WO2011065659A9 - Dispositif de transmission utilisant deux moyens de commande et un ensemble engrenage - Google Patents

Dispositif de transmission utilisant deux moyens de commande et un ensemble engrenage Download PDF

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Publication number
WO2011065659A9
WO2011065659A9 PCT/KR2010/006758 KR2010006758W WO2011065659A9 WO 2011065659 A9 WO2011065659 A9 WO 2011065659A9 KR 2010006758 W KR2010006758 W KR 2010006758W WO 2011065659 A9 WO2011065659 A9 WO 2011065659A9
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Prior art keywords
gear
differential
axis
sub
ratio
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PCT/KR2010/006758
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English (en)
Korean (ko)
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WO2011065659A3 (fr
WO2011065659A2 (fr
Inventor
조재민
강동헌
한광희
강성원
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Publication of WO2011065659A2 publication Critical patent/WO2011065659A2/fr
Publication of WO2011065659A9 publication Critical patent/WO2011065659A9/fr
Publication of WO2011065659A3 publication Critical patent/WO2011065659A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • 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

Definitions

  • the present invention relates to a transmission using two control means and a gear assembly, and more particularly, a transmission using two rotational power sources and a gear combination, which is filed by the applicant of the present invention (application number: 10_2009 ⁇ 0107694).
  • application number: 10_2009 ⁇ 0107694 when the number of revolutions of the main power source transmitted from the drive input shaft constitutes a transmission in which the gear ratio of the planetary gear unit or the differential gear unit is transmitted to the drive means, at least one planetary gear unit and After constructing a gear assembly by combining at least one differential gear unit in double or triple by parallel to the shaft, the ratio of the gear ratio to the rotational speed of the rotating power source is determined by the multiple gear ratio of the gear assembly. By controlling through the speed, the speed of the drive output shaft is changed from the speed at which the drive rotational power source is set to the lowest input.
  • the above relates to a speed change device with two control means and the gear combination which can optionally variously expanded.
  • the engine efficiency is increased when the stepped transmissions, such as L and L, in which a manual transmission and an automatic transmission are widely used for a vehicle, are applied. There was a hassle for the driver to manipulate the transmissions according to the situation.
  • the continuously variable transmissions that can improve the fuel efficiency and maintain the optimum driving conditions for automobiles and industrial use by eliminating the high power transmission efficiency and eliminating the shift stratification during driving without automatically manipulating the transmissions.
  • a separate power transmission means is added to one component of the planetary gear unit having a specific gear ratio, and the belt type stepless transmission is performed according to the power transmission form of the power transmission means. It can be divided into transmission, hydraulic continuously variable transmission and gearless continuously variable transmission.
  • the hydraulic continuously variable transmission has a large shear force of lubricant due to rolling contact of the rotating body. Power can be transmitted, but as a separate hydraulic device for controlling the power transmission means requires weight and price due to a complicated structure and fuel consumption
  • a stepped gearbox or continuously variable transmission using a planetary gear unit consisting of a center sun gear, an outer ring gear, and a planetary gear carrier connecting the planetary gears therebetween as one is a sun gear.
  • These three elements which consist of gears, ring gears and planetary gear carriers, use two elements as input / output shafts and the other one connects a separate power control mechanism such as a clutch to change the rotational force of the entire shaft. It is.
  • the conventional stepped transmission or continuously variable transmissions using the planetary gear units as described above are provided at the designated gear ratios of the respective components of the planetary gear unit (sun gear (S), ring gear (R), planetary gear carrier (C)).
  • the output rotation speed is limited, the shift of the output rotation speed is made only within a certain range, in particular, due to the characteristics of the planetary gear unit composed of a combination of the sun gear and the ring gear planetary gear carrier Since the size is relatively limited to a certain ratio, the transmission range of the output rotation speed using the gear ratio of each component to the planetary gear unit exceeds the range of 3: 1 to 6: 1. Due to the difficult structure, the conventional continuously variable transmission using a single or a plurality of planetary gear units has a very limited range of speed of output rotation. With fundamentally limited underlying issues
  • La, lb, and lc are embodiments showing the coupling relationship of each planetary gear assembly constituting the gear assembly of the present invention.
  • Figure 2a, 2b, 2c is an embodiment showing the coupling relationship of each differential gear coupling constituting the gear coupling of the present invention
  • Figures 3a, 3b, 3c, 3d is an embodiment showing the coupling relationship of each composite gear assembly constituting the gear assembly of the present invention
  • 4A, 4B, and 4C are other examples of the actual view showing the coupling relationship of the composite gear coupling bodies constituting the gear coupling body according to the present invention.
  • the first object of the present invention is any one of any one gear unit that constitutes a gear assembly in which the gear ratio is extended by a combination of at least one planetary gear unit and at least one differential gear unit and is used as a main shaft of the gear assembly.
  • Adds a rotational power source to the component adds a first control means to one component of the other gear unit used as the first sub-shaft, and adds a second control means to the other component respectively to rotate the output of the drive output shaft. It is to provide a transmission using two control means and a gear combination that can be variously extended the transmission range for the number.
  • the second object of the present invention is to arbitrarily desire the initial output rotational speed of the drive output shaft from the stationary output (0 RPM) by means of multiple gear ratios by the sum of the components for each gear unit constituting the gear assembly. To provide a transmission using two control means and a gear combination that can be adjusted by the electrolyzed water.
  • the third object of the present invention is the main power of the engine as the drive input rotation of the main shaft while being connected to any one component of the planetary gear unit or differential gear unit used as the main shaft
  • First control means having a function of shifting to a shift control rotating part of the first sub-shaft while being connected to a rotational driving force (P) through which a circle is transmitted and a planetary gear unit or a car synchronous gear unit used as the first sub-shaft.
  • P rotational driving force
  • F1 and the second control means F2 having another shifting function as the output rotation part of the first sub-shaft, respectively, so that the drive output rotation part of the main shaft is independent of the variation of the input rotational speed of the rotational driving force P. It provides a transmission using two gears and a gear combination that can always maintain a stationary output (0 RPM).
  • each component of the planetary gear unit or the differential gear unit of each gear assembly can arbitrarily expand the range of the output rotation speed by each gear ratio by the engagement of different gears having a constant gear ratio.
  • the present invention provides a transmission using two control means and a gear assembly.
  • the gear combination of the transmission using the two control means and the gear combination according to the present invention (A) is a component of each of the at least one planetary gear unit (110K110 ' ) (110') [sun gear (SKS ' ) ( S ' ), ring gears (R) (R ' ) (R ' ), planetary gear carriers (C) (C) (C)] are geared to each planetary gear unit (110) (110 ' ) (110 " ) Planetary gear assembly (100) (100 ' ), which is a parallel combination of the two axes in parallel with each other; and each component of the at least one differential gear unit (210) (210 ' ) (210 " ) [differential A Axis (DAKDA ' ) (DA " ), Differential B-axis (DB) (DB ' ) (DB " ), Pinion Gear Housing
  • the rotational driving force (P) of the transmission using the two control means and the gear combination according to the present invention becomes the main power source of the engine, the fixed power source (FP) and the variable power source in which the rotational speed is changed in sequence VP).
  • the planetary gear assembly (100K100 ') of the present invention comprises at least one planetary gear unit (110K110') (11 ( ⁇ ) is composed of a parallel combination by parallel to each other, two planetary gear units (110K110)
  • the planetary gear assembly 100 composed of mutually parallel combinations of the two components includes any of the components of the planetary gear unit 110 used as the main shaft 10 (sun gear (S), ring gear (R), Planetary gear carrier (C)]
  • the planetary gear carrier ()] is the first sub-axis 20, the shift control rotation part 22, and any other component [sun gear (S ' ), ring gear (R ' ), planetary gear carrier (;)]. It consists of a first sub-axis output rotation unit 23, the main shaft () driving input rotation unit 11 is given a rotational driving force ( ⁇ ) and the input rotational unit 21 of the first sub-shaft (20) a rotational driving force ( ⁇ ) the mouth of the main shaft 10 It is given by the engagement of the rotating gear 11 and the different gears 1 AX14B having a constant gear ratio, and the shift control rotating part 22 of the first subshaft 20 has a first control means F1 having a control function.
  • the output rotation part 23 of the first subshaft 20 has a control rotation part 12 for driving shift of the main shaft 10 with the addition of a second control means F2 having another control function.
  • different gears 14E and 14D having a constant gear ratio.
  • the other planetary gear assembly (100 ':) of the present invention in three rows has another planetary gear unit (110): used as the second shaft 30 in the two-plane planetary gear assembly (100).
  • One component of another planetary gear unit 110 ⁇ used as the second sub-axis 30 as a parallel combination by parallel between axes [sun gear (S ' ), ring gear (R " ), planetary gear carrier ((;)] As the input rotation part 31 of the second sub-shaft 30, and the other
  • the component [sun gear (S-), ring gear ( ⁇ ), planetary gear carrier (;)] is the variable speed control rotation part 32 of the second subshaft 30, and any other component [sun gear S -), Ring gear (R “), planetary gear carrier ()] is composed of the output rotation part 33 of the second sub-axis (30), the main shaft ( 10)
  • the gear shifting control part of the secondary shaft 30 is coupled to the gear of different gears 14A, 14B, 14G, 14G 'with a constant gear ratio from the driving input rotation part 11; 32 is provided with the first control means F1 having a control function by the engagement of different gears 14C 'and 14K' with a constant gear ratio, and the output rotation part 33 of the second sub-shaft 30.
  • the rotational driving force (P) of the fixed power source (FP) and the variable power source (VP) is a planetary gear assembly ( ⁇ ') And the main shaft (10) (40) (70) of the gear unit constituting the gear assembly of any one of the differential gear assembly (200) (200') and the composite gear assembly (300) (30 0 ' ).
