, gearheads, hoists, goods transfer conveyors, winches, elevators, and escalators, depending on the use. Various types of stepped transmissions and continuously variable transmissions that transmit the output rotation speed to the drive means of the drive shaft are widely used.

However, gear reducers and gear reducers that are widely used for industrial use are mainly geared or belt pulley type or inverters that control the driving speed. As the reduction ratio is limited to a specific ratio, several longitudinal drive shafts are used in combination with multiple gearboxes and gearboxes with high ratios, but this has led to problems that require a large installation space due to volume and weight increase. In order to realize the high speed ratio or reduction ratio, the manufacturing cost is increased by combining a plurality of longitudinal drive shafts whose speed ratio or reduction ratio is determined according to the tooth ratio and the outer diameter.

Due to the above problems, in recent years, a speed increaser or a reducer using a rotation ratio for each rotation part of a planetary gear unit that can transmit a large power with a simple structure is widely used. In particular, in order to obtain a high ratio, a plurality of planetary gear units are double or Various types of transmissions coupled in series in triplicates have been developed and are known in the art.

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

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

An object of the present invention for solving the above problems is to form a gear assembly with an extended gear ratio by a combination of at least one planetary gear unit and at least one differential gear unit, which is used as the main shaft of the gear assembly. One component of a gear unit is provided with a rotational power source transmitted from a drive input shaft, and any component of each gear unit used as an input rotation part of the main shaft of the gear assembly or the first sub shaft and the main shaft of the gear assembly or The other component of each gear unit, which is used as the shift control rotation part of the first sub-shaft, adds a rotational power source having a different gear ratio by the engagement of different gears with a constant gear ratio, thereby extending the range of the shift of the output shaft of the main shaft. To provide a single type of rotational power source and transmission using There used.

The second object of the present invention is to add a rotational force of different speed ratios to the input rotation part and the shift control rotation part of a drive input rotation part of one gear unit used as the main shaft of the gear assembly and the other gear units used as the main shaft or the first sub-axis, respectively. It is to provide a transmission apparatus using a single type of rotational power source and a gear combination that can extend the speed range of the output shaft of the main shaft to a single type of rotational power source.

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

Gear combination of the transmission using a single type of rotational driving force and gear combination according to the present invention is

Each component for at least one planetary gear unit 110 (110 ') [sun gear (S) (S'), ring gear (R) (R '), planetary gear carrier (C) (C') The planetary gear assembly 100 (100 ') formed by combining the planetary gear units (110) (110') in parallel so as to be parallel to each other by means of gears;

Each component for at least one differential gear unit 210 (210 ') (differential A-axis (DA) (DA'), differential B-axis (DB) (DB '), pinion gear housing (DP) ( DP ′)] and differential gear assembly 200 (200 ') formed by combining the respective differential gear units 210 (210') in parallel with each other by the gear teeth in parallel with each other;

Each component for at least one planetary gear unit 110 (110 ') (sun gear (S) (S'), ring gear (R) (R '), planetary gear carrier (C) (C')] And each component for at least one differential gear unit 210 (210 ') [differential A-axis (DA) (DA'), differential B-axis (DB) (DB '), pinion gear housing (DP) ( DP ′)] are combined gears in which at least one planetary gear unit (110) (110 ') and at least one differential gear unit (210) (210') are combined in parallel so as to be parallel to each other by a gear coupling. Combination 300 is composed of separate.

In addition, the rotational driving force of the transmission using the single-type rotational driving force and the single-row gear assembly 100 and 200 according to the present invention is a first rotational power source for transmitting a main power source to the drive input shafts 11 and 41 of the engine. P1 and the shift control rotation part 12 and 42 are comprised by the 1st rotation power source P1 and the 2nd auxiliary power source P2 which transmits the power source with which a gear ratio differs.

In addition, the rotational driving force of the transmission using a single type of rotational driving force and a two-column gear assembly 100 ', 200', 300 according to the present invention is the first rotational power source for transmitting the main power source to the drive input shaft of the engine ( P1), a second auxiliary power source P2 for transmitting a power source having a different transmission ratio from the first rotational power source P1, and an input rotation part of the other gear units used as the first auxiliary shaft of the gear assembly, and the first auxiliary shaft of the gear assembly. The shift control rotation part of the other gear units to be used as is separated into a third auxiliary power source (P3) for transmitting a power source different from the first rotary power source (P1) and the second auxiliary power source (P2).

Here, the planetary gear assembly 100 of the one-row gear assembly of the present invention is composed of any one planetary gear unit 110, any 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 drive shift control rotation part 12, and any other component (sun gear (S), ring gear (R), planetary gear carrier (C)) as the drive output rotation part (13), The drive input rotation part 11 is provided with a first rotational power source P1, and the shift control rotation part 12 has different gears 14D and 14E having a constant gear ratio to the first rotational power source P1. And a second auxiliary power source P2 having a primary shifted rotational force of the first rotational power source P1 by engagement with another gear 14F and 14I. It is supposed to.

