WO2011122766A2 - Transmission utilisant deux sources de puissance de rotation et un ensemble engrenage - Google Patents

Transmission utilisant deux sources de puissance de rotation et un ensemble engrenage Download PDF

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Publication number
WO2011122766A2
WO2011122766A2 PCT/KR2011/001176 KR2011001176W WO2011122766A2 WO 2011122766 A2 WO2011122766 A2 WO 2011122766A2 KR 2011001176 W KR2011001176 W KR 2011001176W WO 2011122766 A2 WO2011122766 A2 WO 2011122766A2
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WO
WIPO (PCT)
Prior art keywords
gear
differential
axis
shaft
main shaft
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PCT/KR2011/001176
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English (en)
Korean (ko)
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WO2011122766A3 (fr
Inventor
강성원
강동헌
한광희
조재민
Original Assignee
Kang Sung Woon
Kang Dong Hun
Han Kwang Heul
Cho Jae Min
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Application filed by Kang Sung Woon, Kang Dong Hun, Han Kwang Heul, Cho Jae Min filed Critical Kang Sung Woon
Publication of WO2011122766A2 publication Critical patent/WO2011122766A2/fr
Publication of WO2011122766A3 publication Critical patent/WO2011122766A3/fr

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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

Definitions

  • the present invention relates to a transmission using two rotational power sources and a gear assembly, and more particularly, to a transmission using two rotational power sources and a gear assembly (patent number: 10-2009-0107694) filed by the applicant of the present invention.
  • a continuous invention at least one planetary gear unit and at least one planetary gear unit when the rotational speed of the main power source transmitted from the drive input shaft constitutes a transmission gear shifted to the gear ratio of the planetary gear unit or the differential gear unit and transmitted to the drive means.
  • the gear ratio of the gear assembly to the rotational speed of the first rotational power source and the rotational speed of the auxiliary power source are determined by the multiple gear ratios of the gear assembly.
  • the first rotational power source is set to the rotational speed of the drive output shaft at the rotational speed set to the lowest input.
  • a shift range relates to transmission using the two rotary power source and the gear combination which can optionally variously expanded.
  • the input rotational speed of main motive power is shifted through the gear ratio to the driving shaft in various places such as industrial machines, hoists, conveyors for transferring goods, winches, elevators, and escalators according to the purpose.
  • Various types of stepped transmissions and continuously variable transmissions that transmit a variable speed of output are widely used.
  • the manual transmission and the automatic transmission are widely used for vehicles.
  • the efficiency of the engine is increased, but the driver There was a hassle to operate the transmissions according to the situation.
  • a separate power transmission means is added to one component of the planetary gear unit having a specific gear ratio, and the belt type continuously variable transmission device according to the power transmission form of the power transmission means. It can be divided into hydraulic continuously variable transmission and gearless continuously variable transmission.
  • a stepped gearbox or continuously variable transmission using a planetary gear unit consisting of a planetary gear carrier that connects a central sun gear, an outer ring gear, and a planetary gear therebetween as one. It is designed to change the rotational force of the axial rotational shaft by using two of these three elements, consisting of a ring gear and a planetary gear carrier, as input / output shafts and connecting a separate power control mechanism such as a clutch to the other one. .
  • 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)).
  • the output rotation speed is shifted only within a certain range.
  • 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.
  • the speed range of the output rotation speed is extremely limited. It had a fundamental problem.
  • the first object of the present invention for solving the above problems is to form a gear assembly with an extended gear ratio by a series combination of at least one planetary gear unit and at least one differential gear unit and to constitute the gear assembly. 2, which is capable of variously extending the transmission range of the output rotational speed of the drive output shaft by adding a first rotational power source serving as a main power source and a second rotational power source serving as an auxiliary power source to each one component of the different gear unit, respectively. To provide a transmission using two rotational power source and gear combination.