  • the differential gear assembly 200K200 'of the present invention includes at least one difference synchronizing gear unit 210K210' or 210 "in a parallel combination by parallelism between two axes, and two differential gear units 210
  • One of the components 210 is a drive input rotation part 41 of the main shaft 40, and another component [ Differential A-axis (DA), differential B-axis (DB), pinion gear housing (DP)] as the control rotation part 42 for shifting the main shaft 40, and any other component [differential A-axis (DA) , Differential B-axis (DB), pinion gear housing (DP)] is composed of the drive output rotation part 43 of the main shaft 40, the other differential gear unit (210 ' ) used as the first sub-shaft (50);
  • One component (differential A-axis (DA ' ), differential B-axis (DB ' ), pinion gear housing (DF;) as the input rotation part 51 of the first sub-shaft 50, and the other configuration Element [differential A-axis (DA ' ), differential B-axis (DB'), pinion gear housing (DF
  • the output rotation part 53 of the first sub-shaft 50 is added to the second control means (F2) having another control function While being coupled to the drive gear control rotation part 42 of the main shaft 40 and the engagement of the different gear 44EX44D having a constant gear ratio.
  • Another differential gear assembly 200 'of the present invention in three rows is another differential gear unit which is used as the second sub-axis 60 in the two-gear differential gear assembly 200.
  • Correction Paper (Rule Article 91) (210 ') is a parallel combination by mutual axis parallelism, and one component of another differential gear unit 2 ⁇ used as the second sub-axis 60 (differential A-axis DA-, differential B-axis ( DB ”) and the pinion gear housing (DP * :)] as the input rotation part 61 of the second sub-shaft 60, and the other components (differential A-axis (DA * ), differential B-axis (DB-) ,
  • the pinion gear housing (D :)] is the shift control rotation part 62 of the second sub-shaft 60, and any other component [differential A-axis (DA ' ), differential B-axis (DB ' ), pinion Gear housing (D :)] as an output rotating part (63) of the second sub-shaft (60), and the input rotating part (61) of the second sub-shaft (60) from the main shaft (40) driving input rotating part (41).
  • the gears of the second sub-shaft 60 are coupled to the gears of different gears 4A, 44B, 44G, and 4G 'with a constant gear ratio, and the shift control rotary part 62 of the second subshaft 60 has different gear ratios.
  • the first control means (F1) having a control function is provided, and the second control means (F2) having another control function is added to the output rotating portion (63) of the second sub-shaft (60), the first sub-shaft 50 is composed of a combination of the transmission control rotation part 52 and the gear of the different gears 44J 44H having a constant gear ratio.
  • the composite gear assembly 300 (300 ') of the present invention includes at least one planetary gear unit ( ⁇ ') 110- and at least one differential gear unit 210 (21 0 ') (210-). ) Are composed of parallel combinations of parallel axes, and the two-column composite gear assembly 300 is composed of each component of the planetary gear unit 110, which is used as the main shaft 70 (sun gear (S). ), Ring gear (R), planetary gear carrier (C)] or each component of any one differential gear unit (differential A-axis ( ⁇ ), differential B-axis (DB), pinion gear)
  • One component of the housing (DP) is the drive input rotation part 71 of the main shaft 70, and the other component (sun gear (S), ring gear (R), planetary gear carrier (C), or differential A).
  • Rotational driving force (P) is applied to the drive input rotational portion 71 of the main shaft 70, and the rotational driving force (P) is applied to the input rotational portion 81 of the first sub-axis (80) It is given by the engagement of the input gear 71 and the different gear 74AK74B having a constant gear ratio, the shift control rotary part 82 of the first sub-shaft 80 is the first control means (F1) having a control function Is added and coupled, and the output rotation part 83 of the first sub-shaft 80 is a control rotation part 72 for driving shift of the main shaft 70 with the addition of the second control means F2 having another control function.
  • Another compound gear assembly 300 'of the present invention in three rows is another planetary gear unit (11 0') or differential gear unit used as the second sub-axis 90 in the two-gear composite gear assembly (300)
  • a first control means (F1) is be given, and the second minor axis 90, with the control by the engagement of with a constant gear ratio
  • the second control means (F2) with another control function is added to the structure coupled to the engagement of the gear shifting control part 82 of the first sub-axis 80 and the different gear (74JK74H) having a constant gear ratio. It is.
  • Fig. La shows the gear assembly (a) of the present invention in two rows of planetary gear units (110) (110';). Is a cross-sectional view showing a coupling relationship according to the first embodiment of the planetary gear assembly (100) coupled to, Figure lb shows a coupling relationship according to the second embodiment of the planetary gear assembly (100) of the present invention.
  • 1 is a cross-sectional view
  • FIG. Lc shows a gear assembly (A) according to the third embodiment, which is formed of a planetary gear assembly 100 'coupled to three planetary gear units 110, 110' and 110 '. It is a cross-sectional view showing the coupling relationship.
  • the minimum rotational speed of P1 is 700rpm
  • the rotation ratio (S: C: R) of each planetary gear unit is 5: 1: 1
  • the gear rotation ratio of 14A: 14B is 5: 1
  • the gear rotation ratio is 1: 1
  • the gear rotation ratio of 14D: 14E is 1: 1
  • the control ratio of F1 is a value for the rotational speeds of the first minor planetary gear and the sun gear
  • the control ratio of F2 is the first minor planetary
  • the numerical value of the rotation speed of a gear and a ring gear is shown.
  • the main gear 10 of the planetary gear unit 110 has a drive input rotating part 11 of the main shaft 10 through which the variable power source VP, in which the rotational speed of the rotational power source P is varied, is transmitted through the main shaft 10.
  • the planetary gear carrier (C) is used as the shift control rotation part 12 of the main shaft 10 and the outer circumferential surface is geared with a constant gear ratio (14D).
  • the ring gear (R) is used as the output rotation portion 13 of the main shaft (10).
  • the sun gear S 'of the first subshaft 20 and the planetary gear unit 110' is used as the input rotating portion 21 of the first subshaft 20, and is coupled to the gear 14B having a constant gear ratio.
  • the planetary gear carrier () is used as the shift control rotary part 22 of the first subshaft 20 while receiving a control function from the first control means F1 by the engagement of the gears 14CX14K having different outer circumferential surfaces.
  • the ring gear R ' is received as another control function from the second control means F2 and used as the output rotation part 23 of the first subshaft 20, and is coupled with the gear 14E having a constant gear ratio.
  • the driving input rotation part 11 of the planetary gear unit 110 of the main shaft 10 may have different gears 14AX14B having a constant gear ratio with the input rotation part 21 of the planetary gear unit 110 ′ of the first subshaft 20. Is coupled by the teeth of the main shaft 10 planetary group
  • the rotation ratio of each of the components [sun gear (S ' ), ring gear (R ' ), planetary gear carrier ()] is set to 5: 1: 1, and then the drive input rotation part of the main shaft 10 is rotated.
  • the gear 14A built into the gear 11 and the gear 14B built into the input rotary part 21 of the first sub-shaft 20 have a gear ratio of 1: 1 and have a planetary gear unit 100 having a gear ratio of 1: 1.
  • first control means (F1) and the second control means (F2) to operate by receiving the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the spindle 10 ( 11)
  • the initial minimum input rotational speed of the variable power source (VP) transmitted from 700RPM to 3,500RPM as shown in the following ⁇ Table 1>
  • the amount of change of rotational speed appearing in the output rotation part 13 of the main shaft 10 The result is a shift from '0' RPM to '700, RPM.
  • correction Paper That is, the transmission according to the first embodiment of the present invention rotates the input by a combination of gears in which at least one of the planetary gear units 110 (110 ':) of each of the components are parallel to each other in parallel.
  • the speed range of the output rotational speed can be arbitrarily expanded, and the engine brake can be operated through two control means (stop mode) when a sudden braking is required, so that safety can be achieved during operation.
  • Component 14D in Table 1 shows the theoretical value of the rotation ratio of the planetary gear unit 110 with respect to the input shaft 11 of the main shaft 10.
  • the minimum rotational speed of P1 is 700rpn
  • the rotational ratio (S: C: R) of each planetary gear unit is 5: 1: 1
  • the gear rotation ratio of 14A: 1 ⁇ is 5: 1
  • 14C: 14K The gear rotation ratio of is 1: 1
  • the gear rotation ratio of 14D: 14E is 1: 1
  • the control ratio of F1 is the number of revolutions of the first minor planetary gear and the sun gear
  • the control ratio of F2 is the first minor axis.
  • the number of revolutions of the planetary gear and the ring gear is shown.
  • the main gear 10 of the planetary gear unit 110 includes a drive input rotating part 11 of the main shaft 10 through which the variable power source VP, in which the rotational speed of the rotational power source P is varied, is transmitted through the main shaft 10.
  • the variable power source VP in which the rotational speed of the rotational power source P is varied, is transmitted through the main shaft 10.
  • the planetary gear carrier C is used as a shift control rotation part 12 of the main shaft 10, and the outer peripheral surface of the gear has a constant gear ratio 14D.
  • the ring gear (R) is used as the output rotation portion 13 of the main shaft (10).
  • Correction Paper (Rule Article 91) It is used as the entire shift control assembly 22 of the first subshaft 20 while receiving a control function from the first control means Fl, and the ring gear R 'is another controller from the second control means F2. It is used as the output rotation part 23 of the first sub-shaft 20 by receiving the function.
  • the drive input rotation part 11 of the planetary gear unit 110 of the main shaft 10 may have different gears 14AK14B having a constant gear ratio with the input rotation part 21 of the planetary gear unit 110 ′ of the first subshaft 20.
