WO2012030083A9 - Appareil de transmission qui utilise une seule source de puissance rotative et un ensemble à engrenages - Google Patents

Appareil de transmission qui utilise une seule source de puissance rotative et un ensemble à engrenages Download PDF

Info

Publication number
WO2012030083A9
WO2012030083A9 PCT/KR2011/006026 KR2011006026W WO2012030083A9 WO 2012030083 A9 WO2012030083 A9 WO 2012030083A9 KR 2011006026 W KR2011006026 W KR 2011006026W WO 2012030083 A9 WO2012030083 A9 WO 2012030083A9
Authority
WO
WIPO (PCT)
Prior art keywords
gear
differential
power source
axis
rotation part
Prior art date
Application number
PCT/KR2011/006026
Other languages
English (en)
Korean (ko)
Other versions
WO2012030083A2 (fr
WO2012030083A3 (fr
Inventor
강성원
조재민
강동헌
한광희
Original Assignee
Kang Sung Woon
Cho Jae Min
Kang Dong Hun
Han Kwang Heui
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kang Sung Woon, Cho Jae Min, Kang Dong Hun, Han Kwang Heui filed Critical Kang Sung Woon
Publication of WO2012030083A2 publication Critical patent/WO2012030083A2/fr
Publication of WO2012030083A9 publication Critical patent/WO2012030083A9/fr
Publication of WO2012030083A3 publication Critical patent/WO2012030083A3/fr

Links

Images

Classifications

    • 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 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.
  • 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.
  • 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.
  • gear ratios in various places such as industrial machines, reducers, gearheads, hoists, goods transfer conveyors, winches, elevators, and escalators.
  • stepped transmissions and continuously variable transmissions that transmit the output rotation speed to the drive means of the drive shaft are widely used.
  • 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.
  • gear type or belt pulley type the gear ratio or the gear ratio of the longitudinal drive shaft is increased depending on the gear ratio and outer diameter
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 [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) (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;
  • DA differential A-axis
  • 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')]
  • 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.
  • 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.
  • the rotational driving force of the transmission using a single type of rotational driving force and a two-column gear assembly 100 ', 200', 300 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).
  • 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) )
  • the drive input rotation part 11 is provided with a first rotational power source P1
  • the shift control rotation part 12 has different gears 14D and 14E 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 by engagement with another gear 14F and 14I. It is supposed to.
  • 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 ′).
  • 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.
  • 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.
  • the differential gear assembly 200 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.
  • 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 In the output rotation part 53 of), the control rotation part 42 for driving shift of the main shaft 40 and the gears 44K and 44J having different gear ratios are coupled to each other.
  • 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)
  • one component of the differential gear unit 210 is used as the driving input rotation part 71 of the main shaft 70.
  • 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 ').
  • 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.
  • a second auxiliary driving force (P2) having a primary shifted rotational force of the first rotational driving force (P1) and the first sub-shaft
  • 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
  • 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.
  • 1 and 2 are each embodiment diagram showing the coupling relationship of each planetary gear assembly constituting the gear assembly of the present invention.
  • 3 and 4 are each embodiment showing the coupling relationship of each differential gear assembly constituting the gear assembly of the present invention.
  • 5 and 6 are each embodiment showing the coupling relationship of each composite gear assembly constituting the gear assembly of the present invention.
  • the present invention relates to a transmission apparatus using a single type of rotation power source and gear combination, wherein the rotational speed of the rotation power source transmitted from the driving input shaft is shifted to the gear ratio of the planetary gear unit or the differential gear unit to constitute a transmission.
  • a single type of rotation power source capable of arbitrarily variously extending the shift range with respect to the rotational speed of the drive output shaft.
  • a transmission using a gear assembly is formed by a combination of at least one planetary gear unit and at least one differential gear unit.
  • FIG. 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
  • FIG. 2 is a two-plane planetary gear unit 110 and 110 according to the present invention.
  • 'I a coupling cross-sectional view showing a coupling relationship according to the first embodiment of the planetary gear assembly 100' coupled to each other.
  • Table 1 shows the shifting process of the output rotational speed. saw.
  • 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.
  • the input rotation part 21 of the planetary gear unit 110 ′ of the first subshaft 20 has different gears 14A having a constant gear ratio with the driving input rotation part 11 of the planetary gear unit 110 of the main shaft 10.
  • 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 fourteenth 14B, and the planetary gear of the first auxiliary shaft 20 is attached to the shift control rotating unit 22.
  • the first rotational power source P1 by the engagement of the different gears 14D and 14E and the other gears 14F and 14I having the gear ratio constant with the input rotation part 21 and the outer peripheral surface of the unit 110 '.
  • the third auxiliary power source (P3) having a secondary shifted rotational force of is given, the output rotary unit 23 is a different gear (14K) (14J) having a constant gear ratio with the shift control rotary unit 12 of the main shaft (10). It is a structure combined with the combination of.
  • 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.
  • 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.
  • the speed change apparatus 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.
  • FIG. 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
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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 transmission 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.
  • the transmission device 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.
  • FIG. 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.
  • 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.
  • 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
  • the outer circumferential surface thereof is coupled to the gear 74J having a constant gear ratio.
  • 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.
  • 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.
  • 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.
  • the following table shows the shifting process of the output rotation speed. .
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.