  • the second object of the present invention is to arbitrarily desired rotation of the initial output rotational speed of the drive output shaft from the stop output (0 RPM) by the multi-gear ratio by the combination of the components for each gear unit constituting the gear assembly It is to provide a transmission using two rotational power sources and a gear combination that can be adjusted by number.
  • the third object of the present invention is to be connected to any one component of the planetary gear unit or the differential gear unit used as the main shaft, the first rotational driving force (P1) and the main shaft of the engine is transmitted to the drive input rotation of the main shaft, and used as a minor
  • the rotational speed of the auxiliary power source is fixed at fixed speed or sequentially.
  • the variable speed can be selected to provide a transmission using two rotational power sources and gear combinations that can be used to increase the use of the transmission, such as a stepper transmission including a speed reducer, an industrial continuously variable transmission, and an automobile continuously variable transmission. There is.
  • Each component of the 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 formed by combining the planetary gear units 110 and 110 'in parallel with 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 ')], a differential gear assembly 200 formed by combining the respective differential gear units 210 and 210' in series to be parallel to each other by a gear tooth;
  • DA differential A-axis DA
  • DB differential B-axis
  • DP pinion gear housing
  • 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 ')] is a compound gear in which at least one planetary gear unit (110) (110') and at least one differential gear unit (210) (210 ') are combined in series to be parallel to each other by a gear tooth.
  • Combination 300 is composed of separate.
  • the rotational driving force P of the transmission using the two rotational driving force and the gear combination according to the present invention controls the speed ratio of the gear unit of the first rotational driving force P1 and the gear assembly (a) serving as the main power sources of the engine. It is composed of a second rotational driving force (P2) to be an auxiliary power source, the first rotational driving force (P1) is a first fixed power source (FP1) and the first variable power source (VP1) in which the rotational speed is changed in sequence
  • the second rotational driving force (P2) is divided into a second fixed power source (FP2) and a second variable power source (VP2) in which the rotational speed is sequentially changed.
  • At least one planetary gear unit 110, 110 ' is composed of a series combination by parallel to each other, two planetary gear units 110, 110'
  • the planetary gear assembly 100 formed of a mutual series combination of) is 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 control rotation part 12 for shifting, and any other.
  • One component (sun gear (S), ring gear (R), planetary gear carrier (C)) is composed of an output rotating section (13), and one of the other planetary gear units (110 ') used as the sub shaft (20).
  • One component is the input shaft 21 of the sub-shaft 20, and the other components (sun gear S', ring) Gear (R '), planetary gear catch Gear C '] as the sub-shaft 20 and the shift control rotation part 22, and any other component (sun gear S', ring gear R ', planetary gear carrier C').
  • the main shaft 10 Comprising a drive output rotating part 23 of the (20), the main shaft 10, the drive input rotation part 11 is given a first rotational driving force (P1) and the main shaft (10) to the input rotation part 21 of the main shaft (10) ) Is provided by the engagement of the output gear 13 and different gears 14D and 14E having a constant gear ratio, and the shift control rotary part 22 of the sub-shaft 20 is given a second rotational driving force P2. It is coupled with the shift control rotation part 12 of the main shaft 10 by the engagement of different gears 14B and 14C having a constant gear ratio, and the output rotation part 23 of the sub-shaft 20 is the input of the main shaft 10.
  • the first rotary power source P1 and the input second rotary power source P2 of the sub-shaft 20 are used as driving outputs of the final shifted rotation force after mutual coupling control.
  • the first rotational driving force P1 of the first fixed power source FP1 and the first variable power source VP1 is the planetary gear coupling body 100.
  • the second rotational driving force P2 of any one of the power sources VP2 is coupled to any one component of the other gear unit that is not coupled to the first rotational driving force P1 of the gear assembly A.