  • the shift control rotation part 12 of the planetary gear unit 110 of the main shaft 10 is a shift control rotation part 22 of the first part shaft of the planetary gear unit 110 'of the first sub shaft 20.
  • other gears (14EK14D) with a constant gear ratio are joined together.
  • the rotation ratio of each of the components [sun gear (S '), ring gear (R'), planetary gear carrier (;) is set to 5: 1: 1, and then the drive input rotation part of the main shaft (10)
  • the gear 14A built into the gear 11 and the gear 14B built into the input rotating part 21 of the first sub-shaft 20 have a gear ratio of 1: 5 and the main shaft 10 of the planetary gear unit 100.
  • the transmission according to the second embodiment of the present invention rotates the input by a combination of gears in which at least one planetary gear unit 110 (110 ' :) of the components are parallel to each other in parallel.
  • the speed range of the output rotational speed can be arbitrarily extended, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.
  • the second embodiment is also not limited to the above configuration example, the structure of the combined form. If the control ratio of each control means, each gear ratio is arbitrarily changed, the transmission ratio corresponding to the corresponding combination conditions will appear, so that it can be variously implemented within the scope not departing from the technical spirit of the present invention.
  • the element 14C represents the theoretical value of the rotation ratio of each planetary gear unit 110 with respect to the input electric charger 11.
  • the minimum rotational speed of P1 is 700 rpm, and the rotation ratio (S: C: R) of each planetary gear unit is 4: 1: 1.
  • the gear rotation ratio of 14A: 14B is 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 1: 14E: 14D gear ratio is 1: 1, the control ratio of F1 is the number of revolutions of the first minor planetary gear and the sun gear, the control ratio of F2 is the first minor planetary gear and the ring The numerical value of the rotation speed of a gear is shown.
  • the sun gear S of the main shaft 10 and the planetary gear unit 110 has a rotational speed of the rotational power source P.
  • Variable variable power source (VP) is used as the drive input rotating part 11 of the main shaft 10 transmitted through the main shaft 10, and is coupled with the gear 14A having a constant gear ratio, and the planetary gear carrier C Is used as the shift control rotation part 12 of the main shaft 10, the outer peripheral surface is coupled to the gear 14D having a constant gear ratio with the gear, the ring gear (R) is used as the output rotation portion 13 of the main shaft 10 do.
  • the sun gear S 'of the first subshaft 20 and the planetary gear unit 110' is used as the input rotation part 21 of the system 1 subshaft 20 and is coupled with a gear 14BK14G having a constant gear ratio.
  • the gear carrier C is used as the shift control rotation part 22 of the first subshaft 20, and the outer circumferential surface thereof is coupled to the gear 14J having a constant gear ratio, and the ring gear R ' is the first subshaft. It is used as the output rotation part 23 of the 20 and is coupled with the gear 14E having a constant gear ratio.
  • the sun gear S 'of the second subshaft 30 planetary gear unit 11 ( ⁇ :) is used as an input rotation part 31 of the second subshaft 30 and is coupled with a gear 14G ' having a constant gear ratio.
  • the planetary gear carrier is shifted on the second subshaft 30 while receiving a control function from the first control means F1 by the engagement of the gears 14C (14 ⁇ ' ) with different peripheral surfaces. It is used as the control rotation part 32, the ring gear 0 ⁇ is received as another control function from the second control means (F2) is used as the output rotation part 33 of the second sub-shaft 30, the gear having a constant gear ratio It is combined with 14H.
  • the drive input rotation part 11 of the main shaft 10 planetary gear unit 110 is a low U
  • correction paper (rule 91)
  • the shaft 20 is coupled to the input rotation part 21 of the planetary gear unit 110 'by the engagement of different gears 14AK14B having a constant gear ratio, and the shift control of the planetary gear unit 110 of the main shaft 10 is carried out.
  • the rotating part 12 is coupled by engagement of the output rotating part 23 of the planetary gear unit 110 'of the first subshaft 20 with different gears 14EK14D having a constant gear ratio.
  • the input rotating part 21 of the first gear shaft 20 and the planetary gear unit 110 ' has a different gear 14G having a constant gear ratio from the input rotating part 31 of the planetary gear unit 1 ⁇ . 14G ') is coupled to each other, and the shift control rotation part 22 of the first subshaft 20 and the planetary gear unit 110' is the output rotation part of the planetary gear unit 110 'of the second subshaft 30. 33) and the other gears (14JK14H) with a constant gear ratio are engaged.
  • correction paper (rule 91)
  • the gear ratio of the gear S 'and the second subshaft 30 to the sun gear s- of the planetary gear unit ii (r) is set to 1: 1: 1, and the shift control rotation part of the main shaft 10 is set.
  • the gear 14D built into the gear 12D and the gear 14E built into the output rotating part 23 of the first subshaft 20 set the gear ratio to 1: 1, and the gear 14D of the first subshaft 20
  • the gear 14H built in the speed change control rotating section 22 and the gear 14H built in the output rotating section 33 of the second sub shaft 30 set the gear ratio to 1: 1.
  • the theoretical value with respect to the rotation ratio of 14D is shown, and the control ratio of the 1st control means F1 is a theoretical value rotation ratio of the gear 14C 'with respect to the rotation ratio of the input rotation part 31 of the 2nd sub-axis 110'.
  • the control ratio of the second control means F2 represents the control ratio with respect to the theoretical value rotation ratio of the gear 14J with respect to the rotation ratio of the entire input rotation 21 of the first sub-axis 110 '.
  • the transmission in accordance with the third embodiment of the present invention is a parallel combination by engaging each gear such that each component of at least three or more planetary gear units 110K110 'and 110 ": is parallel to each other.
  • the range of shift of the output rotational speed to the input rotational speed can be arbitrarily extended, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.
  • the present invention is not limited to the above-described setting examples, and if the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear, without departing from the technical spirit of the present invention. Of course, it can be variously performed within the scope.
  • FIG. 2A shows that the gear combiner (A) of the present invention comprises two rows of differential gear units 210 (210 ' ).
  • a coupling cross-sectional view showing a coupling relationship according to a fourth embodiment of the differential gear coupling body 200 coupled to FIG. 2b shows a coupling relationship according to a fifth embodiment of the differential gear coupling body 200 of the present invention.
  • Fig. 2C shows a sixth embodiment in which the gear assembly (A) consists of a differential gear assembly (200 ' :) in which three gear arrays (210) (210') and 210 "are coupled to each other. Is a cross-sectional view showing the coupling relationship according to
  • the minimum rotational speed of P1 is 700rpm
  • the gear rotation ratio of 4A: 44B is 2: 1
  • the gear rotation ratio of 44C: is 1: 1.
  • 44D The gear rotation ratio of 44E is 1: 1
  • the control ratio of F1 is the value for the first sub-axis differential gear and the pinion housing rotation speed
  • the control ratio of F2 is the rotational speed of the first sub-axis differential gear and the differential B axis
  • the numerical value is shown.
  • the differential A axis (DA) of the main shaft (40) and the differential gear unit (210) has
  • Variable variable power source (VP) is used as the drive input rotation part 41 of the main shaft 40 transmitted through the main shaft 40, and is coupled with the gear 44A having a constant gear ratio
  • the pinion gear housing (DP) Is used as the shift control rotation part 42 of the main shaft 40, and is coupled with the gear 44D having a constant gear ratio
  • the differential B axis DB is used as the output rotation part 43 of the main shaft 40. do.
  • the differential A-axis DA 'of the differential gear unit 210 ' of the first sub-shaft 50 is used as the input rotation part 51 of the first sub-shaft 50 and is coupled with 44B having a constant air ratio.
  • the pinion gear housing D is used as the entire shift control assembly 52 of the first sub-shaft 50 while receiving a control function from the first control means F1 by the engagement of the different gears 44CK44K.
  • the axle shaft DB '> receives another control function from the second control means F2 and is used as the output rotation part 53 of the first subshaft 50, and is coupled with the gear 44E having a constant gear ratio.
  • the drive input rotational portion 41 of the differential gear unit 210 of the main shaft 40 has a different gear 44AK4 having a constant gear ratio with the input rotational portion 51 of the differential gear unit 210 'of the first sub-axis 50.
  • the shift control rotary part 42 of the main shaft 40 differential gear unit 210 is the first Shaft 50 is coupled over thing by the coupling of the differential gear unit (210 ') the output rotation part 53 and the different gear (44DK44E) with a constant gear ratio.
  • each component of each differential gear unit (210K210 ' ) [differential A-axis (DA, D
  • first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (40).
  • the initial minimum input rotational speed of the variable power source (VP) transmitted to (41) from 700RPM to 3,500RP the variation in the rotational speed appearing in the output rotation part 43 of the main shaft 40 as shown in Table 4 below.
  • the result is a shift from the '0' RPM to the '3,500' RPM.
  • the transmission according to the fourth embodiment of the present invention has an input rotational speed in parallel combination by engaging each gear such that each component of at least one or more differential gear units 210, 210 ' is parallel to each other. It is possible to arbitrarily expand the speed range of the output rotational speed of the engine, and the engine brake is operated through two control means (stop mode) to ensure safety during operation.
  • the fourth embodiment is also not limited to the above-described setting example, and if the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously performed as long as it does not deviate.
  • Component 44D in Table 4 shows the theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation part 41.
  • the rotation speed of P1 is 700rpm
  • the gear reduction ratio of 4A: 44B is 4: 1
  • the gear rotation ratio of 44D: 44E is fixed paper.
  • It is 1: 1
  • the control ratio of Fl is the numerical value for the electromagnetism of the first sub-axis differential gear and the differential A axis
  • the control ratio of F2 is the numerical value for the rotational speed of the first sub-axis differential gear and the differential B axis.
