CN102562967B - Triaxial planet row type six-gear manual transmission - Google Patents
Triaxial planet row type six-gear manual transmission Download PDFInfo
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- CN102562967B CN102562967B CN201110453370.7A CN201110453370A CN102562967B CN 102562967 B CN102562967 B CN 102562967B CN 201110453370 A CN201110453370 A CN 201110453370A CN 102562967 B CN102562967 B CN 102562967B
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Abstract
The invention provides a triaxial planet row type six-gear manual transmission which comprises an input shaft (1), a middle shaft (2) and a third shaft (3), wherein the input shaft (1), the middle shaft (2) and the third shaft (3) are mounted in a shell (7); the input shaft (1) and the third shaft (3) are both parallel to the middle shaft (2); the input shaft (1) is used for receiving a power input from an engine; on the basis of a common triaxial transmission, a set of planet row with a Ravigneaux structure is additionally arranged, so that the six gears can be realized by using least parts; the quantity of normally engaged gears is reduced, so that the transmission efficiency is greatly increased; and a reverse gear is directly outputted by the planet row and a reverse gear synchronizer and a reverse gear idle pulley are cancelled, so that gear-shifting elements are reduced, the loss is reduced and the fuel oil consumption is reduced. The planet row is of an inner engaging mechanism which has the advantage of shortened central distance as compared with external engaging, so that the central distance of the whole transmission is reduced, the space size of the transmission is greatly reduced and the manufacturing cost is reduced by 10%-15%.
Description
Technical field
The invention belongs to automotive transmission structure field, especially relate to a kind of six grades of manual transmissions.
Background technique
In Vehicle Driving Cycle, motor is the link of manufacturing power, and clutch is the hinge of transferring power, and speed changer is the link that realizes the distributed power of vehicle under different running condition.Speed changer is divided into manual transmission and automatic transmission, although that manual transmission operates is cumbersome, can more directly show driver's wish.
Manual transmission is to be made up of the gear train of different tooth ratios, and its basic functional principle is by switching different gear trains, realizes the conversion of tooth ratio.Gear train is made up of the different gear of diameter, and the power transmission effect that different gear ratio reaches is diverse, alleged namely change gear ratio of gearshift in usually driving.
At present, at the passenger car of China market, manual vehicle mostly adopts 5 grades of manual transmissions, and 5 grades of directions of advance add 1 reverse gear shift.And in the passenger car of European market, six grades of manual transmission uses are very general, there are a lot of design examples for such speed changer.Major part is on the basis of original 5 grades of manual transmissions, to increase synchronizer or adopt double output shaft to realize, belong to ordinary transmission, complex structure, use part comparison is many, and transmission efficiency is low, and reverse gear adopts idle pulley to change transmission direction, and use synchronizer, synchronizer uses too much, causes frictional loss higher, and energy consumption is larger.
Summary of the invention
The problem to be solved in the present invention is to provide a kind of shifting element, the six grades of manual transmissions that simple in structure, transmission efficiency is high of reducing.
For solving the problems of the technologies described above, claimant is studying on the basis of AT for many years, textural association in conjunction with three axle manual transmissions forms, that is: on the basis of common 3 shaft transmissions, increase a set of draw dimension micro-nano structure planet row, make it realize 6 gears with minimum part, structure is driven for indulging postpone.Reverse gear is directly exported by planet row simultaneously, has reduced shifting element, has reduced loss, has reduced fuel consume.
Advantage and good effect that the present invention has are:
1,6 grades of employings of tradition, 7 cover constant mesh gears, this programme number of spare parts is few, adopts 4 cover constant mesh gears, and number of spare parts significantly reduces.
2, because the quantity of constant mesh gear reduces, thereby increased substantially transmission efficiency.
3, common manual speed changer adopts reversing-gear synchronizer and reverse idler gear, and this programme, because planet row can directly be exported reverse gear, has been cancelled synchronizer and reverse idler gear, has reduced cost, has improved transmission efficiency.
4, this scheme is owing to having adopted La Weinashi planet row, and compact structure, compares the space of greatly having shortened speed changer with conventional manual speed changer.