  • differential gear assembly 200 at least one or more differential gear units 210, 210 'are constituted in series by parallel interaxial parallelism, and the interaxial parallelism of two differential gear units 210 is established.
  • the differential gear assembly 200 in series combination by any one of the components of the differential gear unit 210 used as the main shaft 30 (differential A-axis (DA), differential B-axis (DB), pinion gear Housing DP] as the drive input rotation part 31 of the main shaft 30, and other components (differential A-axis DA, differential B-axis DB, pinion gear housing DP) are the main shaft 30;
  • Control rotation unit 32 for shifting, and any other component is output rotation 33 of the main shaft 30.
  • any one component of the other differential gear unit 210 'used as the sub-axis 40 (differential A-axis DA', differential B-axis DB ', pinion gear housing DP').
  • Input rotation of the auxiliary shaft (40) (41) the other components (differential A-axis DA ', differential B-axis DB', pinion gear housing DP ') are the shift control rotation part 42 of the sub-shaft 40
  • One of the other components includes a drive output rotating portion 43 of the sub-axis 40, wherein the main shaft ( 30.
  • the first input driving force P1 is applied to the driving input rotation part 31, and the input rotation part 41 of the subshaft 40 has different gears having a constant gear ratio with the output input rotation part 33 of the main shaft 30.
  • 34D) is provided by the engagement of the 34E
  • the shift control rotary section 42 of the sub-shaft 40 is the engagement of the different gear 34B (34C) is given a second rotational driving force (P2) and having a constant gear ratio.
  • P1 is coupled to the shift control rotation part 32 of the main shaft 30
  • the output rotation portion 43 of the sub-shaft 40 is the input first rotation power source (P1) of the main shaft 30 and the input of the sub-shaft 40 After two-rotation power source (P2) It is used as the drive output of the final shifted torque.
  • the composite gear assembly 300 of the present invention comprises at least one planetary gear unit (110) (110 ') and at least one differential gear unit (210) (210') in a series combination by parallel to each other axis.
  • the composite gear assembly 300 is composed of each component of the planetary gear unit 110, which is used as the main shaft 50 (sun gear (S), ring gear (R), planetary gear carrier (C)).
  • differential gear unit 210 (differential A axis DA, differential B axis DB, pinion gear housing DP) as the drive input rotation part 51 of the main shaft 50, ,
  • the other component (sun gear (S), ring gear (R), planetary gear carrier (C), or differential A axis (DA), differential B axis (DB), pinion gear housing (DP))
  • the other control element (sun gear (S), ring gear (R), planetary gear carrier (C), or differential A axis (DA), differential B axis (DB)).
  • Pinion gear housing (DP) Any one of the other planetary gear unit 110 'or the differential gear unit 210' constituted by the whole 53 and used as the subshaft 60 (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 61 of the sub-shaft 60, One component (sun gear (S '), ring gear (R'), planetary gear carrier (C ') or differential A-axis (DA'), differential B-axis (DB '), pinion gear housing (DP') Is the shift control rotation part 62 of the sub-axis 60, and any other component (sun gear S ', ring gear R', planetary gear carrier C ', or differential A axis DA').
  • a driving force P1 is applied to the input rotational portion 61 of the sub-shaft 60 and the different gear 54D having a constant gear ratio with the main shaft 50 axial rotational portion 53.
  • the shift control rotary part 62 of the subshaft 60 is coupled to the gears of different gears 54B and 54C given a second rotational driving force P2 and having a constant gear ratio.
  • the output rotation part 63 of the subshaft 60 has a final shift after the input first rotational power source P1 of the main shaft 50 and the input second rotational power source P2 of the subshaft 60 are mutually controlled. It is used as drive output of torque.
  • 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
  • the field of application has a very large effect that can be applied to various types of transmissions including a gear reducer and also for automobile and industrial use.
  • the engine power is transferred to the gear assembly to maximize the engine efficiency in the power transmission process, thereby reducing fuel costs, and having a simple structure, the compactness of the gear assembly that can realize a very large reduction ratio can be produced. As a result, the manufacturing cost can be significantly reduced, and thus the economic effect is very great.
  • 3 and 4 are views of each differential gear assembly constituting the gear assembly of the present invention.
  • 5 and 6 are views of each compound gear assembly constituting the gear assembly of the present invention.