In the two-row gear assembly of the present invention, the planetary gear assembly 100 'is composed of at least one planetary gear unit 110, 110' in a parallel combination by parallel interaxial axis. One component of the planetary gear unit 110 (sun gear (S), ring gear (R), planetary gear carrier (C)) to be used as the drive input rotation unit 11, and another component [Sun gear (S), ring gear (R), planetary gear carrier (C)] is the drive rotation control rotation part 12, and any other component (sun gear (S), ring gear (R), planetary The gear carrier C is constituted by the drive output rotating part 13, and any component of the other planetary gear unit 110 'used as the first sub-shaft 20 (sun gear S', ring gear ( R ′) and planetary gear carrier C ′ as the first sub-shaft input rotation part 21, and other components (sun gear S ′, ring gear R ′, planetary gear carrier C ′). 1st Shaft Transmission Rotating portion 22, and any other component (sun gear (S '), ring gear (R'), planetary gear carrier (C ') is composed of the output rotating portion 23 of the first sub-shaft, A first rotational driving force P1 is applied to the driving input rotation part 11, and different gears 14A and 14B having a constant gear ratio to the first rotational driving force P1 are provided to the first sub-axis input rotational part 21. The second auxiliary driving force (P2) having the first rotational driving force (P1) of the first rotational driving force (P1) by the teeth of the coupling is given, and the second auxiliary driving force (20) of the first control shaft 22, the second auxiliary driving force (22) Combination of different gears 14D, 14E and another gear 14F, 14I having a constant gear ratio to the motive force P2 has a second shifted rotational force of the first rotational driving force P1. The third auxiliary driving force P3 is applied, and the output rotation part 23 of the first subshaft 20 has a constant gear ratio with the drive rotation control rotation part 12 of the main shaft 10. The structure is coupled by engagement of different gears 14K and 14J.

In addition, the gear assembly of the first row of the present invention, the differential gear assembly 200 is composed of any one of the differential gear unit 210, any one of the differential gear unit 210 used as the main shaft (40) A component (differential A-axis DA, differential B-axis DB, pinion gear housing DP) is the drive input rotation part 41 of the main shaft 40, and another component (differential A-axis DA). , The differential B axis (DB), the pinion gear housing (DP)] is the control rotation part 42 for the drive shift of the main shaft 40, and any other component (differential A axis DA, differential B axis ( DB) and pinion gear housing DP as a drive output rotation part 43 of the main shaft 40, wherein the drive input rotation part 41 is provided with a first rotational power source P1, and the drive shift control. The first rotary power source P1 is coupled to the rotating unit 42 by engagement between different gears 44D and 44E having a constant gear ratio to the first auxiliary power source P1 and another gear 44F and 44I. )of The second auxiliary power source P2 having the primary shifted rotational force is provided.

In the two-column gear assembly of the present invention, the differential gear assembly 200 'includes at least one differential gear unit 210 (210') in a parallel combination by parallel between each other, and the main shaft 40 Drive input rotation part 41 of the main shaft 40 to any one component of the differential gear unit 210 (differential A-axis DA, differential B-axis DB, pinion gear housing DP). The other components (differential A-axis DA, differential B-axis DB, pinion gear housing DP) as the control rotation part 42 for the drive shift of the main shaft 40, One 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, which is used as the first sub-shaft 50 One component of the other differential gear unit 200 '(differential A-axis DA', differential B-axis DB ', pinion gear housing DP') is connected to the input rotation part of the first sub-shaft 50. 51), and another component [differential A Axis DA ′, differential B axis DB ′, and pinion gear housing DP ′ as the shift control rotation part 52 of the first sub-shaft 50, and the other component (differential A-axis ( DA ′), differential B-axis (DB ′), and pinion gear housing (DP ′) are configured as the output rotation part 53 of the first subshaft 50, and the drive input rotation part 41 has a first rotational driving force ( P1) is applied to the input rotational portion 51 of the first sub-shaft 50 by the engagement of different gears 44A and 44B having a constant gear ratio to the first rotational driving force P1. The second auxiliary driving force P2 having the primary shifted rotational force of P1 is given, and the shift control rotation part 52 of the first subshaft 50 has a predetermined gear ratio to the second auxiliary driving force P2. Coupling by engagement of another gear 44D, 44E and another gear 44F, 44I gives a third auxiliary driving force P3 having a second shifted rotational force of the first rotating driving force P1. , The first auxiliary shaft 50 The output rotation part 53 of the main shaft 40 has a structure in which the drive rotation control rotation part 42 of the main shaft 40 is coupled to each other by engagement of different gears 44K and 44J having a constant gear ratio.

On the other hand, in the two-column gear assembly of the present invention, the composite gear assembly 300 has at least one planetary gear unit (110) (110 ') and at least one differential gear unit (210) (210') mutually It is composed of parallel combination by parallel between axes, and one component of one planetary gear unit 110 used as main shaft 70 (sun gear S, ring gear R, planetary gear carrier C) Alternatively, one component of the differential gear unit 210 (differential A axis DA, differential B axis DB, pinion gear housing DP) is used as the driving input rotation part 71 of the main shaft 70. Other components (sun gear (S), ring gear (R), planetary gear carrier (C), or differential A axis (DA), differential B axis (DB), pinion gear housing (DP)) Control rotation part 72 for driving shift of the motor, and any other component (sun gear S, ring gear R, planetary gear carrier C, or differential A axis DA, differential B axis DB). ), The pinion gear housing (DP) to drive the main shaft 70 Any one of the other planetary gear unit 110 'or the differential gear unit 210' used as the first sub-shaft 80, which is constituted by the output rotation unit 73 (sun gear S ', ring gear) (R '), planetary gear carrier (C') or differential A-axis (DA '), differential B-axis (DB'), pinion gear housing (DP '). ), And other components (sun gear (S '), ring gear (R'), planetary gear carrier (C '), or differential A-axis (DA'), differential B-axis (DB '), pinion gear housing (DP ′)] is the shift control rotation part 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 ′, and pinion gear housing DP ′ as an output rotation part 83 of the first sub-axis 80, wherein the drive input of the main shaft 70 is formed. The rotation part 71 is provided with a first rotational driving force P1, and the input rotation part 81 of the first sub-axis 80 is provided with the first rotational driving force P1. ) By the engagement of the different gears 74A and 74B having a constant gear ratio is given a second auxiliary driving force (P2) having a primary shifted rotational force of the first rotational driving force (P1) and the first sub-shaft ( In the shift control rotation part 82 of the 80, the second auxiliary driving force P2 is coupled to each other by engagement of different gears 74D, 74E and another gear 74F, 74I having a constant gear ratio. A third auxiliary driving force P3 having a second shifted rotational force of the first rotational driving force P1 is provided, and the output rotating portion 83 of the first subshaft 80 is a control rotation portion for driving shifting of the main shaft 70 ( 72 and a combination of gears 74K and 7J having a constant gear ratio.