5, because planet row is interior engaging mechanism, compares and shortened centre distance with outer gearing, thereby shortened the centre distance of whole speed changer, reduced the volume and weight of speed changer.
6, owing to having reduced the quantity of part, so manufacture cost has approximately reduced 10%-15%.
Brief description of the drawings
Fig. 1 is structure principle chart of the present invention
Fig. 2 is that rotating speed is analyzed schematic diagram
Fig. 3 is gearshift logical comparison table
In figure:
The 1st, input shaft; 2, jack shaft; 3, the 3rd axle; 31, rear sun gear; 4, front sun gear; 5, planet carrier; 6, output gear; 7, case of transmission; 17, long planet wheel; 18, short planet wheel I, the first countershaft-gear; II, input gear; III, three shaftgears; IV, two axle continuously-meshing gears; V, the second countershaft-gear; VI, three axle continuously-meshing gears; VII, three axle the second continuously-meshing gears; VIII, the 3rd countershaft-gear;
C1, the first synchronizer (replacement clutch); C2, the second synchronizer (replacement clutch); C3, the 3rd synchronizer (replacement clutch);
B1, the first brake synchronous device (replacement break); B2, the second brake synchronous device (replacement break);
101, the first synchronizer sliding sleeve; 102, the first synchromesh gear hub;
201, the second synchronizer sliding sleeve; 202, the second synchromesh gear hub;
301, the 3rd synchronizer sliding sleeve; 302, the 3rd synchromesh gear hub;
Embodiment
As shown in Figure 1, the present invention includes the input shaft 1, jack shaft 2 and the 3rd axle 3 that are arranged in housing 7, input shaft 1 is all parallel with jack shaft 2 with the 3rd axle 3; Input shaft 1 is accepted the power input from motor;
On input shaft (1), be fixed with input gear (II); The first intermediate gear (I), the 3rd synchronizer (C3), the second countershaft-gear (V), the 3rd countershaft-gear (VIII) are installed on jack shaft (2) successively; Three shaftgears (III), three axle continuously-meshing gears (VI), the first synchronizer (C1), two brake synchronous devices (B1, B2), the second synchronizer (C2) and planet row are installed on the 3rd axle;
Input gear II on input shaft 1 often engages with the first intermediate gear I being fixedly mounted with on jack shaft; Second, third countershaft-gear (V, VIII) being fixedly mounted with on the two axle continuously-meshing gear IV that are set with on jack shaft, jack shaft, often engages with the three axle continuously-meshing gear VI that are set with on the three shaftgear III that are fixedly mounted with on the 3rd axle, the 3rd axle, three axle the second continuously-meshing gear VII respectively;
The combination gear of two axle continuously-meshing gear IV and the 3rd clutch synchronizer C3 is coupled as one, and the 3rd synchromesh gear hub 302 is bound up on jack shaft 2, and the 3rd synchronizer sliding sleeve 301 can connect the combination gear of the 3rd synchromesh gear hub 302 and the 3rd clutch synchronizer C3;
The combination gear of three axle continuously-meshing gear VI and the first synchronizer C1 is coupled as one, and two brake synchronous devices (B1, B2) are all coupled as one with housing 7, and the combination gear of three axle the second continuously-meshing gear VII and the second synchronizer C2 is coupled as one;
Described planet row comprises planet carrier 5, organize long and short planet wheel (17,18), forward and backward sun gear (4,31) and output gear 6 more, long planet wheel 17 and short planet wheel 18 are rotatably mounted on planet carrier 5, the short planet wheel of every group and long planet wheel be corresponding engagement mutually, long planet wheel 17 also engages with front sun gear 4 and output gear 6 respectively, and short planet wheel 18 also engages with rear sun gear 31; The power after conversion is exported to the vertical postpone driving car load of transmission shaft by output gear 6;
The tooth hub 202 of planet carrier 5 and the second synchronizer C2 is coupled as one, and the tooth hub 102 of front sun gear 4 and the first synchronizer C1 is coupled as one, and rear sun gear 31 and the 3rd axle 3 are coupled as one;
The first synchronizer sliding sleeve 101 can make the tooth hub 102 of the first synchronizer C1 connect with the combination gear of the first synchronizer C1 or with the first brake synchronous device B1 respectively; The second synchronizer sliding sleeve 201 can make the tooth hub 202 of the second synchronizer C2 connect with combination gear or the second brake synchronous device B2 of the second synchronizer C2 respectively.