  • Gear assembly 100 Planetary gear assembly
  • 10,30,50 Main axis
  • 20,40,60 Sub axis
  • 1 is a cross-sectional view showing a coupling relationship according to the first embodiment in which the gear assembly (a) of the present invention is formed of a planetary gear assembly (100) coupled to two rows of planetary gear units (110, 110 '), 2 is a cross-sectional view showing a coupling relationship according to the second embodiment of the planetary gear assembly 100 of the present invention.
  • the planetary gear carrier C of the planetary gear unit 110 of the main shaft 10 may include a main shaft in which the first variable power source VP1, in which the rotation speed of the first rotational power sources VP1 and FP1 is changed, is transmitted through the main shaft 10.
  • 10 is used as the drive input rotation part 11
  • the sun gear (S) is used as the shift control rotation part 12 of the main shaft 10 is coupled with the gear 14B having a constant gear ratio
  • the ring gear (R) is It is used as the output rotation part 13 of the main shaft 10 is coupled to the gear 14D having a constant gear ratio.
  • the planetary gear carrier C 'of the planetary gear unit 110' of the minor shaft 20 is used as the input rotation part 21 of the minor shaft 20, and has a gear 14E having a constant gear ratio, and the sun gear S ' ) Is transmitted to the shift control rotation part 22 of the sub-shaft 20 while receiving a second fixed power source FP2 having a constant rotation speed of the second rotational power sources VP2 and FP2 by engagement of different gears 14B and 14C.
  • Ring gear (R ') is used as the drive output rotation 23 of the sub-shaft 20.
  • the shift control rotation part 12 of the planetary gear unit 110 of the main shaft 10 is a different gear 14B having a constant gear ratio from the shift control rotation part 12 of the planetary gear unit 110 'of the sub-axis 20 ( 14C) coupled to each other, and the output rotation part 13 of the planetary gear unit 110 of the main shaft 10 has a constant gear ratio with the input rotation part 21 of the planetary gear unit 110 'of the sub-shaft 20. It is coupled by the engagement of different gears 14D and 14E.
  • the rotation ratio of each component (sun gear S ', ring gear R', planetary gear carrier C ') is set to 2: 1: 1
  • the shift control rotation part of the main shaft 10 The gear 14B built into the gear 12B and the gear 14C built into the shift control rotation part 22 of the sub shaft 20 have a gear ratio of 1: 1 so that the planetary gear unit 110 of the planetary gear unit 110 of the main shaft 10 may have a gear ratio of 1: 1.
  • the gear ratio of the sun gear S and the sub shaft 20 to the sun gear S 'of the planetary gear unit 110' is set to 1: 1 and is built up in the output rotation part 13 of the main shaft 10.
  • 14B) and the gear 14E arranged on the input rotation part 21 of the subshaft 20 have a gear ratio of 1: 1, and the ring gear R and the subshaft 20 of the planetary gear unit 100 of the main shaft 10 are rotated.
  • Set the rotation ratio for the planetary gear carrier C 'of the planetary gear unit 100' to 1: 1. The.
  • the transmission device has an input rotational speed in series combination by engaging each gear such that each component of at least one planetary gear unit 110, 110 'is parallel to each other. It is possible to arbitrarily extend the shift range of the output rotational speed with respect to.
  • the main gear 10 of the planetary gear unit 110 of the main shaft 10 includes a main shaft 10 through which a first variable power source VP1 having a change in rotation speed of the first rotational power sources VP1 and FP1 is transmitted through the main shaft 10.
  • the second fixed power source FP2 which is used as the driving input rotation part 11 of the second planetary gear carrier C, has a constant rotation speed of the second rotary power sources VP2 and FP2 due to the engagement of the different gears 14B and 14C. It is used as the transmission control rotation part 12 of the main shaft 10 while receiving the ring gear (R) is used as the output rotation portion 13 of the main shaft 10 is coupled to the gear 14D having a constant gear ratio.
  • the planetary gear carrier C ′ of the planetary gear unit 110 ′ of the subshaft 20 is used as an input rotation part 21 of the subshaft 20 and is coupled with different gears 14D and 14E having a constant gear ratio.
  • the sun gear S ' is shifted of the sub-shaft 20 while receiving a second fixed power source FP2 having a constant rotational speed of the second rotational power sources VP2 and FP2 by engagement of different gears 14B and 14C. It is used as the control rotation part 22, the ring gear (R ') is used as the drive output rotation part 23 of the sub-shaft 20.