Landscapes

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

Abstract

La présente invention concerne un appareil de transmission qui utilise une seule source de puissance rotative et un ensemble à engrenages. Plus particulièrement, la présente invention est une continuation de l'invention dont le titre est « Appareil de transmission qui utilise deux sources de puissance rotatives et un ensemble à engrenages » (demande de brevet enregistrée n° 10-2009-0115229) qui a été déposée par le demandeur. Lorsque la vitesse de rotation de la source de puissance rotative transférée de l'arbre d'entrée d'entraînement est changée par le rapport d'engrenage d'une unité engrenage satellite ou d'une unité engrenage différentiel, et est transférée à l'unité d'entraînement, l'ensemble à engrenages est constitué en associant au moins une ou plusieurs unités engrenages satellites et au moins une ou plusieurs unités engrenages différentiels. Alors, la plage de changement pour la vitesse de rotation de l'arbre de sortie d'entraînement est augmentée arbitrairement et largement.
PCT/KR2011/006026 2010-08-31 2011-08-17 Appareil de transmission qui utilise une seule source de puissance rotative et un ensemble à engrenages WO2012030083A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
KR1020100084504A KR101002175B1 (ko) 2010-08-31 2010-08-31 단일 종류의 회전동력원과 기어결합체를 이용한 변속장치
KR10-2010-0084504 2010-08-31

Publications (3)

Publication Number Publication Date
WO2012030083A2 WO2012030083A2 (fr) 2012-03-08
WO2012030083A9 true WO2012030083A9 (fr) 2012-04-05
WO2012030083A3 WO2012030083A3 (fr) 2012-05-24

Family

ID=43007351

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/KR2011/006026 WO2012030083A2 (fr) 2010-08-31 2011-08-17 Appareil de transmission qui utilise une seule source de puissance rotative et un ensemble à engrenages

Country Status (2)

Country Link
KR (1) KR101002175B1 (fr)
WO (1) WO2012030083A2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9347541B2 (en) * 2013-05-30 2016-05-24 GM Global Technology Operations LLC Modular power transfer unit assembly for a vehicle
CN105114557A (zh) * 2015-10-12 2015-12-02 李建利 高速比行星轮多级减速器

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5980410A (en) * 1998-09-28 1999-11-09 Caterpillar Inc. Electro-mechanical transmission
JP4038460B2 (ja) * 2003-09-04 2008-01-23 株式会社日立製作所 アクティブシフト変速機，変速機制御装置、および自動車
JP2009045993A (ja) 2007-08-17 2009-03-05 Hitachi Ltd 車両用制御装置および車両用動力伝達装置
KR100965101B1 (ko) 2009-11-09 2010-06-22 조재민 2개의 회전동력원과 기어결합체를 이용한 변속장치
KR100965102B1 (ko) 2009-11-26 2010-06-22 조재민 2개의 제어수단과 기어결합체를 이용한 변속장치
KR100982934B1 (ko) * 2010-03-30 2010-09-17 강성원 2개의 회전동력원과 기어결합체를 이용한 변속장치

Also Published As

Publication number Publication date
WO2012030083A2 (fr) 2012-03-08
KR101002175B1 (ko) 2010-12-17
WO2012030083A3 (fr) 2012-05-24
KR20100102082A (ko) 2010-09-20

Similar Documents

Publication Publication Date Title
WO2014081105A1 (fr) Système d'engrenage à synthèse d'entrée
WO2012036426A2 (fr) Système d'engrenage épicycloïdal utilisant deux caractéristiques d'entrée, module d'engrenage comprenant celui-ci et procédé pour le commander
WO2020218749A1 (fr) Dispositif de transmission de puissance
WO2013100620A1 (fr) Groupe motopropulseur à 10 vitesses d'une transmission automatique pour véhicule
WO2010134732A2 (fr) Transmission automatique multirapport
US8936529B2 (en) Ratio step of a stepped transmission, and stepped transmission
US9683632B2 (en) Multistage gearbox for motor vehicles
EP0300108A3 (fr) Transmission planétaire et dispositif à engrenages complexes à développante avec petite différence de dents
WO2013008976A1 (fr) Transmission manuelle automatisée
WO2012030083A9 (fr) Appareil de transmission qui utilise une seule source de puissance rotative et un ensemble à engrenages
WO2014069709A1 (fr) Cannelure souple à roue dentée accouplée à des corps élastiques et ailettes, et dispositif d'entraînement harmonique possédant celle-ci
WO2009088232A2 (fr) Train planétaire et appareil de transmission de puissance et leur utilisation
WO2019172582A1 (fr) Transmission de bicyclette utilisant un moteur à vitesse variable et un mécanisme d'engrenage planétaire
FR2618509B1 (fr) Reducteur a arbres paralleles ou orthogonaux a couple divise et rattrapage de jeux
WO2015156598A1 (fr) Appareil de synthèse d'entrée
KR100509325B1 (ko) 하이포이드 감속장치 및 그 그룹
WO2014069721A1 (fr) Groupe motopropulseur de transmission automatique
KR100965101B1 (ko) 2개의 회전동력원과 기어결합체를 이용한 변속장치
WO2011122766A2 (fr) Transmission utilisant deux sources de puissance de rotation et un ensemble engrenage
WO2014142369A1 (fr) Groupe motopropulseur pour transmission automatique
WO2017018763A1 (fr) Transmission automatique pour véhicule
JPS5845613B2 (ja) ヘンソクソウチ
WO2018124341A1 (fr) Bicyclette à transmission à étages multiples
WO2019198957A1 (fr) Transmission différentielle
KR100965102B1 (ko) 2개의 제어수단과 기어결합체를 이용한 변속장치

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 11822058

Country of ref document: EP

Kind code of ref document: A2

NENP Non-entry into the national phase in:

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 11822058

Country of ref document: EP

Kind code of ref document: A2