The working principle of this example and working procedure:
The sliding sleeve of each synchronizer is by selector fork control, the part that it is horizontally slipped.
The effect of the 3rd synchronizer sliding sleeve 301: the 3rd synchromesh gear hub 302 and jack shaft 2 are connected into one, the combination gear of the 3rd synchronizer C3 and two axle continuously-meshing gear IV are connected into one, in the time that the 3rd synchronizer sliding sleeve 301 moves right, the combination gear of the 3rd synchromesh gear hub 302 and the 3rd synchronizer C3 is linked together, and power passes to two axle continuously-meshing gear IV from input shaft 1 through input gear II, the first countershaft-gear I, jack shaft 2.
The effect of the first synchronizer sliding sleeve 101: the first synchromesh gear hub 102 is coupled as one with front sun gear 4, and coordinate with the first synchronizer sliding sleeve 101, the combination gear of the first synchronizer C1 and three axle continuously-meshing gear VI are connected into one, and the first brake synchronous device B1 and case of transmission 7 are linked together.When the first synchronizer sliding sleeve 101 is moved to the left, three axle continuously-meshing gear VI are linked together by combination gear and the front sun gear 4 of the first synchronizer C1.When the first synchronizer sliding sleeve 101 moves right, front sun gear 4 is linked together by the first brake synchronous device B1 and housing, by front sun gear 4 stop.
The effect of the second synchronizer sliding sleeve 201: the second brake synchronous device B2 and case of transmission 7 are connected into one, the combination gear of the second synchronizer C2 and three axle the second continuously-meshing gear VII are connected into one, the combination gear of the second synchronizer C2 and planet carrier 5 are coupled as one, and and the second synchronizer sliding sleeve 201 cooperation connections.In the time that the second synchronizer sliding sleeve 201 is moved to the left, planet carrier 5 is linked together by the second brake synchronous device B2 and housing, make planet carrier 5 stop.In the time that the second synchronizer sliding sleeve 201 moves right, planet carrier 5 is linked together to interlock by combination gear and three axle the second continuously-meshing gear VII of the second synchronizer C2, transmit by the 3rd countershaft-gear VIII the power of coming thereby receive from jack shaft 2.
General function is described:
The function of speed changer be by the transmission of power of motor to car load, power is inputted by the input shaft 1 of speed changer, through the action of different synchronizer sliding sleeve, will after power-supply change-over, pass to output gear 6 axles outputs, thereby pass to car load.
Fig. 2 has provided concrete rotating speed combination contrast.Table 3 has provided the logical table of gearshift, is described as follows:
1, one grade: the 3rd synchronizer C3 (replacement clutch) work, the 3rd synchronizer sliding sleeve 301 moves right, the combination gear of the 3rd synchromesh gear hub 302 and the 3rd synchronizer C3 is linked together, power passes to jack shaft 2 by input shaft 1 by gear I, II, then passes to rear sun gear 31 by gear IV, III;
The second brake synchronous device B2 works simultaneously: the second synchronizer sliding sleeve 201 connects the second synchromesh gear hub 202 and the second synchronizer B2, and both connect respectively again planet carrier 5 and housing, and therefore planet carrier 5 is braked.
Working procedure: the 3rd synchronizer C3 and the second brake synchronous device B2 work (closure), power is inputted by rear sun gear 31, and planet carrier 5 is braked, thus output gear 6 output speeds.
2, second gear: the 3rd synchronizer C3 work: power passes to jack shaft 2 by input shaft 1 by gear I, II, is passing to rear sun gear 31 by gear III, IV;
The first brake synchronous device B1 work simultaneously: the first synchronizer sliding sleeve 101 is connected front sun gear 4 and housing, and front sun gear 4 is braked;
Working procedure: the 3rd synchronizer C3 and the first brake synchronous device B1 work (closure), power is inputted by rear sun gear 31, and front sun gear 4 is braked, thus output gear 6 output speeds.