  • the differential A-axis DA of the differential gear unit 210 of the main shaft 40 has a drive input rotation of the main shaft 40 through which the variable power source VP whose rotational speed of the rotational power source P1 is varied is transmitted through the main shaft 40. It is used as part 41 and is coupled to the gear 44A having a constant gear ratio, and the pinion gear housing DP is used as the shift control rotation part 42 of the main shaft 40 and the gear 44D having a constant gear ratio.
  • the differential B axis DB is used as the output rotation part 43 of the main shaft 40.
  • the pinion gear housing ⁇ DP 'of the first subshaft 50 and the differential gear unit 210' is used as the input rotation part 51 of the first subshaft 50, and is coupled with the gear 44B having a constant gear ratio.
  • the differential A-axis DA ' is used as the shift control rotation part 52 of the first sub-shaft 50 while receiving a control function from the first control means F1.
  • Another control function is transmitted from the second control means (F2) is used as the output rotation portion 53 of the first sub-shaft 50 is coupled to the gear 44E having a constant gear ratio.
  • the drive input rotation part 41 of the main shaft 40 differential gear unit 210 may have different gears 44AK44B having a constant gear ratio with the input rotation part 51 of the first sub-shaft 50 differential gear unit 210 '.
  • the main shaft 40 differential is coupled by the
  • the shift control rotation part 42 of the gear unit 210 is coupled to the output rotation part 53 of the first sub-shaft 50 differential gear unit 210 ' by engagement of different gears 44DK44E having a constant gear ratio. have.
  • the rotation ratio of each component of the differential gear units 210 and 210 ' (the teeth "A-axis (DA.DA'), the differential B-axis (DB, DB ') and the pinion gear housing (DP, DP')] is determined.
  • the gear 44A built in the drive input rotation part 41 of the main shaft 40 is mounted.
  • the gear 44B arranged on the input rotation part 51 of the first subshaft 50 have a gear ratio of 1: 4 and the differential A axis DA of the main synchronous unit 210 of the main shaft 40.
  • the rotation ratio with respect to the pinion gear housing DP 'of the first sub-shaft 50 differential gear unit 210 ' is set to 4: 1, and is built up in the shift control rotation section 42 of the main shaft 40.
  • the gear 44E built in the gear 44D and the output rotation part 53 of the first sub-shaft 50 has a gear ratio of 1: 1 so that the pinion gear housing (DP) of the differential shaft unit 210 of the main shaft (40).
  • first auxiliary shaft (50) differential gear unit (210 ') was set to one: the rotation rate of the differential axis B (DB ') 1.
  • first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump and the like, and then the drive input rotation part of the main shaft (40).
  • the initial minimum input rotational speed of the variable power source (VP) transmitted from (41) from 700 RPM to 3,500 RPM as shown in the following ⁇ Table 5>
  • the amount of change in the rotation speed appearing in the output rotation part 43 of the main shaft 40 The result is a shift from the '0' RPM to the '3,500' RPM.
  • the transmission device outputs the input rotational speed by a combination of gears in which at least one of the components of the at least one differential gear unit 210K210 'is parallel to each other.
  • the speed range of rotation can be arbitrarily extended, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.
  • the fifth embodiment is also not limited to the above-described setting example. If the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously performed as long as it does not deviate.
  • the component 44D represents a theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation part 41.
  • the precondition for explaining the shifting process according to the sixth embodiment using the differential gear assembly 200 'of the present invention is the following correction paper (rule 91) After setting ⁇ Example 6>, the shift process of the output rotation speed was examined.
  • the minimum rotational speed of P1 is 700rpm
  • the gear rotation ratio of 44A: 44B is 1: 1
  • the gear rotation ratio of 44G: 4G ' is 1: 1
  • the gear rotation ratio of 44C ' : 44K ' is 1: 1
  • the gear rotation ratio of 44J: 44H is 1: 1
  • the gear rotation ratio of 4E: 44D is 1: 1.
  • the control value of F1 represents the value for the rotational speed of the first sub-axis differential gear and the pinion housing
  • the control rate of F2 represents the value for the rotational speed of the first sub-axis differential gear and the differential B-axis.
  • the differential A-axis DA of the differential gear unit 210 of the main shaft 40 has a drive input rotating part of the main shaft 40 through which the variable power source VP, in which the rotational speed of the rotational power source P is varied, is transmitted through the main shaft 40. It is used as (41) and is coupled to the gear (44A) having a constant gear ratio, the pinion gear housing (DP) is used as the shift control rotation part 42 of the main shaft (40), and has a constant gear ratio (44D)
  • the differential B-axis (DB) is used as the output rotation portion 43 of the main shaft (40).
  • differential A-axis (DA ' :) of the differential gear unit (210') of the first sub-shaft (50) is used as the input rotation part 51 of the first sub-shaft (50) and is coupled with the gear (44BK44G) having a constant gear ratio.
  • the differential B-axis DB ' is used as the shift control rotation part 52 of the first sub-shaft 50 and is coupled to the gear 44J having a constant gear ratio, and the pinion gear housing D
  • Correction Paper (Rule Article 91) P ' :) is used as the output rotation part 53 of the first sub-shaft 50 and has a constant gear ratio.
  • the differential A-axis DA 'of the second sub-axis 60 differential gear unit 2 ⁇ is coupled with the gear 44G ' having a constant gear ratio, and the pinion gear housing D has different gears (D).
  • 44C) is used as the shift control rotation part 62 of the second sub-shaft 60 while receiving the control function from the first control means F1 by the engagement of the 44 ' ), and the differential B-axis D is the second It receives another control function from the control means F2 and is used as the output rotation part 63 of the second sub-shaft 60 and is coupled with the gear 44H having a constant gear ratio.
  • the drive input rotational portion 41 of the main shaft 40 differential gear unit 210 may have different gears 44AK44B having a constant gear ratio from the input rotational portion 51 of the first minor shaft 50 differential gear unit 210 '; ), And the shift control rotation part 42 of the main shaft 40 differential gear unit 210 is connected to the output rotation part 53 of the first sub shaft 50 differential gear unit 210 ' :.
  • the gears are engaged by the engagement of different gears (44EX4 D) with a constant gear ratio.
  • the input rotational portion 51 of the differential gear unit 210 'of the first subshaft 50 has a different gear 44GK44 having a constant gear ratio with the input rotational portion 61 of the differential gear unit 2 ⁇ of the second subshaft 60.
  • the shift control rotation part 52 of the first sub-shaft 50 differential gear unit 210 ' is coupled by a coupling of G ' :), and the output of the second sub-shaft 60 differential gear unit (2 ⁇ ;) It is coupled by the engagement of the rotating part 53 and the different gears 44JX44H having a constant gear ratio.
  • the gear 44G 'built on the input rotation part 61 of the gear 44BK44G and the second subshaft 60 both have the gear ratio of 1: 1: 1 and the primary synchronous unit 210 of the main shaft 40 Differential A-axis (DA) and first sub-axis (50) differential gear unit 210 '(and type 2, a minor axis 60, the differential all the rotation rate of the differential ⁇ axes (DA') of the gear unit (21 ( ⁇ ) 1 differential A axis DA) of the "1: 1 set, and the
  • the gear 44D built into the speed control rotation part 42 of the main shaft 40 and the gear 44E built into the output rotation part 53 of the first subshaft 50 set the gear ratio to 1: 1.
  • the gear 44J built on the shift control rotation part 52 of the first subshaft 50 and the gear 44H built on the output rotation part 63 of the second subshaft 60 have a gear ratio of 1: 1. Set to.
  • first control means (F1) and the second control means (F2) are operated by the clutch disk plate, the drum-type clutch, the hydraulic internal gear pump and the like, and then the drive input rotating part ( 41), the initial minimum input rotation speed of the variable power source (VP) transmitted to the variable from 700 RPM to 3,500 RPM, as shown in Table 6, the main shaft (40)
  • the component 44D represents a theoretical value of the rotational ratio of the gear 44D to the drive input rotational unit (4DDML rotational speed), and the control rate of the first control means F1 is the second sub-axis 210. Is the control rate with respect to the theoretical value rotation ratio of the gear 44C ' with respect to the rotation speed of the input rotation part 61 of'; ' , and the control rate of the 2nd control means F2 is the input rotation of the 1st subshaft 210 ' ; The control ratio with respect to the theoretical value rotation ratio of the gear 44J with respect to the rotation speed of the whole 51 is shown.
  • At least three or more differential gear units 210, 210 ′ , 210 ′ are paralleled by the engagement of respective gears such that the respective axes are parallel to each other.
  • Combination can extend the speed range of output rotation to input speed arbitrarily, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made. Paper (rule 91) will be.
  • the sixth embodiment is also not limited to the above-described setting example, and when the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the gear ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously performed as long as it does not deviate from the idea.
  • FIG. 3A shows a planetary gear unit in which the gear combiner (A) of the present invention is used as the main shaft 70
  • 110 is a coupling stage diagram showing a coupling relationship according to the seventh embodiment of the composite gear coupling body 300 in which any one differential gear unit 210 ' used as the first auxiliary shaft 80 is coupled.
  • 3B is a cross-sectional view showing a coupling relationship according to the eighth embodiment of the composite gear assembly 300 of the present invention
  • FIG. 3C shows a first differential gear unit 210 and a first differential gear unit 210 used as the main shaft 70.
  • FIG 3 is a cross-sectional view showing a coupling relationship according to the ninth embodiment of the composite gear assembly 300 in which any one planetary gear unit 110 ′ used as the minor axis 80 is coupled.
  • Coupling cross section showing a coupling relationship according to the tenth embodiment of the coupling body 300 A.