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

In particular, it is possible to make a compact volume of the gear assembly that can realize a very large speed increase or reduction ratio while having a very simple structure of a speed reducer or a reducer, so that the manufacturing cost can be significantly reduced. Will appear.

1 and 2 are views of each planetary gear assembly constituting the gear assembly of the present invention.
Each embodiment showing the coupling relationship
3 and 4 are diagrams of each differential gear assembly constituting the gear assembly of the present invention.
Each embodiment showing the coupling relationship
5 and 6 are views of each compound gear assembly constituting the gear assembly of the present invention.
Each embodiment showing the coupling relationship

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

Of the transmission using planetary gear assembly 100 (100 ') and a single type of rotary power source. Example >

1 is a cross-sectional view illustrating a planetary gear assembly 100 including a planetary gear unit 110 having a single gear assembly according to the present invention, and FIG. 2 is a two-plane planetary gear unit 110 and 110 according to the present invention. 'Is a coupling cross-sectional view showing a coupling relationship according to the first embodiment of the planetary gear assembly 100' coupled to each other.

First, as shown in FIG. 2, the coupling relationship between a single type of rotational power source consisting of a planetary gear assembly 100 ′ according to the first embodiment of the present invention and a transmission using a gear assembly will be described.

After setting the prerequisites for explaining the shifting process according to the first embodiment using the two-plane planetary gear assembly 100 'according to the present invention, the following Table 1 shows the shifting process of the output rotational speed. saw.

One Rotation of P1 → 1 rpm 2 Rotation ratio of each part of each planetary gear unit (S: C: R) → 5: 1: 1 3 14A: 14B gear rotation ratio → 1: 2 4 14D: gear turn ratio of 14E → 1: 2 5 14F: gear rotation ratio of 14I → 1: 2 6 14J: gear rotation ratio of 14K → 1: 2

The ring gear R of the planetary gear unit 110 of the main shaft 10 has a constant gear ratio as the first rotational power source P1 is used as the driving input rotation part 11 of the main shaft 10 through which the main rotational force P1 is transmitted. It is coupled to the excitation gear 14A, 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 (14K) having a constant gear ratio to the gear, the sun gear ( S) is used as the output rotation part 13 of the main shaft 10.

The ring gear R ′ of the planetary gear unit 110 ′ of the first subshaft 20 is used as an input rotation part 21 of the first subshaft 20, and the outer peripheral surfaces thereof are gears with each other having a constant gear ratio. 14D is coupled, and the planetary gear carrier C 'is used as the shift control rotation part 22 of the first sub-shaft 20 while the outer circumferential surface thereof is coupled to the gear 14I having a constant gear ratio. The sun gear S 'is used as the output rotation part 23 of the first sub-shaft 20, and the outer circumferential surface thereof is coupled to the gear 14J having a constant gear ratio.

Here, the gear 14A of the first subshaft 20 and the planetary gear unit 110 'of the first rotation shaft 21 has a constant gear ratio with the drive input rotation unit 11 of the main shaft 10 planetary gear unit 110. By the engagement of the 14B, the second auxiliary power source P2 having the primary shifted rotational force of the first rotational power source P1 is provided, and the shift control rotating unit 22 has the first auxiliary shaft 20 planetary gear unit. The input rotational portion 21 and the outer circumferential surface of (110 ') of the first rotational power source (P1) by the engagement of different gears (14D) 14E and another gear (14F) (14I) having a gear ratio uniformly. A third auxiliary power source P3 having a secondary shifted rotational force is provided, and the output rotational unit 23 has a gear ratio of the different gears 14K and 14J having a constant gear ratio with the shift control rotational unit 12 of the main shaft 10. It is a structure that is joined by an engagement.

At this time, each 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 C ′) is set to 5: 1: 1, and then the main shaft 10 is driven. Both the gear 14A built into the input rotating unit 11 and the gear 14B built into the input rotating unit 21 of the first subshaft 20 set the gear rotation ratio to 1: 2, and the main shaft 10 The gear 14K built in the shift control rotation part 12 of the gearbox 14 and the gear 14J built in the output rotation part 23 of the first subshaft 20 set the gear rotation ratio to 1: 2. The gear rotation ratio of the other gear 14E meshed with the gear 14D built into the input rotation part 21 of the one subshaft 20, and the gear control rotation part 22 of the first subshaft 20. Another gear (1) meshing with gear (14I) The gear rotation ratio of 4F) is set to 1: 2, and the second auxiliary power source P2 having the rotational force primarily shifted from the first rotational power source P1 to the input rotation part 21 of the first subshaft 20. Is provided, and the shift control rotation part 22 is set so that the 3rd auxiliary power source P3 which has the secondary shifted rotational force of the said 1st rotational power source P1 may be provided.