3, third gear: the 3rd synchronizer C3 work: power passes to jack shaft 2 by input shaft 1 by gear I, II, is passing to rear sun gear 3 by gear III, IV;
The first synchronizer C1 work: power passes to part 2 by input shaft 1 by gear I, II, then passes to front sun gear 4 by gear V, VI;
Working procedure: C3 and C1 work (closure), power is inputted by rear sun gear 31 and front sun gear 4, thus output gear 6 output speeds.
4, fourth gear: the 3rd synchronizer C3 work: power passes to jack shaft 2 by input shaft 1 by gear I, II, is passing to rear sun gear 31 by gear III, IV;
C2 work: power passes to jack shaft 2 by input shaft 1 by gear I, II, then passes to planet carrier 5 by gear VIII, VII;
Working procedure: C3 and C2 work (closure), power is inputted by rear sun gear 31 and planet carrier 5, thus output gear 6 output speeds.
5, five grades: C1 work: power passes to jack shaft 2 by input shaft 1 by gear I, II, then passes to front sun gear 4 by gear V, VI;
C2 work: power passes to jack shaft 2 by input shaft 1 by gear I, II, then passes to planet carrier 5 by gear VIII, VII;
Working procedure: C1 and C2 work (closure), power is inputted by front sun gear 4 and planet carrier 5, thus output gear 6 output speeds.
6, six grades: C2 work: power passes to jack shaft 2 by input shaft 1 by gear I, II, then passes to planet carrier 5 by gear VIII, VII;
B1 work: the first synchronizer sliding sleeve 101 is connected front sun gear 4 and housing, and front sun gear 4 is braked;
Working procedure: power is inputted by planet carrier 5, front sun gear 4 is braked, output gear 6 output speeds.
7, reverse gear: C1 work: power passes to jack shaft 2 by input shaft 1 by gear I, II, then passes to front sun gear 4 by gear V, VI;
B2 work: planet carrier 5 is braked.
Working procedure: power is inputted by front sun gear 4, and planet carrier 5 is braked, output gear 6 output speeds.
Above one embodiment of the present of invention are had been described in detail, but described content is only preferred embodiment of the present invention, can not be considered to for limiting practical range of the present invention.All equalization variation and improvement etc. of doing according to the present patent application scope, within all should still belonging to patent covering scope of the present invention.
Claims (1)
1. six grades of manual transmissions of three axle planet row types, is characterized in that: comprise the input shaft (1), jack shaft (2) and the 3rd axle (3) that are arranged in housing (7), input shaft (1) is all parallel with jack shaft (2) with the 3rd axle (3); Input shaft (1) is accepted the power input from motor;
On input shaft (1), be fixed with input gear (II); The first intermediate gear (I), the 3rd synchronizer (C3), the second countershaft-gear (V), the 3rd countershaft-gear (VIII) are installed on jack shaft (2) successively; Three shaftgears (III), three axle continuously-meshing gears (VI), the first synchronizer (C1), two brake synchronous devices (B1, B2), the second synchronizer (C2) and planet row are installed on the 3rd axle;
Input gear (II) on input shaft (1) often engages with the first intermediate gear (I) being fixedly mounted with on jack shaft; Second, third countershaft-gear (V, VIII) being fixedly mounted with on the upper two axle continuously-meshing gears (IV) that are set with of jack shaft (2), jack shaft, often engages with the three axle continuously-meshing gears (VI), three axle the second continuously-meshing gears (VII) that are set with on three shaftgears (III) that are fixedly mounted with on the 3rd axle (3), the 3rd axle respectively;
The combination gear of the 3rd synchronizer (C3) and two axle continuously-meshing gears (IV) are coupled as one, the tooth hub (302) of the 3rd synchronizer is coupled as one with jack shaft (2), and the sliding sleeve (301) of the 3rd synchronizer can interconnect its tooth hub (302) and combination gear;