  • the gear rotation ratio of 74B is 5: 1
  • the gear rotation ratio of 74E: 74D is 1: 1
  • the gear rotation ratio of 74C: 74K is 1: 1.
  • the control rate of F1 represents a numerical value for the rotational speed of the first sub-axis pinion gear and the housing
  • the control rate of F2 represents a numerical value for the first sub-axis difference synchronizing gear and the differential B-axis rotational speed.
  • the sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70.
  • the planetary gear carrier (C) is combined with the gear 74D having the constant gear ratio while being used as the shift control rotation part 72 of the main shaft 70.
  • the ring gear R is used as the output rotation portion 73 of the main shaft 70.
  • the differential A-axis DA ′ of the differential gear unit 210 'of the first sub-axis 80 is used as the input dropping portion 81 of the first sub-axis 80 and is coupled with a gear 74B having a constant gear ratio.
  • the pinion gear housing D is used as the shift control rotary part 82 of the first sub-shaft 80 while receiving a control function from the first control means F1 by engagement of different gears 74CK74K having a constant gear ratio.
  • the differential B-axis DB 'receives another control function from the second control means F2 and is used as the output rotation part 83 of the first sub-shaft 80 and has a constant gear ratio 74E.
  • the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 7 AX74B having a constant gear ratio from the input rotation part 81 of the differential gear unit 210 'of the first sub-axis 80.
  • the rotation ratio of each component of the main shaft 70 planetary gear unit 110 is set to 5: 1: 1 and the first sub-shaft (80)
  • the gear 74B built in the input rotation part 81 of the main shaft (81) has a gear ratio of 1: 5, and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the differential gear unit 210 of the first sub-axis 80.
  • the rotation rate of the "a differential shaft (DA's)" of 5:
  • correction Paper (Rule Article 91) It is set to 1, and the gear 74E built in the speed control rotation part 72 of the main shaft 70 and the gear 74E built in the output rotation part 83 of the first subshaft 80 have a gear ratio of 1.
  • the rotation ratio of the planetary gear carrier C of the main shaft 70 planetary gear unit 110 and the differential B-axis (DB ' :) of the first sub-axis 80 and the differential gear unit 210 ' is 1 :. Set to 1.
  • first control means (F1) and the second control means (F2) are operated by the clutch, the disk tube and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70).
  • the initial minimum input rotational speed of the variable power source (VP) transmitted from (71) from 700RPM to 3,500RPM as shown in Table 7 below
  • the amount of change of rotational speed appearing in the output rotation part 73 of the main shaft 70 The result is a shift from the '0' RPM to the '700' RPM.
  • the transmission device is a component of any one planetary gear unit 110 used as the main shaft 70, and any one used as the first auxiliary shaft 80 Parallel combinations of gears that allow each component of the differential gear unit (210 ':) to be parallel to each other to make it possible to arbitrarily expand the transmission range of the output speed to the input speed as well
  • the engine brake is operated through two control means (stop mode) to ensure safety during operation.
  • the seventh embodiment is also not limited to the above-described setting example, and if the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear.
  • Component 74D in Table 7 shows the theoretical value of the rotation ratio of the planetary gear unit 110 with respect to the input rotation part 71.
  • the gear rotation ratio of the 74B is 10: 1
  • the gear rotation ratio of the 74E: 74D is 1: 1.
  • the control rate of F1 represents the number of revolutions of the first sub-differential gear and the differential A-axis
  • the control rate of F2 represents the number of revolutions of the first sub-differential gear and the differential B-axis.
  • correction Paper (Rule Article 91) Indicates.
  • the sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70.
  • the planetary gear carrier (C) is combined with the gear 74D having the constant gear ratio while being used as the shift control rotation part 72 of the main shaft 70.
  • the ring gear R is used as the output rotation portion 73 of the main shaft 70.
  • the pinion gear housing (DF :) of the first sub-axis (80) of the differential gear unit (210 ' ) is used as the input rotating portion (81) of the first sub-axis (80) and is coupled with a gear (74B) having a constant gear ratio.
  • the differential A-axis DA ' is used as the shift control rotation part 82 of the first sub-axis 80 while receiving the control function from the first control means F1, and the differential B-axis DB ' is the second control. It receives another control function from the means F2 and is used as the output rotation part 83 of the first sub-shaft 80 and is coupled with a gear 74E having a constant gear ratio.
  • the drive input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 74AX74B having a constant gear ratio from the input rotation part 81 of the differential gear unit 210 ': of the first sub-axis 80. ), And the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 has a constant gear ratio with the output rotation part 83 of the differential gear unit 210 ′ of the first sub-shaft 80.
  • the rotation ratio of each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] is set to 5: 1: 1 and the first sub-shaft (80)
  • X 2 Differential A-axis (DA ' ) + Differential B-axis (DB' :)]
  • the gear 74A and the first gear 74 which are built up in the drive input rotation part 71 of the main shaft 70.
  • the gear 74B built in the input rotation part 81 of the subordinate shaft 80 has a gear ratio of 1:10 so that the sun gear S of the planetary gear unit 110 of the main shaft 70 and the first subordinate shaft 80 are differential.
  • the rotation ratio of the gear unit 210 ': to the pinion gear housing (DF) is set to 10: 1, and the gear 74D and the first gear set in the shift control rotation part 72 of the main shaft 70 are rotated.
  • the gear 74E has a gear ratio of 1: 1, and the differential B-axis of the planetary gear carrier C of the main shaft 70 and the planetary gear unit 100 and the differential gear unit 210 'of the first sub-axis 80.
  • the rotation ratio for (DB ' ) was set to 1: 1.
  • first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70).
  • the initial minimum input rotational speed of the variable power source (VP) transmitted from (71) from 700RPM to 3,500RPM, as shown in ⁇ Table 8> the change amount of rotational speed appearing in the output rotation part 73 of the main shaft 70 as shown in Table 8 below. The result is a shift from the '0' RPM to the '700' RPM.
  • the transmission device is a component of any one planetary gear unit 110 used as the main shaft 70, and any one used as the first auxiliary shaft 80
  • Parallel combinations of gears which allow the components of the differential gear unit 210 'to be parallel to each other, make it possible to arbitrarily expand the shift range of the output rotational speed to the input rotational speed, as well as to request sudden braking.
  • the engine brake is activated through two control means (stop mode) to ensure safety during operation.
  • the eighth embodiment is not limited to the above-described setting example, but if the structure of the coupling type, the shift control ratio of each shifting means, and the gear ratio are arbitrarily changed, the shift ratio corresponding to the corresponding coupling condition will appear. Of course, it can be variously performed as long as it does not deviate from the idea. ⁇ Table 8>
  • the component 74D represents a theoretical value of the rotation ratio of the planetary gear unit 110 to the input rotation unit 71.
  • the control rate of F1 represents the number of revolutions of the first sub-axis differential gear and the differential A-axis
  • the control rate of F2 represents the number of revolutions of the first sub-axis differential gear and the differential B-axis.
  • the sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70.
  • the planetary gear carrier (C) is combined with the gear 74D having the constant gear ratio while being used as the shift control rotation part 72 of the main shaft 70.
  • the ring gear R is used as the output rotation portion 73 of the main shaft 70.
  • the pinion gear housing DP 'of the first subshaft 80 differential gear unit 210 ' is used as the input rotation part 81 of the first subshaft 80 and is coupled with a gear 74B having a constant gear ratio. And the differential A-axis DA ' receives the control function from the first control means F1.
  • the differential B-axis (DB ':) receives another control function from the second control means (F2) output shaft of the first sub-shaft (80) It is used as (83) and is coupled with a gear (74E) with a constant gear ratio.
  • the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 74AK74B having a constant gear ratio with the input rotation part 81 of the differential gear unit 210 'of the first sub-axis 80.
  • the shift control rotation part 72 of the main shaft 70 planetary gear unit 110 has a constant gear ratio with the output rotation part 83 of the differential gear unit 210 ': of the first sub-shaft 80.
  • the gears are coupled by the engagement of the different gears (74DX74E).
  • the rotation ratio of each component of the main shaft 70 planetary gear unit 110 is set to 5: 1: 1 and the first sub-shaft (80)
  • X 2 differential A-axis (DA ' ) + differential B-axis (DB ' ;)], and the gear 74A and the first sub-shaft built into the drive input rotation part 71 of the main shaft 70.
  • the gear 74B built in the input rotation part 81 of the 80 has a gear ratio of 1: 2.5 and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the differential gear of the first subshaft 80.
  • the rotation ratio of the pinion gear housing DF of the unit 210 ' is set to 2.5: 1, and the gear 74D and the first subshaft 80, which are built up in the shift control rotation part 72 of the main shaft 70, are rotated.
  • the planetary gear unit 100 includes: a gear (74E) has a gear ratio 1
  • first control means (F1) and the second control means (F2) to operate by receiving the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump and the like, and then the first control means (F1)
  • the initial minimum input rotational speed of the variable equal power source (VP) transmitted to the drive input rotation part 71 of the main shaft 70 with a specific rotational speed of 75% at the initial control rate was changed from 700RPM to 3,500RPM.
  • Table 9 the variation in the number of revolutions appearing in the output rotation part 73 of the main shaft 70 is shifted from '0' RPM to '1,680' RPM.
  • the transmission in accordance with the ninth embodiment of the present invention is any one differential used as each of the components of one planetary gear unit 110 used as the main shaft 70 and the first sub-axis (80)
  • Parallel combinations of gears that allow each component of the gear unit 2 T to be parallel to each other can be arbitrarily extended to shift the output rotational speed to the input rotational speed.
  • the engine brake is activated through the control means (stop mode) to ensure safety during operation.