In addition, when the initial rotational speed of the first rotational power source (P1) transmitted to the drive input rotation unit 11 of the main shaft 10 is set to 1 RPM, the rotational speed appearing on the output rotation portion 13 of the main shaft 10 increases to 505 RPM. I got the result.

That is, the speed change apparatus according to the first embodiment of the present invention has an input rotational speed by a combination of gears in which at least one planetary gear unit (110) (110 ') is in parallel with each other so that the components are parallel to each other. It is possible to arbitrarily expand the range of acceleration and deceleration of the output rotational speed with respect to the one-column planetary gear assembly 100 of the present invention is also applied together.

At this time, if the number of revolutions and the gear ratio of the structure P1 of the coupling type is not limited to the above setting example, the speed ratio corresponding to the corresponding combination condition will appear, so as not to depart from the technical spirit of the present invention. Of course, it can be carried out in various ways.

<Embodiment of Transmission Device Using Differential Gear Combination Body 200 (200 ') and a Single Type of Rotating Power Source>

3 is a cross-sectional view illustrating a differential gear assembly 200 composed of a differential gear unit 210 having one gear assembly according to the present invention, and FIG. 4 is a differential gear unit 210 having two rows of 210 according to the present invention. ′) Is a coupling cross-sectional view showing a coupling relationship according to the second embodiment of the differential gear assembly 200 ′ coupled with each other.

First, as shown in FIG. 4, a coupling relationship between a single type of rotational power source consisting of a two-column differential gear assembly 200 ′ according to a second embodiment of the present invention and a transmission using a gear assembly will be described. .

After setting the prerequisites for explaining the shifting process according to the second embodiment using the two-column differential gear assembly 200 'of the present invention as shown in Table 2 below, the shifting process of the output rotational speed will be described. saw.

One Rotation of P1 → 1 rpm 2 Rotation ratio of each part of each differential gear unit → DP X 2 = DA + DB 3 44A: 44B gear turn ratio → 1: 2 4 44D: Gear turn ratio of 44E → 1: 2 5 44F: Gear rotation ratio of 44I → 1: 2 6 44J: Gear turn ratio of 44K → 1: 2

The differential A axis DA of the differential gear unit 210 of the main shaft 40 is used as a driving input rotation part 41 of the main shaft 40 through which the first rotary power source P1 is transmitted through the main shaft 40. And the pinion gear housing (DP) is used as the shift control rotation part 42 of the main shaft 40 while the outer circumferential surface thereof is coupled with the gear 44K having a constant gear ratio. The B axis DB is used as the output rotation part 43 of the main shaft 40.

The differential A-axis DA ′ of the differential gear unit 210 ′ of the first sub-shaft 50 is used as an input rotation part 51 of the first sub-shaft 50, and the gears 44B have mutually constant gear ratios. (44D) is coupled, the pinion gear housing (DP ') is used as the shift control rotation part 52 of the first sub-shaft 50, the outer peripheral surface is geared to the gear (44I) having a constant gear ratio. The differential B-axis DB 'is used as the output rotation part 53 of the first sub-shaft 50, and the outer circumferential surface thereof is coupled to the gear 44J having a constant gear ratio.

Herein, the input rotation part 51 of the first sub-shaft 50 differential gear unit 210 'has a different gear 44A having a constant gear ratio from the driving input rotation part 41 of the main shaft 40 differential gear unit 210. The second auxiliary power source P2 having the primary shifted rotational force of the first rotational power source P1 is provided by the engagement of the 44Bs, and the shift control rotation unit 52 is provided with the first sub-shaft 50 differential gear unit. Input rotation part 51 of 210 'and the outer peripheral surface of the 1st rotational power source P1 by the engagement of different gear 44D, 44E, and another gear 44F, 44I which have a gear ratio fixed to the gear. The third auxiliary power source P3 having the secondary shifted rotational force is given, and the output rotation part 53 is formed of the gears 44K and 44J of the different gears having a constant gear ratio with the shift control rotation part 42 of the main shaft 40. It is a structure that is joined by an engagement.

In this case, the respective rotation ratios of the respective components (differential A-axis DA, differential B-axis DB, pinion gear housing DP) of the main shaft 40 differential gear unit 210 and the first sub-shaft 50 differential gear Each rotation ratio of each component (differential A-axis DA ', differential B-axis DB', and pinion gear housing DP 'of the unit 210' is [Pinion gear housing DP 2 × differential] A-axis (DA) + differential-B-axis (DB)], and then the input rotation portion (44A) and the first sub-shaft (50A) of the gear 44A built in the drive input rotation portion 41 of the main shaft 40 ( The gears 44B built in 51 are all set at a gear rotation ratio of 1: 2, and the gears 44K and the first subshaft 50 built in the shift control rotary part 42 of the main shaft 40 are all set. The gear 44J built in the output rotation part 53 sets the gear rotation ratio to 1: 2, and another gear meshed with the gear 44D built in the input rotation part 51 of the first subshaft 50. A gear rotation ratio of 44E and a shift control of the first subshaft 50 The gear rotation ratios of the other gears 44F meshed with the gears 44I built into the rotary part 52 are all 1: 2, and the first rotational power source is connected to the input rotation part 51 of the first subshaft 50. A second auxiliary power source P2 having a primary shifted rotational force of P1 is provided, and the shift control rotation unit 52 has a third auxiliary power source having a secondary shifted rotational force of the first rotational power source P1 (P1). P3) was set to be given.