Three axle continuously-meshing gears (VI) are coupled as one with the combination gear of the first synchronizer (C1), two brake synchronous devices (B1, B2) are all coupled as one with housing (7), and three axle the second continuously-meshing gears (VII) are coupled as one with the combination gear of the second synchronizer (C2);
Described planet row comprises planet carrier (5), organize long and short planet wheel (17,18), forward and backward sun gear (4,31) and output gear (6) more, long planet wheel (17) and short planet wheel (18) are all rotatably mounted on planet carrier (5), the short planet wheel of every group and long planet wheel be corresponding engagement mutually, long planet wheel (17) also engages with front sun gear (4) and output gear (6) respectively, and short planet wheel (18) also engages with rear sun gear (31); The power after conversion is exported to the vertical postpone driving car load of transmission shaft by output gear (6);
Planet carrier (5) is coupled as one with the tooth hub (202) of the second synchronizer (C2), and front sun gear (4) is coupled as one with the tooth hub (102) of the first synchronizer (C1), and rear sun gear (31) is coupled as one with the 3rd axle (3);
The first synchronizer sliding sleeve (101) can make the tooth hub (102) of the first synchronizer (C1) connect with the combination gear of the first synchronizer (C1) or with the first brake synchronous device (B1) respectively; The second synchronizer sliding sleeve (201) can make the tooth hub (202) of the second synchronizer (C2) connect with combination gear or the second brake synchronous device (B2) of the second synchronizer (C2) respectively.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110453370.7A CN102562967B (en) | 2011-12-30 | 2011-12-30 | Triaxial planet row type six-gear manual transmission |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110453370.7A CN102562967B (en) | 2011-12-30 | 2011-12-30 | Triaxial planet row type six-gear manual transmission |
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| CN102562967A CN102562967A (en) | 2012-07-11 |
| CN102562967B true CN102562967B (en) | 2014-06-25 |
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| CN201110453370.7A Active CN102562967B (en) | 2011-12-30 | 2011-12-30 | Triaxial planet row type six-gear manual transmission |
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Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102913598B (en) * | 2012-10-30 | 2016-03-23 | 顺德职业技术学院 | Planetary gear type manual transmission |
| CN109505939B (en) * | 2018-12-28 | 2024-03-19 | 东风商用车有限公司 | Hybrid power gearbox |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101012868A (en) * | 2007-01-23 | 2007-08-08 | 陕西法士特齿轮有限责任公司 | Six-speed mechanical saloon car transmission |
| CN101956793A (en) * | 2009-07-20 | 2011-01-26 | 中国北方车辆研究所 | Six-drive and three-reverse planet speed changer |
| CN201891808U (en) * | 2010-11-30 | 2011-07-06 | 长城汽车股份有限公司 | Four-speed automatic transmission |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8113978B2 (en) * | 2007-07-31 | 2012-02-14 | GM Global Technology Operations LLC | Nine speed automatic transmission |
| JP2010216605A (en) * | 2009-03-18 | 2010-09-30 | Honda Motor Co Ltd | Transmission |
| US20100248884A1 (en) * | 2009-03-31 | 2010-09-30 | Richard Tremblay | Transmission for an Electrically Powered Vehicle |
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Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN101012868A (en) * | 2007-01-23 | 2007-08-08 | 陕西法士特齿轮有限责任公司 | Six-speed mechanical saloon car transmission |
| CN101956793A (en) * | 2009-07-20 | 2011-01-26 | 中国北方车辆研究所 | Six-drive and three-reverse planet speed changer |
| CN201891808U (en) * | 2010-11-30 | 2011-07-06 | 长城汽车股份有限公司 | Four-speed automatic transmission |
Non-Patent Citations (1)
| Title |
|---|
| JP特开2010-216605A 2010.09.30 |
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Address after: 301600 Jinhai Road, Jinghai Development Zone, Jinghai County, Tianjin 5 Patentee after: TIANJIN TANHAS TECHNOLOGY CO., LTD. Address before: 301600 Jinhai Road, Jinghai Development Zone, Jinghai County, Tianjin 5 Patentee before: Tianjin Tanhas Technology Co., Ltd. |
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