  • the ninth embodiment is also not limited to the above-described setting example, and when the structure of the coupling type, the shift control ratio of each shifting means, and each gear ratio are arbitrarily changed, the shift ratio corresponding to the corresponding coupling condition will appear. Of course, it can be variously performed as long as it does not deviate from the idea.
  • the component 74D represents the theoretical value of the rotation ratio of the gear 74D to the rotational speed of the drive input rotation part 71 of the main shaft 110, and the first control means F1
  • the control rate shows the control rate with respect to the theoretical value rotation ratio of the differential A-axis with respect to the rotation speed of the input rotation part 81 of the 1st sub-axis 210 '.
  • the minimum rotational speed of P1 is 700rpn
  • the rotational ratio (S: C: R) of the planetary gear unit is 4: 1: 1
  • the gear rotation ratio of 74B shall be 1: 1
  • the gear rotation ratio of 74D: 74E shall be 2: 1.
  • the gear rotation ratio of 74C: 74K is 1: 1.
  • the control ratio of F1 represents the numerical value for the rotational speed of the first minor shaft planetary gear and the carrier gear
  • the control ratio of F2 represents the numerical value of the rotational speed of the first minor shaft planetary gear and the ring gear.
  • the differential A-axis DA of the differential gear unit 210 of the main shaft 70 has a drive input rotating part of the main shaft 70 through which the variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70.
  • the differential B-axis (DB) is used as the output rotation portion 73 of the main shaft (70).
  • the sun gear S ′ of the first subshaft 80 and the planetary gear unit 110 ′ is used as the input arm portion 81 of the first subshaft 80 and is coupled with a gear 74B having a constant gear ratio.
  • the gearbox carrier () is used as the shift control rotary part 82 of the first sub-shaft 80 while receiving a control function from the first control means pi by the engagement of different gears 74CK74K having a constant gear ratio.
  • the driving input rotation part 71 of the differential gear unit 210 of the main shaft 70 has different gears 74AX74B having a constant gear ratio with the input rotation part 81 of the planetary gear unit 110 ′ of the first sub-axis 80.
  • the shift control rotation part 72 of the gear unit 210 is engaged by engaging the output rotation part 83 of the planetary gear unit 110 ′ of the first subshaft 80 with different gears 74DK74E having a constant gear ratio. It is.
  • the gear 74B built in the planetary gear unit 110 'input rotation part 81 of the differential gear unit 210 has a gear ratio of 1: 1 and the differential A-axis DA and the first sub-axis of the differential gear unit 210 of the main shaft 70.
  • the gear 74E built in the portion 83 has a gear ratio of 1: 2 and the pinion gear housing DP of the differential gear unit 210 of the main shaft 70 and the planetary gear unit 110 'of the first subshaft 80.
  • the rotation ratio with respect to the ring gear R 'of;) was set to 2: 1.
  • first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, and the like.
  • the transmission device is a component of any one differential gear unit 210 used as the main shaft 70, any one used as the first sub-axis (80)
  • Parallel combinations of gears that make the components of the planetary gear unit 110 ' make parallel to each other are able to arbitrarily expand the speed range of the output rotational speed to the input rotational speed, as well as demanding braking.
  • the engine brake is activated through the main control means (stop mode) to ensure stability during operation.
  • the tenth embodiment is also not limited to the above configuration example, the structure of the combined form. If the control ratio of each control means, each gear ratio is arbitrarily changed, the speed ratio corresponding to the corresponding combination conditions will appear, so that various modifications can be made within the scope without departing from the technical spirit of the present invention.
  • the minimum rotational speed of P1 is 700rpm
  • the rotational ratio (S: C: R) of the planetary gear unit is 3: 1: 1
  • the gear rotation ratio of 74B is 2: 1
  • the gear rotation ratio of 74E: 74D is 1: 1
  • the gear rotation ratio of 74C: 74K is 1: 1.
  • the control ratio of F1 represents a numerical value based on the first minor shaft planetary gear and the sun gear rotational speed
  • the control ratio of F2 represents a numerical value for the first minor shaft planetary gear and the ring gear rotational speed.
  • the differential A-axis (M) of the differential gear unit (210) of the main shaft (70) has a drive input rotating part of the main shaft (70) through which a variable power source (VP) whose rotational speed of the rotating power source (P) is varied is transmitted through the main shaft (70). It is used as a 71 and is coupled with a gear 74A having a constant gear ratio, and the pinion gear housing DP is used as a shift control rotation part 72 of the main shaft 70 and has a constant gear ratio 74D.
  • the differential B-axis (DB) is used as the output rotation portion 73 of the main shaft (70).
  • a first minor axis 80, the planetary gear unit (110; group control with a constant gear ratio as used to ") the planetary gear carrier () has a first minor axis 80, the planetary gear unit (110 of" input rotation part 81 of) ( 74B), the sun gear (S ' :) is coupled to the gear (74C) having a constant gear ratio and the transmission control rotary part of the first sub-axis (80) while receiving a control function from the first control means (F1) Ring gear (R ' ) is coupled to the gear (74E) having a constant gear ratio and receives the control function from the second control means (F2) (82), the output rotation part 83 of the first sub-shaft (80) Is used.
  • the drive input rotation part 71 of the differential gear unit 210 of the main shaft 70 may have different gears 7 AX74B having a constant gear ratio with the input rotation part 81 of the planetary gear unit 110 ′ of the first sub-axis 80. ) Is coupled to each other, and the shift control rotation part 72 of the main gear 70 differential gear unit 210 is constant with the output rotation part 83 of the planetary gear unit 110 'of the first sub-shaft 80.
  • the gears are coupled by the engagement of different gears 74E and 74D with gear ratios.
  • the gear 74B built in the drive input rotation part 81 of the main shaft 70 has a gear ratio of 1: 2 and is equal to the differential A axis DA of the differential gear unit 210 of the main shaft 70.
  • first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70).
  • the initial minimum input rotation speed of the variable power source (VP) transmitted from (71) from 700 RPM to 3,500 RPM the change amount of rotation speed displayed on the output rotation part 73 of the main shaft 70 as shown in Table 11 below. The result is a shift from the '0' RPM to the '3,500' RPM.
  • the transmission device is a component of any one differential gear unit 210 used as the main shaft 70, any one used as the first sub-axis (80)
  • Parallel combinations of gears that make the components of the planetary gear unit 110 'make parallel to each other are able to arbitrarily extend the shift range of the output electromagnetism with respect to the input rotational speed, as well as when braking is required.
  • the engine brake is activated through two control means (stop mode) to ensure safety during operation.
  • the eleventh embodiment is also not limited to the above configuration example, the structure of the coupling form ,
  • the component 74D represents a theoretical value of the rotation ratio of the differential gear unit 210 with respect to the input rotation unit 71.
  • the minimum rotational speed of P1 is 700rpm
  • the ratio of the gears of the planetary gear units (S: C: R) is 5: 1: 1
  • 74A The gear rotation ratio of 74B is 5: 1
  • the gear rotation ratio of 74G: 7G ' is 1: 1.
  • the gear rotation ratio of 74C ': 74K' is 1: 1
  • the gear rotation ratio of 7 J: 74H is 1: 1
  • the gear rotation ratio of 74E: 74D is 1: 1.
  • the control rate of F1 represents the number of revolutions of the first sub-axis differential gear and the pinion housing
  • the control rate of F2 represents the number of revolutions of the first sub-axis differential gear and the differential B-axis.
  • the sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70.
  • the planetary gear carrier (C) is combined with the gear (74D) having a constant gear ratio while being used as the shift control rotary part (72) of the main shaft (70).
  • the ring gear R is used as the output rotation portion 73 of the main shaft 70.
  • the differential A-axis DA ′ of the differential gear unit 210 ′ of the first sub-axis 80 is used as the input rotation part 81 of the first sub-axis 80 and is coupled with a gear 74BX74G having a constant gear ratio.
  • the pinion gear housing DF is used as the shift control rotation part 82 of the first subshaft 80 and is coupled with the gear 74J having a constant gear ratio
  • the differential B axis DB ′ is the first subshaft 80. It is used as the output rotation part 83 of the) and is coupled with the gear 74E having a constant gear ratio.
  • the differential A-axis DA 'of the second sub-axis 90 and the differential gear unit 210- is used as the input rotation part 91 of the second sub-axis 90 and is coupled with the gear 74G ' having a constant gear ratio.
  • the pinion gear housing (DP-) is driven by the engagement of the different gears (74C ' ) (74 ⁇ ' ).
  • Correction Paper (Rule Article 91) It is used as the shift control rotation part 92 of the second sub-shaft 90 while receiving the control function from the female 1 control means F1, and the differential B-axis D: is made from the second control means F2. Received the fish function is used as the output rotation part 93 of the second sub-shaft 90 is coupled to the gear (74H) having a constant gear ratio.
  • the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 7 AK74B having a constant gear ratio with the input rotation part 81 of the differential gear unit 210 ′ of the first sub-axis 80.
  • the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 has a constant gear ratio with the output rotation part 83 of the differential gear unit 210 ′ of the first sub-shaft 80.
  • the gears are coupled by the engagement of the different gears (74EX74D).
  • the input rotational portion 81 of the differential gear unit 210 'of the first sub-axis 80 has a different gear 74G having a constant gear ratio with the input rotational portion 91 of the differential gear unit 210' of the second sub-axis 90.
  • (7 G ' ) is coupled by the coupling
  • the shift control rotary portion 82 of the first sub-axis (80) differential gear unit (21 0 ' ) is the output of the second sub-axis (90) differential gear unit 210 ' It is coupled by the engagement of the rotary part 93 and the different gears 74JK74H having a constant gear ratio.