In addition, when the initial rotational speed of the first rotational power source P1 transmitted to the drive input rotational portion 41 of the main shaft 40 is set to 1 RPM, the speed of rotation appearing at the output rotational portion 43 of the main shaft 40 is increased to 73 RPM. I got the result.

That is, the transmission device according to the second embodiment of the present invention has an input rotational speed in parallel combination by engagement of gears such that at least one of the components of at least one differential gear unit (210) (210 ') are parallel to each other. It is possible to arbitrarily expand the range of acceleration and deceleration of the output rotational speed with respect to the one-column differential gear assembly 200 of the present invention is also applied together.

At this time, not limited to the above-described setting example of the present invention, if the number of revolutions, the gear ratio of the coupling structure P1 is changed arbitrarily, the speed ratio corresponding to the combination conditions will appear, so as not to depart from the technical spirit of the present invention Of course, it can be variously performed in the inside.

<Of a transmission using a composite gear assembly 300 and a single type of rotational power source Example >

5 is a two-row compound gear in which any one differential gear unit 210 and one planetary gear unit 110 'used as the main shaft 70 are coupled to the gear assembly of the present invention. Coupling cross-sectional view showing a coupling relationship according to a third embodiment of the assembly 300, Figure 6 is one of which is used as the planetary gear unit 110 and the first sub-shaft 80 used as the main shaft 70 4 is a cross-sectional view showing a coupling relationship according to the fourth embodiment, in which a differential gear unit 210 'is coupled to another two-row composite gear assembly 300 coupled thereto.

First, as shown in FIG. 5, a coupling relationship between a single type of rotational power source consisting of a two-gear composite gear assembly 300 according to a third embodiment of the present invention and a transmission using a gear assembly will be described.

After setting the preconditions for describing the shifting process according to the third embodiment using the two-column composite gear assembly 300 according to the present invention as shown in Table 3, the shifting process of the output rotation speed was examined. .

One Rotation of P1 → 1 rpm 2 Rotation ratio of each part of each differential gear unit → DP X 2 = DA + DB 3 Rotation ratio of each part of the planetary gear unit (S: C: R) → 5: 1: 1 4 74A: 74B gear turn ratio → 1: 2 5 74D: gear turn ratio of 74E → 1: 2 6 74F: 74I gear turn ratio → 1: 2 7 74J: gear turn ratio of 74K → 1: 2

The differential A axis DA of the differential gear unit 210 of the main shaft 70 is used as a driving input rotation part 71 of the main shaft 70 through which the first rotary power source P1 is transmitted through the main shaft 70. And the pinion gear housing (DP) is used as the shift control rotation part 72 of the main shaft 70 while the outer circumferential surface thereof is coupled with the gear 74K having a constant gear ratio. The B axis DB is used as the output rotation part 73 of the main shaft 70.

The ring gear R ′ of the planetary gear unit 110 ′ of the first sub-shaft 80 is used as an input rotation part 81 of the first sub-shaft 80 while the outer circumferential surface thereof is geared to each other with a constant gear ratio 74B. (74D) is coupled, the planetary gear carrier (C ') is used as the shift control rotation portion 82 of the first sub-shaft 80, the outer peripheral surface is coupled to the gear (74I) having a constant gear ratio to the gear, The sun gear S 'is used as the output rotation part 83 of the first sub-shaft 80, and the outer circumferential surface thereof is coupled to the gear 74J having a constant gear ratio.

In this case, the input rotation part 81 of the planetary gear unit 110 ′ of the first sub-axis 80 has different gears 74A having a constant gear ratio from the driving input rotation part 71 of the differential gear unit 210 of the main shaft 70. The second auxiliary power source P2 having the primary shifted rotational force of the first rotational power source P1 is provided by the engagement of the 74Bs, and the shift control rotating unit 82 has the first auxiliary shaft 80 planetary gear unit. Secondary shifting of the first rotary power source P1 by engagement of the input gear 81 of 110 'with the different gears 74D and 74E having a constant gear ratio and another gear 74F and 74I. A third auxiliary power source P3 having a rotational force is provided, and the output rotation unit 83 is coupled to a gear of different gears 74K and 74J having a constant gear ratio with the shift control rotation unit 72 of the main shaft 70. It is structured.

At this time, each rotation ratio of each component (differential A-axis DA, differential B-axis DB, pinion gear housing DP) of the main gear 70 differential gear unit 210 [pinion gear housing (DP) × 2 = differential A-axis (DA) + differential B-axis (DB)], and each component of the first sub-axis 80 planetary gear unit 110 '[sun gear S', ring gear R ′) And the planetary gear carriers C ′] are set to 5: 1: 1, and then the gear 74A and the first subshaft which are built up in the drive input rotation part 71 of the main shaft 70. The gears 74B built in the input rotation part 81 of the 80 all set the gear rotation ratio to 1: 2, and the gear 74K built in the shift control rotation part 72 of the main shaft 70 and the gear 74B. The gear 74J built on the output rotation part 83 of the first subshaft 80 sets the gear rotation ratio to 1: 2, and the gear built on the input rotation part 81 of the first subshaft 80. The gear rotation ratio of the other gear 74E engaged with 74D), and The gear rotation ratio of the other gear 74F meshed with the gear 74I arranged on the shift control rotation part 82 of the first subshaft 80 is 1: 2, and the input rotation part of the first subshaft 80 is set to 1: 2. A second auxiliary power source P2 having a primary shifted rotational force of the first rotational power source P1 is provided to the 81, and the shift control rotation unit 82 is a secondary shift of the first rotational power source P1. The third auxiliary power source P3 having the given rotational force was set to be provided.