  • the shift control rotation part 12 of the planetary gear unit 110 of the main shaft 10 may have different gears 14B having a constant gear ratio from the shift control rotation part 22 of the planetary gear unit 110 'of the sub-axis 20 ( 14C) coupled to each other, and the output rotation part 13 of the planetary gear unit 110 of the main shaft 10 has a constant gear ratio with the input rotation part 21 of the planetary gear unit 110 'of the sub-shaft 20.
  • the gears of the different gears 14E and 14D are engaged by each other.
  • the rotation ratio of each component (sun gear S ', ring gear R', planetary gear carrier C ') is set to 2: 1: 1
  • the shift control rotation part of the main shaft 10 The gear 14B built into the gear 12B and the gear 14C built into the shift control rotation part 22 of the sub shaft 20 have a gear ratio of 1: 1 so that the planetary gear unit 110 of the planetary gear unit 110 of the main shaft 10 may have a gear ratio of 1: 1.
  • the rotation ratio of the planetary gear carrier C and the subordinate shaft 20 to the sun gear S 'of the planetary gear unit 110' is set to 1: 1, and is built up in the output rotation part 13 of the main shaft 10.
  • the gear 14E built in the gear 14D and the input rotation part 21 of the sub-shaft 20 has a gear ratio of 1: 1, and the ring gear R and the sub-shaft of the planetary gear unit 110 of the main shaft 10.
  • Gear ratio of the planetary gear carrier 110 'to the planetary gear carrier C' is 1: 1. It was set up.
  • the speed change apparatus has an input rotational speed by a series combination of gears such that each component of at least one planetary gear unit 110, 110 ′ is parallel to each other. It is possible to arbitrarily extend the shift range of the output rotational speed with respect to.
  • the second embodiment is also not limited to the above-described setting example, and when the structure of the coupling type, the rotational speed and the gear ratio of the gears are arbitrarily changed, the gear ratio corresponding to the corresponding combination condition will appear, so as not to depart from the technical spirit of the present invention. Of course, it can be variously performed as long as it does not.
  • gear assembly (a) of the present invention comprises a differential gear assembly (200) coupled with two rows of differential gear units (210, 210 ')
  • 4 is a cross-sectional view showing a coupling relationship according to a fourth embodiment of the differential gear assembly 200 of the present invention.
  • the differential A-axis DA of the differential gear unit 210 of the main shaft 30 has a main shaft (1) through which the first variable power source VP1 in which the rotation speed of the first rotational power sources VP1 and FP1 is varied is transmitted through the main shaft 30 ( 30 is used as the drive input rotation part 31, the pinion gear housing (DP) is used as the shift control rotation part 32 of the main shaft 30, coupled with the gear 34B having a constant gear ratio, differential B axis DB is used as the output rotation part 33 of the main shaft 30 and is coupled to the gear 34D having a constant gear ratio.
  • differential gear unit 210' is used as the input rotation portion 41 of the sub-axis 40, coupled to the gear 34E having a constant gear ratio, pinion gear housing DP 'is used as the output rotation part 43 of the subshaft 40, and the differential A-axis DA' receives the second fixed power source FP2 while the rotation speed of the second rotation power source VP2, FP2 is constant. It is used as the shift control rotation part 42 of the 40 and is coupled with the gear 34C having a constant gear ratio.
  • the shift control rotation part 32 of the main shaft 30 differential gear unit 210 is different from the shift control rotation part 42 of the sub-gear 40 differential gear unit 210 ′ with different gears 34B ( 34C) coupled to each other, and the output rotation part 33 of the main shaft 30 differential gear unit 210 has a constant gear ratio with the input rotation part 41 of the sub-axis 40 differential gear unit 210 '.
  • the gears of the different gears 34D and 34E are engaged.
  • the gear 34C built in (42) has a gear ratio of 1: 1, and the differential of the pinion gear housing (DP) of the differential gear unit 210 of the main shaft 30 and the differential gear unit 210 'of the sub-axis 40 is different.
  • the rotation ratio with respect to the A-axis DA ' is set to 1: 1, and is built in the gear 34D built in the output rotation part 33 of the main shaft 30 and the input rotation part 41 of the sub-axis 40.
  • the gear 34E has a gear ratio of 1: 1.5, and the differential B axis DB 'of the main shaft 30 differential gear unit 210 and the differential B axis DB' of the sub-axis 40 differential gear unit 210 '.
  • the rotation ratio for was set at 1.5: 1.
  • the initial minimum input rotation speed of the first variable power source VP1 transmitted to the driving input rotation part 41 of the main shaft 40 is set at 700 RPM to 4,000 RPM.