  • the rotation ratio of each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] is set to 5: 1: ⁇ and the first sub-shaft ( 80)
  • the gear 74E built in the shift control rotation part 72 of the main shaft 70 and the gear 74E built in the output rotation part 83 of the first subshaft 80 have a gear ratio of 1: 1.
  • the gear 74H set in the gear 74J and the output circuit 93 of the second subshaft 90 and the gear 74J arranged in the shift control rotation part 82 of the first subshaft 80 set the gear ratio. 2: 1 was set.
  • first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70).
  • the initial minimum input rotational speed of the variable power source (VP) transmitted to (71) from 700 RPM to 3,500 RPM, as shown in Table 12 the rotation speed of the rotational speed appearing in the output rotation portion 73 of the main shaft (70) The amount of change was shifted from '0' RPM to '700' RPM.
  • the component 74D represents a theoretical value of the rotation ratio of the gear 74D to the rotation speed of the drive input rotation part 71 of the main shaft 110, and the first control means F1
  • the control rate is the control rate with respect to the theoretical value rotation ratio of the gear 74C with respect to the rotation speed of the input rotation part 91 of the 2nd sub-axis 210 ':
  • the control rate of the 2nd control means F2 is 1st.
  • the transmission device is a component of any one planetary gear unit 110 used as the main shaft 70, and any one used as the first sub-axis (80) Input rotational speed in parallel combination by meshing each gear such that the components of the second differential gear unit 2 ⁇ used as the first differential gear unit 210 'and the second secondary shaft 90 are parallel to each other.
  • the speed range of output rotation can be arbitrarily expanded, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.
  • the twelfth embodiment is also not limited to the above-described setting examples, and when the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition is shown. Of course, it can be variously carried out within the scope not departing.
  • the minimum rotational speed of P1 is 700rpm
  • the rotational ratio (S: C: R) of each planetary gear unit is 4: 1: 1
  • 74A The gear rotation ratio of 74B is 4: 1
  • the gear rotation ratio of 74G: 74G ' is 2: 1
  • the gear rotation ratio of 74J: 74H is 1.
  • the gear rotation ratio of 74E and 74D is 1: 1.
  • control rate of F1 represents the number of revolutions of the first sub-axis differential gear and the differential A-axis
  • control rate of F2 represents the number of revolutions of the first sub-axis differential gear and the differential B-axis.
  • the sun gear S of the main shaft 70 of the planetary gear unit 110 includes a drive input arm portion of the main shaft 70 through which the variable power source VP whose rotational speed of the rotation power source P is varied is transmitted through the main shaft 70 ( 71), combined with a gear (74A) with a constant gear ratio,
  • the gear gear carrier C is used as the shift control rotation part 72 of the main shaft 70 and is coupled with the gear 74D having a constant gear ratio, and the ring gear R is the output rotation part 73 of the main shaft 70. Used as
  • the differential A-axis DA 'of the first sub-axis 80 and the differential gear unit 210' is used as an input rotation part 81 of the first sub-axis 80 and is coupled with a gear 74BK74G having a constant gear ratio.
  • the pinion gear housing DF is used as the shift control rotation part 82 of the system 1 sub-axis 80 and is coupled with the gear 74J having a constant gear ratio, and the differential B-axis DB 'is connected to the first sub-axis ( It is used as an output rotation part 83 of 80 and is coupled with a gear 74E having a constant gear ratio.
  • the pinion gear housing (D :) of the second sub-axis (90) differential gear unit 21 ( ⁇ :) is used as the input rotation part 91 of the second sub-shaft 90 and has a gear 74G 'having a constant gear ratio.
  • the differential A-axis DA * is coupled to the shift control of the second sub-axis 90 while receiving a control function from the first control means F1 by the engagement of the different gears 74C ' and 74 ⁇ ' .
  • the differential ⁇ -axis (DB-) is received as another control function from the second control means (F2) and used as the output rotating part 93 of the second sub-shaft (90) while maintaining a constant gear ratio Coupled with an excitation gear (74 ⁇ ).
  • the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 74 ⁇ 74 ⁇ having a constant gear ratio with the input rotation part 81 of the differential gear unit 210 'of the first sub-axis 80. Coupled to each other, and the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 outputs the differential gear unit 210 'of the first sub shaft 80.
  • the input rotation part 81 of the first sub-shaft 80 differential gear unit 210 ' is different from the input rotation part 91 of the second sub-axis 90 differential gear unit 210 ⁇ with a different gear 74G. (74G ';) coupled to each other, the shift control rotation portion 82 of the first sub-axis (80) differential gear unit (21 0 ' i) is the output rotation of the second sub-axis (90) differential gear unit (2 ⁇ ) And 93 are engaged by engagement of different gears 74J and 74H with a constant gear ratio.
  • the rotation ratio of each component of the main shaft 70 planetary gear unit 110 is set to 4: 1: 1: 1 and the first sub-shaft ( 80) Rotation ratio and second sub-axis 90 of each component [: lower A axis DA ', differential B axis DB', pinion gear housing DP ') of the differential synchronous unit 210'.
  • the gear 74B built in the input rotation part 81 of the shaft 80 has a gear ratio of 1: 4, and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the differential gear of the first sub-shaft 80.
  • the speed control rotation part of the main shaft 70 by setting the rotation ratio with respect to DP ';
  • the gear 74D built in the 72 and the gear 74D built in the output rotation part 83 of the first subshaft 80 set the gear ratio to 1: 1, and the speed change of the first subshaft 80.
  • the gear 74H built in 82 and the gear 74H built in the output rotation part 93 of the 2nd sub-shaft 90 set the gear ratio to 1: 1.
  • the first control means (F1) and the second control means (F2) are operated by the clutch, the disk plate and drum-type clutch, the hydraulic internal gear pump, etc., and then the drive input rotation part of the main shaft (70).
  • VP variable power source
  • the component 74D represents a theoretical value of the rotation ratio of the gear 74D to the rotational speed of the drive input dielectric unit 71 of the main shaft 110, and the first control step F1.
  • the control rate of the 2nd control means F2 is a control rate of the 1st subshaft ( The control ratio with respect to the theoretical value rotation ratio of the gear 74J with respect to the rotation speed of the input rotation part 81 of 210 'is shown.
  • the transmission device is a component of any one planetary gear unit 110 used as the main shaft 70, and any one used as the first auxiliary shaft 80 Compound parallelism by the engagement of the gears in which the components of the second differential gear unit 21 ( ⁇ ) used as the first differential gear unit 210 'and the second sub-axis 90 are parallel to each other.
  • the speed range of the output rotation to the input rotation can be arbitrarily expanded by the combination, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety can be achieved during operation.
  • the thirteenth embodiment of the present invention is also not limited to the above-described setting example, and when the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the gear ratio corresponding to the corresponding combination condition is shown. Of course, it can be variously performed as long as it does not deviate from the technical spirit of the.
  • the gear rotation ratio of 74B is 1: 1
  • the gear rotation ratio of 74G: 74G ' is 5: 1
  • the gear rotation ratio of 74J: 74H is 1.
  • the gear rotation ratio of 74E: 74D is 1: 1.
  • control rate of F1 represents the number of revolutions of the second sub-axis differential gear and the pinion housing
  • control * of F2 represents the number of revolutions of the first sub-axis differential gear and the differential B-axis.
  • the sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70.
  • the planetary gear carrier (C) is combined with the gear (74D) having a constant gear ratio while being used as the shift control rotary part (72) of the main shaft (70).
  • the ring gear R is used as the output rotation portion 73 of the main shaft 70.
  • the sun gear S 'of the first subshaft 80 and the planetary gear unit 110' is used as an input rotation part 81 of the first subshaft 80 and is coupled with a gear 74BK74G having a constant gear ratio.
  • the gear carrier () is used as the shift control portion 82 of the first sub-axis (80).
  • correction Paper (Rule Article 91)
  • the outer circumferential surface thereof is coupled to the gear 7 j having a constant gear ratio, and the ring gear R 'is used as the output rotation part 83 of the first sub-shaft 80 and has a constant gear ratio 74E. Combined with.
  • the differential A-axis DA- of the differential gear unit 21 ( ⁇ ) of the second sub-axis 90 is used as the input rotation part 91 of the second sub-axis 90 and has a gear 74G 'having a constant gear ratio.
  • the pinion gear housing DP- is shifted on the second axle 90 while receiving a control function from the first control means F1 by engagement of different gears 74C ' (74 ⁇ ' :).
  • the differential ⁇ -axis (DB-) is received as another control function from the second control means (F2) used as the output rotation portion 93 of the second sub-axis 90, the constant gear ratio Is combined with a gear (74 ⁇ ).
  • the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 74 ⁇ 74 ⁇ having a constant gear ratio with the input rotation part 81 of the first sub-axis 80 planetary gear unit 110 '.
  • the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 has a constant gear ratio with the output rotation part 83 of the planetary gear unit 110 'of the first sub-shaft 80.
  • the different gears (74EK74D) with the teeth are engaged by the teeth.
  • the input rotation part 81 of the first sub-axis 80 planetary gear unit 110 ' is different from the input rotation part 91 of the second sub-axis 90 differential gear unit 210': different gears having a constant gear ratio 74GK74G. Coupled to each other, and the shift control rotation part 82 of the first sub-axis 80 and the planetary gear unit 11 0 ′ is the output of the second sub-axis 90 and the differential gear unit 210 ⁇ .
  • each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear 00, planetary gear carrier (C)] and each of the first sub-axis 80, planetary gear unit (110 ' )
  • the ratio of the element [sun gear (S '), ring gear (R'), planetary gear carrier (:)] is set to 5: 1: 1, and each component of the second sub-axis 90 differential gear unit 21CT is constructed.