In addition, when the initial rotational speed of the first rotational power source (P1) transmitted to the drive input rotation unit 71 of the main shaft 70 is set to 1 RPM, the number of revolutions appearing in the output rotation portion 73 of the main shaft 70 increases to 201 RPM. I got the result.

That is, in the transmission apparatus according to the third embodiment of the present invention, each gear of each component of any one differential gear unit 210 and each component of any one planetary gear unit 110 ′ are in parallel with each other. The parallel combination by the combination of the two can arbitrarily expand the range of acceleration and deceleration of the output rotational speed to the input rotational speed.

At this time, not limited to the above-described setting example of the present invention, if the number of revolutions, the gear ratio of the coupling structure P1 is changed arbitrarily, the speed ratio corresponding to the combination conditions will appear, so as not to depart from the technical spirit of the present invention Of course, it can be variously performed in the inside.

Next, as shown in Figure 6, to look at the coupling relationship of the transmission device using a single type of rotational power source and the gear assembly made of another fourth embodiment of the two-row composite gear assembly 300 of the present invention do.

After setting the prerequisites for explaining the shifting process according to the fourth embodiment using the two-gear composite gear assembly 300 according to the present invention, the following table shows the shifting process of the output rotation speed. .

One Rotation of P1 → 1 rpm 2 Rotation ratio of each part of each differential gear unit → DP X 2 = DA + DB 3 Rotation ratio of each part of the planetary gear unit (S: C: R) → 5: 1: 1 4 74A: 74B gear turn ratio → 1: 2 5 74B: Gear rotation ratio of 74C → 1: 2 6 74D: 74E gear rotation ratio → 1: 2 7 74F: 74G gear rotation ratio → 1: 2 8 74H: Gear rotation ratio of 74I → 1: 2 9 74J: Gear rotation ratio of 74K → 1: 2

The ring gear R of the planetary gear unit 110 of the main shaft 70 has a constant gear ratio as the first rotational power source P1 is used as the driving input rotation part 71 of the main shaft 70 transmitted through the main shaft 70. And a planetary gear carrier (C) is used as the shift control rotation part 72 of the main shaft 70, and the outer circumferential surface thereof is coupled to the gear (74K) having a constant gear ratio, and the sun gear ( S) is used as the output rotation part 73 of the main shaft 70.

The differential A axis DA ′ of the differential gear unit 210 ′ of the first sub-shaft 80 is used as an input rotation part 81 of the first sub-shaft 80, and the outer peripheral surfaces thereof have gears with constant gear ratios. ) 74D is coupled, the pinion gear housing (DP ') is used as the shift control rotation portion 82 of the first sub-shaft 80, the outer peripheral surface is geared to the gear (74I) having a constant gear ratio. The differential B-axis DB ′ is used as the output rotation part 83 of the first sub-shaft 80, and the outer circumferential surface thereof is coupled to the gear 74J having a constant gear ratio.

Here, the input rotation portion 81 of the differential gear unit 210 'of the first sub-shaft 80 has a different gear 74A having a constant gear ratio from the input rotation portion 71 of the planetary gear unit 110 of the main shaft 70 ( The second auxiliary power source P2 having the primary shifted rotational force of the first rotational power source P1 is provided by the engagement of the 74B), and the shift control rotation unit 82 is provided with a differential gear unit of the first sub-axis 80. Secondary shifted rotational force of the first rotary power source P1 by engagement of the input gear 81 of 210 'and the different gears 74D and 74E having a constant gear ratio and another gear 74F and 74I. The third auxiliary power source (P3) having the same, and the output rotation unit 83 is a structure coupled to the engagement of the gear shifting control unit 72 of the main shaft 70 and the different gears 74K (74J) having a constant gear ratio. It is.

At this time, each rotation ratio of each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft 70 planetary gear unit 110 is set to 5: 1: 1, and The rotational ratios of the respective components (differential A-axis DA ', differential B-axis DB', and pinion gear housing DP 'of the one-axis 80 differential gear unit 210' are all referred to as [pinion gear housing]. (DP) × 2 = differential A-axis (DA) + differential B-axis (DB)], and then the gear 74A and the first sub-shaft built in the drive input rotation part 71 of the main shaft 70. The gears 74B built in the input rotation part 81 of the 80 all set the gear rotation ratio to 1: 2, and the gear 74K built in the shift control rotation part 72 of the main shaft 70 and the gear 74B. The gear 74J built on the output rotation part 83 of the first subshaft 80 sets the gear rotation ratio to 1: 2, and the gear built on the input rotation part 81 of the first subshaft 80. The gear rotation ratio of the other gear 74E engaged with 74D), and the first The gear rotation ratio of the other gear 74F meshed with the gear 74I built into the shift control rotation part 82 of the shaft 80 is set to 1: 2, and the input rotation part 81 of the first sub-shaft 80 is formed. ) Is provided with a second auxiliary power source (P2) having a primary shifted rotational force of the first rotational power source (P1), the shift control rotary unit 82 is a secondary shifted rotational force of the first rotational power source (P1) The third auxiliary power source (P3) having a set to be given.