  • the amount of change in the number of revolutions appearing in the output rotation part 43 of the subshaft 40 is shifted from 0 RPM to 1,200 RPM.
  • the transmission device has an input rotational speed in series 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 extend the shift range of the output rotational speed with respect to.
  • the pinion gear housing DP of the differential gear unit 210 of the main shaft 30 has a drive input rotation part of the main shaft 30 to which the first variable power source VP1 to which the rotation speed of the first rotation power source VP1 and FP1 is transmitted is transmitted. While used as (31) is coupled to the gear 34A having a constant gear ratio, the differential A-axis (DA) is used as a gear 34B having a constant gear ratio while being used as the shift control rotation part 32 of the main shaft (30). And, the differential B-axis (DB) is used as the output rotation portion 43 of the main shaft 40 is coupled with the gear 34D having a constant gear ratio.
  • the pinion gear housing DP 'of the sub-axis 40 differential gear unit 210' is used as an input rotation part 41 of the sub-axis 40, and is coupled with a gear 34E having a constant gear ratio.
  • DA ′ receives the second fixed power source FP2 having a constant rotation speed of the second rotary power sources VP2 and FP2 by the engagement of the different gears 34B and 34C. 42), the differential B-axis (DB ') is used as the drive output rotation portion 43 of the sub-axis (40).
  • the shift control rotation part 32 of the main shaft 30 differential gear unit 210 is different from the shift control rotation part 42 of the sub-gear 40 differential gear unit 210 ′ with different gears 34B ( 34C) coupled to each other, and the output rotation part 33 of the main shaft 30 differential gear unit 210 has a constant gear ratio with the input rotation part 41 of the sub-axis 40 differential gear unit 210 '.
  • the gears of the different gears 34D and 34E are engaged.
  • each component differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)
  • Pinion gear housing (DP) 2 differential A-axis (DA) + differential B-axis (DB)
  • the gear 34C built-in has a gear ratio of 1: 1 and the differential A axis DA of the differential gear unit 210 of the main shaft 30 and the differential A axis DA of the differential gear unit 210 'of the sub-axis 40.
  • the rotation ratio with respect to ') is set to 1: 1, and the gear 34E built in the output 34 of the main shaft 30 and the input wheel 41 of the sub-shaft 50 are built up. ),
  • the gear ratio is 1: 2
  • the rotation ratio of the differential B-axis (DB) of the differential gear unit 210 of the main shaft 30 and the pinion gear housing DP 'of the differential gear unit 210' of the sub-axis 40 is determined. 2: 1 was set.
  • the initial minimum input rotation speed of the first variable power source VP1 transmitted to the drive input rotation part 31 of the main shaft 30 is 4,000 RPM from 700 RPM.
  • Table 8 the amount of change in the number of revolutions appearing in the output rotation part 43 of the subshaft 40 is shifted from 0 RPM to 6,600 RPM.
  • the transmission according to the fourth embodiment of the present invention has an input rotational speed in series 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 extend the shift range of the output rotational speed with respect to.
  • FIG. 5 is a compound gear assembly in which any one gear unit (A) of the present invention is used as the main shaft (50) and any one planetary gear unit (110 ') used as the sub-axis (60).
  • Figure 6 is a coupling cross-sectional view showing a coupling relationship according to the sixth embodiment consisting of the composite gear coupling body 300 of the present invention.
  • the differential A-axis DA of the differential gear unit 210 of the main shaft 50 has a main shaft (1) through which the first variable power source VP1 in which the rotation speed of the first rotational power sources VP1 and FP1 is varied is transmitted through the main shaft 50 ( 50 is used as the input rotation part 51, the pinion gear housing (DP) is used as the shift control rotation part 52 of the main shaft 50 is coupled with the gear 54B having a constant gear ratio, differential B-axis ( DB) is used as the output rotation portion 53 of the main shaft 50 is coupled to the gear 54D having a constant gear ratio.
  • DP pinion gear housing
  • DB differential B-axis
  • the sun gear S 'of the subshaft 60 planetary gear unit 110' is used as the input rotation part 63 of the subshaft 60 and is coupled with the gear 54E having a constant gear ratio, and the ring gear R '.
  • the shift control rotary part of the sub-shaft 60 receives a second fixed power source FP2 having a constant rotational speed of the second rotational power source VP2, FP2 by engagement of different gears 54B and 54C having a constant gear ratio ( 62, and the planetary gear carrier C 'is used as the drive output rotation part 63 of the sub-shaft 60.