  • gear (74G ') has a gear ratio of 1: 5 to Sun gear S of the planetary gear unit 110 and the sun gear S of the planetary gear unit 110 'of the first sub-axis 80 and the second sub-axis 90 of the planetary gear unit 110 and the differential shaft unit 210-;
  • gear 74D and the first subshaft 80 which are set in the shift control rotation section 72 of the main shaft 70, with a rotation ratio of the differential A-axis (DA * ;) set to 5: 5: 1.
  • 74E built on the output rotating unit 83 sets the gear ratio to 1: 1, and the gear 74J and the second subshaft 90 built on the shift control rotating unit 82 of the first sub-axis 80.
  • the gear ratio 74H built in the output rotation part 93 of the wheel) is set at a gear ratio of 1: 1.
  • first control means (F1) and the second control means (F2) are operated by receiving a sense.
  • the component 74D represents a theoretical value of the rotation ratio of the gear 74D to the rotation speed of the drive input rotation part 71 of the main shaft 110, and the first control step F1.
  • the control rate of is the control rate with respect to the theoretical value rotation ratio of the gear 74C ' with respect to the rotation speed of the input rotation part 91 of the 2nd subshaft 21 ( ⁇ ;), and the control rate of the 2nd control means F2 is the 1st subshaft
  • the control ratio with respect to the theoretical value elimination ratio of the gear 74J with respect to the rotation speed of the input rotation part 81 of (210 ' :) is shown.
  • the transmission device is a fixed paper used as the main shaft 70 (rule 91)
  • the engine brake is operated through the two control means (stop mode) to ensure safety during operation.
  • the fourteenth embodiment is also not limited to the above-described setting examples. If the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously carried out within the scope not departing.
  • the minimum rotational speed of P1 is 700rpm
  • the rotational ratio (S: C: R) of each planetary gear unit is 5: 1: 1
  • 74A The gear rotation ratio of 74B is 1: 1
  • the gear rotation ratio of 74G: 74G ' is 2: 1
  • the gear reduction ratio of 74C': 74K ' is 1: 1: 1: 1: 1: 1
  • correction Paper (Rule Article 91) 74E The gear ratio of the 74D is 1: 1.
  • the control rate of F1 represents a value for the rotational speed of the first sub-axis difference synchronizing gear and the pinion housing
  • the control rate of F2 represents the rotational speed value for the first sub-axis differential gear and the differential B axis.
  • the sun gear S of the planetary gear unit 110 of the main shaft 70 has a drive input rotating part 71 of the main shaft 70 to which a variable power source VP whose rotational speed of the rotational power source P is varied is transmitted through the main shaft 70.
  • the planetary gear carrier (C) is combined with the gear (74D) having a constant gear ratio while being used as the shift control rotary part (72) of the main shaft (70).
  • the ring gear R is used as the output rotation portion 73 of the main shaft 70.
  • the sun gear (S ' ) of the first sub-axis (80) planetary gear unit (110') is coupled to the gear (74BK74G) having a constant gear ratio when used as the input rotation portion 81 of the first sub-axis (80),
  • the planetary gear carrier () is used as the shift control rotation part 82 of the first sub-shaft 80 and the outer circumferential surface thereof is coupled to the gear 74J having a constant gear ratio, and the ring gear R ' is the first sub-shaft. It is used as the output rotation portion 83 of the 80 and is engaged with the gear 74E having a constant gear ratio.
  • the differential A-axis DA- of the second sub-axis 90 and the differential gear unit 2 ⁇ is used as the input rotation part 91 of the second sub-axis 90, and is coupled with a gear 74G ' having a constant gear ratio.
  • the pinion gear housing (DP * ) is driven by the engagement of different gears (74C ' ) (74 ⁇ ' )
  • the driving input rotation part 71 of the planetary gear unit 110 of the main shaft 70 may have different gears 7 AK74B having a constant gear ratio from the input rotation part 81 of the first sub-axis 80 planetary gear unit 110 ′ .
  • the shift control rotation part 72 of the planetary gear unit 110 of the main shaft 70 is fixed to the output rotation part 83 of the planetary gear unit 110 ': of the first sub-axis 80.
  • the gears are coupled by the engagement of the different gears (7 EK74D).
  • the input rotation part 81 of the first sub-axis 80 planetary gear unit 110 ' is different from the input rotation part 91 of the second sub-gear 90 90 differential gear unit 210.
  • (74G ') is coupled by a coupling, and the shift control rotary part 82 of the first sub-axis 80 planetary gear unit (110' :) output of the second sub-axis (90) differential gear unit (2 ⁇ ) It is coupled by the engagement of the rotary part 93 and the different gears 7 JK74H with a constant gear ratio.
  • each component of the main shaft 70 planetary gear unit 110 [sun gear (S), ring gear (R), planetary gear carrier (C)] and the first sub-axis 80 of the planetary gear unit (110 ')
  • the rotation ratio of each of the components [sun gear (S ' ), ring gear (R'), planetary gear carrier (;) is set to 5: 1: 1 and the second sub-axis 90 differential gear unit (210 * :)
  • Correction Paper [Pinion Gear Housing] can be used to set the rotation ratio for the differential B-axis (Dr) and pinion gear housings (Dr :)].
  • the gear 74B built in the input rotation part 81 of the 80 sets the gear ratio to 1: 1, and the gear 74B built in the input rotation part 81 of the 1st subshaft 80 and the 2nd
  • the gear 74G ′ installed in the input rotation part 91 of the subordinate shaft 90 has a gear ratio of 1: 2, and the sun gear S of the planetary gear unit 110 of the main shaft 70 and the planetary body of the first subordinate shaft 80 are formed.
  • the first control answer F1 and the second control means F2 which are operated under the sense, are constituted by a clutch, a disk plate and a drum type clutch, a hydraulic internal gear pump, and the like.
  • the initial minimum input rotational speed of the variable power source (VP) transmitted to the drive input rotation part 71 of the main shaft 70 from 700RPM to 3,500RPM with a specific rotational speed with an initial control rate of 75%.
  • the amount of change in the electrolyzed water appearing in the output rotation part 73 of the main shaft 70 is changed from '0' RPM to '1,300' RPM.
  • the component 74D represents a theoretical value of the rotation ratio of the gear 74D to the rotation speed of the drive input rotation part 71 of the main shaft 110, and the first control step F1.
  • the control rate of is the control rate with respect to the theoretical value rotation ratio of the gear 7 C ': with respect to the rotation speed of the input rotation part 91 of the 2nd sub-axis (2 ⁇ :), and the control rate of the 2nd control means F2 is 1st
  • the control ratio with respect to the theoretical value rotation ratio of the gear 74J with respect to the rotation speed of the input rotation part 81 of the sub-axis 210 ': is shown.
  • the transmission device is any one used as each of the components of the first planetary gear unit 110 and the first sub-shaft 80 used as the main shaft (70).
  • Compound parallel combination by engaging each gear such that the components of any one differential gear unit 210 ⁇ used as the second planetary gear unit 110 ′ and the second sub-axis 90 are parallel to each other.
  • Paper of output rotational speed with respect to input rotational speed (Rule Article 91)
  • the speed range can be arbitrarily extended, and the engine brake is operated through two control means (stop mode) when a sudden braking request is made, so that safety during operation can be achieved.
  • the fifteenth embodiment is also not limited to the above-described setting example, and when the structure of the coupling type, the control ratio of each control means, and the gear ratio are arbitrarily changed, the transmission ratio corresponding to the corresponding combination condition will appear. Of course, it can be variously carried out within the scope not departing.
  • the present invention as described above is not limited to the reduction ratio of any one unit of the gear combination, there is an advantage that can implement a wide variety of speed range ranging from the low speed range and high speed range, various embodiments of the gear assembly Therefore, it is possible to easily realize a large reduction ratio with a simple structure, so that the field of application has a great effect that can be applied to various types of transmission including a gear reducer and also for automobile and industrial use.
  • the engine power is transmitted to the gear assembly, thereby maximizing the engine efficiency in the power transmission process, thereby reducing the fuel cost, and achieving a very large reduction ratio with a simple structure and making the volume of the gear assembly compact. Since it can be manufactured, it is possible to reduce the manufacturing cost significantly, such as to have a very economical effect.

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

Abstract

La présente invention porte sur un dispositif de transmission comprenant au moins un moyen de commande et un ensemble engrenage qui sont accouplés l'un à l'autre. La présente invention porte plus particulièrement sur un dispositif de transmission utilisant deux moyens de commande et un ensemble engrenage dans lequel une transmission est configurée de telle sorte que la fréquence de rotation de la source d'énergie principale, transmise en provenance d'un arbre d'entrée d'entraînement, est commutée dans le rapport d'engrenage d'unités de trains épicycloïdaux ou d'unités d'engrenages différentiels et transmise au moyen d'entraînement, et l'ensemble engrenage est formé par la combinaison d'une ou plusieurs unités de trains épicycloïdaux et d'au moins une unité d'engrenage différentiel en une structure double ou triple par une combinaison axiale parallèle, et un rapport de transmission pour la fréquence de rotation d'une source d'énergie rotative est commandé par les deux moyens de commande en accord avec les rapports d'engrenages multiples de l'ensemble engrenage. Ainsi, dans un mode de fonctionnement, la source d'énergie rotative peut élargir la gamme de commutation pour la fréquence de rotation d'un arbre de sortie d'entraînement, à partir de la fréquence de rotation qui est déterminée en tant que niveau d'entrée minimum.
PCT/KR2010/006758 2009-11-26 2010-10-04 Dispositif de transmission utilisant deux moyens de commande et un ensemble engrenage Ceased WO2011065659A2 (fr)

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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
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