In addition, when the initial rotational speed of the first rotational power source (P1) transmitted to the drive input rotation unit 71 of the main shaft 70 is set to 1 RPM, the rotation speed appearing on the output rotation portion 73 of the main shaft 70 increases to 185 RPM. I got the result.

That is, in the transmission apparatus according to the fourth embodiment of the present invention, each gear of each component of any one planetary gear unit 110 and each component of any one differential gear unit 210 'is parallel to each other. The parallel combination by the combination of the two can arbitrarily expand the range of acceleration and deceleration of the output rotational speed to the input rotational speed.

At this time, not limited to the above-described setting example of the present invention, if the number of revolutions, the gear ratio of the coupling structure P1 is changed arbitrarily, the speed ratio corresponding to the combination conditions will appear, so as not to depart from the technical spirit of the present invention Of course, it can be variously performed in the inside.

100,100 ′: Planetary gear assembly 110,110 ′: Planetary gear unit
200,200 ′: Differential gear assembly 210,210 ′: Differential gear unit
300: compound gear assembly
10,40,70: Spindle 20,50,80: First Shaft
11, 41, 71: drive input rotation part 21, 51, 81: input rotation part of the first sub-shaft
12, 42, 72: shift control rotation part 22, 52, 82: shift control rotation part of the first sub-shaft
13,43,73: output rotation part 23,53,83: output rotation part of the first sub-shaft
14,44,74: Gear
P1: first rotating power source P2: second auxiliary power source
P3: third auxiliary power source

Claims (5)

Planetary gear assembly formed by combining each of the components for at least one planetary gear unit (110) (110 ') in parallel so that the planetary gear units (110) (110') are parallel to each other by a gear coupling ( 100) (100 ');
A differential gear assembly in which each component for at least one differential gear unit (210) (210 ') is combined in parallel so that each differential gear unit (210) (210') is parallel to each other by means of gear teeth 200) 200 ';
Each component for at least one planetary gear unit (110) (110 ') and each component for at least one differential gear unit (210) (210') are at least one planetary gear due to gear gearing. The gear assembly is expanded by the combination of the unit 110, 110 'and at least one differential gear unit (210, 210') in parallel to each other in parallel parallel to each other axis; In the transmission using