  • the shift control rotation part 52 of the main shaft 50 differential gear unit 210 is different gear 54B having a constant gear ratio from the shift control rotation part 62 of the planetary gear unit 110 'of the sub-shaft 60 ( 54C) coupled to each other, and the output rotation part 53 of the main shaft 50 differential gear unit 210 has a constant gear ratio with the input rotation part 61 of the planetary gear unit 110 ′ of the minor shaft 60. It is engaged by the engagement of the different gears 54D and 54E.
  • the gear 54C has a gear ratio of 1: 1, and the differential A axis DA of the differential gear unit 210 of the main shaft 50 and the ring of the planetary gear unit 110 'of the minor shaft 60 are fixed.
  • the rotation ratio with respect to the gear R ' is set to 1: 1, and is built up in the gear 54D and the input rotation part 61 of the sub-shaft 60 which are built in the output rotation part 53 of the said main shaft 50.
  • the gear 54E has a differential ratio of 1 to 1 with a differential B axis (DB) of the main shaft 50 and the differential gear unit 210. Was set to 1: minor axis 60, the rotation ratio for the "sun gear (S in), the planetary gear unit 100 '1.
  • the main shaft 50 is driven.
  • the output rotating unit 63 of the sub-shaft 60 appears. The result is that the amount of rotational speed changes from '0' RPM to '1,650' RPM.
  • the transmission device includes each component of any one differential gear unit 210 used as the main shaft 50 and any one planetary gear unit used as the sub shaft 60 ( 110 ') can be arbitrarily extended to the speed range of the output rotational speed to the input rotational speed by the combination of the gears to make each component parallel to each other axis.
  • the sun gear S of the planetary gear unit 110 of the main shaft 50 includes a main shaft 50 through which the first variable power source VP1 having the rotational speed of the first rotational power sources VP1 and FP1 is changed through the main shaft 50.
  • the planetary gear carrier (C) is used as the shift control rotation part 52 of the main shaft 50 and is coupled with the gear 54B having a constant gear ratio, and the ring gear R is used as the driving input rotation part 51 of the main shaft 50. It is used as the output rotation part 53 of the main shaft 50 is coupled to the gear 54D having a constant gear ratio.
  • the pinion gear housing DP 'of the sub-shaft 60 differential gear unit 210' is used as an input rotation portion 61 of the sub-shaft 60 and is coupled with a gear 54E having a constant gear ratio, and the differential A-axis ( DA ') shifts the subshaft 60 while receiving a second fixed power source FP2 having a constant rotational speed of the second rotational power source VP2, FP2 by engagement of different gears 54B and 54C having a constant gear ratio. It is used as the control rotation part 62, the differential B-axis (DB ') is used as the drive output rotation part 63 of the sub-shaft 60.
  • the shift control rotation part 52 of the main shaft 50 planetary gear unit 110 is different gear 54B having a constant gear ratio from the shift control rotation part 62 of the sub-shaft 60 differential gear unit 210 '( 54C) coupled to each other, and the output rotation part 53 of the planetary gear unit 110 of the main shaft 50 has a constant gear ratio with the input rotation part 61 of the differential gear unit 210 'of the sub-shaft 60. It is engaged by the engagement of the different gears 54D and 54E.
  • each component (sun gear (S), ring gear (R), planetary gear carrier (C)) of the main shaft 70 planetary gear unit 110 is set to 2: 1: 1 and the first sub-shaft (80)
  • the gear 54C built in the shift control rotation part 62 has a planetary gear carrier C of the planetary gear unit 110 and a subordinate shaft 60 of the planetary gear unit 110 at a gear ratio of 1: 1.
  • the rotation ratio with respect to the differential A axis DA ' is set to 1: 1, and the gear 54D and the input rotation part 61 of the sub-shaft 60 are arranged in the output rotation part 52 of the main shaft 50.
  • the gear 54E installed in the ring has a gear ratio of 1: 1 and a ring of the planetary gear unit 100 of the main shaft 50.
  • the rotation ratio with respect to the pinion gear housing DP 'of the gear R and the subshaft 60 differential gear unit 210' was set to 1: 1.
  • the transmission device includes each component of any one planetary gear unit 110 used as the main shaft 50 and any one differential gear unit used as the sub-shaft 60 (The combination of the gears to make the components of the 210 'are parallel to each other in parallel to each other in the series combination to be able to arbitrarily extend the transmission range of the output rotational speed to the input rotational speed.

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

Abstract

La présente invention concerne une transmission utilisant deux sources de puissance de rotation et un ensemble engrenage, et plus particulièrement, une transmission utilisant deux sources de puissance de rotation et un ensemble engrenage qui est formée en tant que transmission grâce à laquelle une vitesse de rotation d'une source de puissance principale transmise depuis un arbre d'entrée d'entraînement est changée par un rapport d'engrenage d'une unité d'engrenage planétaire ou d'une unité d'engrenage différentiel et transmise à un moyen d'entraînement. La transmission comporte un ensemble engrenage qui possède au moins une unité d'engrenage planétaire et au moins une unité d'engrenage différentiel, qui sont doublement combinées sur des arbres parallèles. Un rapport d'engrenage pour une vitesse de rotation d'une première source de puissance de rotation et un rapport d'engrenage pour une vitesse de rotation d'une source de puissance auxiliaire sont combinés de manière optimale au moyen de rapports d'engrenage multiples de l'ensemble engrenage, de telle sorte que, grâce à un apport de puissance optimal en provenance de la première source de puissance de rotation à une vitesse de rotation donnée, une plage de changement de vitesse pour la vitesse de rotation d'un arbre de sortie d'entraînement puisse être étendue de manière arbitraire et variable.
PCT/KR2011/001176 2010-03-30 2011-02-23 Transmission utilisant deux sources de puissance de rotation et un ensemble engrenage WO2011122766A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020100028267A KR100982934B1 (ko) 2010-03-30 2010-03-30 2개의 회전동력원과 기어결합체를 이용한 변속장치
KR10-2010-0028267 2010-03-30

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WO2011122766A2 true WO2011122766A2 (fr) 2011-10-06
WO2011122766A3 WO2011122766A3 (fr) 2011-12-29

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Publication number Priority date Publication date Assignee Title
KR101002175B1 (ko) * 2010-08-31 2010-12-17 강성원 단일 종류의 회전동력원과 기어결합체를 이용한 변속장치

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000108693A (ja) * 1998-09-28 2000-04-18 Caterpillar Inc 電気機械式トランスミッション
JP2005076875A (ja) * 2003-09-04 2005-03-24 Hitachi Ltd アクティブシフト変速機，変速機制御装置、および自動車
JP2005155843A (ja) * 2003-11-27 2005-06-16 Nissan Motor Co Ltd ハイブリッド車両の駆動装置
JP2009179208A (ja) * 2008-01-31 2009-08-13 Toyota Motor Corp ハイブリッド車両

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100965101B1 (ko) * 2009-11-09 2010-06-22 조재민 2개의 회전동력원과 기어결합체를 이용한 변속장치

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000108693A (ja) * 1998-09-28 2000-04-18 Caterpillar Inc 電気機械式トランスミッション
JP2005076875A (ja) * 2003-09-04 2005-03-24 Hitachi Ltd アクティブシフト変速機，変速機制御装置、および自動車
JP2005155843A (ja) * 2003-11-27 2005-06-16 Nissan Motor Co Ltd ハイブリッド車両の駆動装置
JP2009179208A (ja) * 2008-01-31 2009-08-13 Toyota Motor Corp ハイブリッド車両

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KR100982934B1 (ko) 2010-09-17
KR20100040282A (ko) 2010-04-19
WO2011122766A3 (fr) 2011-12-29

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