The planetary gear assembly 100 ′ in which at least two planetary gear units 110 and 110 ′ of the gear assembly are arranged in parallel with each other in parallel with each other is a planetary gear unit 110 used as the main shaft 10. One component (sun gear S, ring gear R, planetary gear carrier C) as the drive input rotation part 11, and the other components (sun gear S, ring gear R, The planetary gear carrier C is the drive rotation control rotation part 12, and any other component (sun gear S, the ring gear R, the planetary gear carrier C) is the drive output rotation part 13. ) And any component of the other planetary gear unit 110 'used as the first auxiliary shaft 20 (sun gear S', ring gear R ', planetary gear carrier C'). Is the first sub-shaft input rotation part 21, and the other components (sun gear (S '), ring gear (R'), planetary gear carrier (C ')) are the first sub-shaft shift control rotation part (22). , Another component [ Sun gear (S '), ring gear (R'), planetary gear carrier (C ') is composed of the output rotation portion 23 of the first sub-shaft, the drive input rotation portion (11) has a first rotational power source (P1) The first sub-shaft input rotation part 21 is provided with one of the first rotational power source P1 by engagement of different gears 14A and 14B having a constant gear ratio to the first rotational power source P1. The second auxiliary power source P2 having the vehicle's shifted rotational force is provided, and the gear shift control unit 22 of the first subshaft 20 has different gears 14D having a constant gear ratio to the second auxiliary power source P2. Engagement by engagement of 14E and another gear 14F and 14I gives a third auxiliary power source P3 having a secondary shifted rotational force of the first rotational power source P1, and the first auxiliary shaft The output rotation part 23 of the 20 is coupled by the engagement of the control rotation part 12 for driving shift of the main shaft 10 and the different gears 14K and 14J having a constant gear ratio. Transmission using a source of rotational power and gear assemblies of a single kind of. The planetary gear assembly (100) of any one of the planetary gear units (110) is any one component of the planetary gear unit (110) used as the main shaft (Sun gear (S), ring gear). (R) and planetary gear carrier (C) as the drive input rotation part 11, and other components (sun gear (S), ring gear (R), planetary gear carrier (C)) are drive rotation control rotation parts. (12), and any other component (sun gear (S), ring gear (R), planetary gear carrier (C)) is constituted by the drive output rotation part (13), and the drive input rotation part (11) A first rotational power source P1 is provided, and the gear shifting control unit 12 has different gears 14D and 14E and another gear 14F having a constant gear ratio to the first rotational power source P1 ( 14I) a single type of rotational power, characterized in that a second auxiliary power source P2 having a primary shifted rotational force of the first rotational power source P1 is given by engagement by the engagement. Transmission using a gear with conjugate. According to claim 1, wherein at least two differential gear units (210) (210 ') in combination with each other in parallel parallel to each other in the parallel gear assembly 200' is used as the main shaft 40 any one differential gear unit ( One component (differential A-axis DA, differential B-axis DB, pinion gear housing DP) of 210 is used as the 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)] is the control rotation part 42 for the drive shift of the main shaft 40, and another component (differential A-axis (DA)) , The differential B-axis (DB), the pinion gear housing (DP)] is composed of the drive output rotating portion 43 of the main shaft 40, and 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 DP ') is the input rotation part 51 of the first sub-shaft 50, and the other component [ Differential A-axis (DA '), Differential B-axis (DB'), Pinion gear housing (DP ) As the shift control rotation part 52 of the first sub-shaft 50, and any other component (differential A-axis DA ', differential B-axis DB', pinion gear housing DP '). It is composed of the output rotating part 53 of the first sub-shaft 50, the drive input rotation part 41 is provided with a first rotational power source (P1) and the input rotation part 51 of the first sub-shaft 50 The second auxiliary power source P2 having the first shifted rotational force of the first rotational power source P1 is provided by engagement of different gears 44A and 44B having a constant gear ratio to the first rotational power source P1. The gear shift control rotary part 52 of the first sub-shaft 50 is engaged with the gears 44D and 44E and the other gears 44F and 44I having a constant gear ratio to the second auxiliary power source P2. A third auxiliary power source (P3) having a secondary shifted rotational force of the first rotational power source (P1) is provided by the coupling by, by the output rotation portion 53 of the first sub-shaft (50) of the main shaft (40) Drive shifting Transmission using a single type of source of rotational power and gear combination, characterized in that the coupling engagement of the different gears (44K) (44J) having a constant gear ratio and a rotation control (42). The method of claim 1, wherein the differential gear assembly 200 composed of any one differential gear unit 210 is any component of any one differential gear unit 210 used as the main shaft (differential A-axis DA ), Differential B-axis (DB), pinion gear housing (DP)] as the drive input rotation part 41 of the main shaft 40, and other components (differential A-axis (DA), differential B-axis (DB), The pinion gear housing DP as the control rotation part 42 for the drive shift of the main shaft 40, and any other component (differential A-axis DA, differential B-axis DB, pinion gear housing DP). ) Is configured as the drive output rotation part 43 of the main shaft 40, wherein the drive input rotation part 41 is provided with a first rotational power source P1, and the drive transmission control rotation part 42 is provided with the first rotation power source. The first shifted rotational force of the first rotational power source P1 is coupled to the rotational power source P1 by engagement of different gears 44D and 44E having a constant gear ratio and another gear 44F and 44I. Having second Division power source (P2) transmission using a single type of source of rotational power and gear combination, characterized by the granted. According to claim 1, wherein at least one differential gear unit (210) (210 ') and at least one planetary gear unit (110) (110') of the combined gear assembly 300 in parallel combined by the mutual axis parallel Is one component of the planetary gear unit 110 used as the main shaft 70 (sun gear (S), ring gear (R), planetary gear carrier (C)) or one of the differential gear unit (210) A component (differential A-axis DA, differential B-axis DB, pinion gear housing DP) is the drive input rotation part 71 of the main shaft 70, and another component (sun gear S, ring). Gear (R), planetary gear carrier (C) or differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)] as control rotation part 72 for drive shifting of main shaft 70. , The other main component (sun gear (S), ring gear (R), planetary gear carrier (C), or differential A axis (DA), differential B axis (DB), pinion gear housing (DP)) It consists of the drive output rotation part 73 of 70, and is used as the 1st sub-shaft 80. Is any component of the other planetary gear unit 110 'or the differential gear unit 210' (sun gear (S '), ring gear (R'), planetary gear carrier (C '), or differential A axis. (DA '), differential B-axis (DB'), pinion gear housing (DP ') as the input rotation part 81 of the first sub-shaft 80, and other components (sun gear (S'), ring gear (R '), planetary gear carrier (C') or differential A-axis (DA '), differential B-axis (DB'), pinion gear housing (DP ')] 82), and any other component (sun gear S ', ring gear R', planetary gear carrier C ', or differential A axis DA', differential B axis DB ', The pinion gear housing DP ′ as an output rotation part 83 of the first sub-shaft 80, wherein a first rotational power source P1 is provided to the drive input rotation part 71 of the main shaft 70, The input rotation part 81 of the first sub-axis 80 has different gears 74A and 74B having a constant gear ratio to the first rotational power source P1. A second auxiliary power source P2 having a primary shifted rotational force of the first rotational power source P1 is provided by the engagement, and the second control power source 82 is provided to the shift control rotation unit 82 of the first sub-axis 80. A third shifted rotational force of the first rotational power source P1 due to the engagement by engagement of different gears 74D, 74E and another gear 74F, 74I with a constant gear ratio to P2); The auxiliary power source P3 is provided, and the output rotation part 83 of the first subshaft 80 has different gears 74K (7J) having a constant gear ratio with the control rotation part 72 for driving shift of the main shaft 70. Transmission using a single type of rotational power source and gear combination, characterized in that coupled to the teeth of.
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US9347541B2 (en) * 2013-05-30 2016-05-24 GM Global Technology Operations LLC Modular power transfer unit assembly for a vehicle
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KR100965102B1 (en) 2009-11-26 2010-06-22 조재민 Two reply power source speed change gear using gear corporate bady
KR100965101B1 (en) 2009-11-09 2010-06-22 조재민 Two reply power source speed change gear using gear corporate bady

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JP4038460B2 (en) * 2003-09-04 2008-01-23 株式会社日立製作所 Active shift transmission, transmission control device, and automobile
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JP2009045993A (en) 2007-08-17 2009-03-05 Hitachi Ltd Vehicular control device and vehicular power transmission device
KR100965101B1 (en) 2009-11-09 2010-06-22 조재민 Two reply power source speed change gear using gear corporate bady
KR100965102B1 (en) 2009-11-26 2010-06-22 조재민 Two reply power source speed change gear using gear corporate bady

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