CN204572953U - Share the two intermediate-shaft speed changing box of non-equidistant of input shaft gear - Google Patents
Share the two intermediate-shaft speed changing box of non-equidistant of input shaft gear Download PDFInfo
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- CN204572953U CN204572953U CN201520128607.8U CN201520128607U CN204572953U CN 204572953 U CN204572953 U CN 204572953U CN 201520128607 U CN201520128607 U CN 201520128607U CN 204572953 U CN204572953 U CN 204572953U
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- gear
- shaft
- change gear
- input shaft
- jack
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Abstract
Share the two intermediate-shaft speed changing box of non-equidistant of input shaft gear, it is characterized in that: input shaft (1) is connected by bearing (2) with output shaft (3), input shaft (1) is equipped with change gear (4) and change gear (5), jack shaft (6) is equipped with change gear (7) and change gear (8), jack shaft (9) is equipped with change gear (10) and change gear (11), output shaft (3) is connected with jack shaft (9) with jack shaft (6) with constant mesh gear (13) respectively by constant mesh gear (12), the centre distance of jack shaft (6) and jack shaft (9) and input shaft (1) is unequal, change gear (4), change gear (5), change gear (7), change gear (8), change gear (10), diameter and the number of teeth of change gear (11) are all unequal, by control synchro (14) and synchronizer (15), change gear (4) and change gear (7) can be made respectively, change gear (5) and change gear (8), change gear (4) and change gear (10), change gear (5) and change gear (11) engage separately, the 4 kind rotating speeds different from input shaft (1) are obtained at output shaft (3).
Description
Technical field
The utility model relates to a kind of two intermediate-shaft speed changing box of non-equidistant of shared input shaft gear, is specially adapted to rear-engined hybrid vehicle or pure electric bus automobile.
Background technique
The gear of automobile gearbox is more, and speed-change process is more steady, and the working efficiency of motor is also higher.
Current mixed power or pure electric bus automobile are all engine at extreme rears, and due to rear overhang limited length, in fixing axial space, gearbox axial length dimension is restricted, and can not use many grades of casees, are all generally adopt second gear gearbox.
Current second gear gearbox be all adopt single jack shaft or wait distance of shaft centers discharge two intermediate shaft structures, this structure, when not increasing gearbox axial length dimension, can only realize the speed change of two gears usually.
Adopt second gear gearbox Problems existing to be: the speed change between two gears is differential excessive, there is the problem that gear shift lock in time is long or shifting shock is large, easily cause the stall of gear shifting motor, shorten the working life of gear shifting motor.Meanwhile, because shift time is long, the power performance of vehicle and gear shift pause and transition in rhythm or melody sense can affect the travelling comfort of vehicle ride.In addition, in current city, electrically-charging equipment is not complete, automobile is when electricity is not enough, the second gear case of mixed power can not the torque characteristics of covering engine, and vehicle can not travel by Direct driver as normal orthodox car, and need first generate electricity, be stored into storage battery, to power to motor to drive automobile by storage battery again, cause automobile fuel ecomomy and engine operating efficiency to reduce, do not reach the requirement of energy-saving and emission-reduction.
Model utility content
In order to overcome current rear-engined mixed power or pure electric bus automobile due to rear overhang limited length, the problem that multi-speed gear box brings can not be used, the utility model provides a kind of two intermediate-shaft speed changing box of non-equidistant discharge of shared input shaft gear, be characterized in, when not changing second gear gear-box axle to dimensions length, adopt 2 jack shafts, and the centre distance of 2 jack shafts and input shaft is unequal, input shaft and 2 jack shafts are equipped with 2 change gears respectively, when the diameter of 6 change gears and the number of teeth all unequal time, by controlling 2 synchronizers, the 4 kind rotating speeds different from input shaft can be obtained at output shaft, achieve four-speed gear shift function, the speed change reduced between two gears is differential, improve the working efficiency of automobile fuel ecomomy and motor, so be specially adapted to rear-engined hybrid vehicle or pure electric bus automobile.
The technological scheme that the utility model adopts is: the two intermediate-shaft speed changing box of non-equidistant sharing input shaft gear, primarily of input shaft, the jack shaft of non-equidistant discharge, bearing, output shaft, change gear, constant mesh gear, synchronizer forms, it is characterized in that: input shaft (1) is connected by bearing (2) with output shaft (3), input shaft (1) is equipped with change gear (4) and change gear (5), jack shaft (6) is equipped with change gear (7) and change gear (8), jack shaft (9) is equipped with change gear (10) and change gear (11), output shaft (3) is connected with jack shaft (9) with jack shaft (6) with constant mesh gear (13) respectively by constant mesh gear (12), the centre distance of jack shaft (6) and jack shaft (9) and input shaft (1) is unequal, change gear (4), change gear (5), change gear (7), change gear (8), change gear (10), diameter and the number of teeth of change gear (11) are all unequal, by control synchro (14) and synchronizer (15), the 4 kind rotating speeds different from input shaft (1) can be obtained at output shaft (3), when not changing second gear gear-box axle to dimensions length, achieve fourth gear box function.
Transmission principle of the present utility model is as follows: in FIG, if the diameter of change gear (4), change gear (5), change gear (7), change gear (8), change gear (10), change gear (11) and the number of teeth is unequal mutually and the number of teeth is respectively z4, z5, z7, z8, z10, z11.When synchronizer (14) upward sliding makes the gear of jack shaft (6) (7) engage with the gear (4) of input shaft (1), the transmission speed ratio of jack shaft (6) is z4/z7; When synchronizer (14) slide downward makes the gear of jack shaft (6) (8) engage with the gear (5) of input shaft (1), the transmission speed ratio of jack shaft (6) is z5/z8; When synchronizer (15) upward sliding makes the gear of jack shaft (9) (10) engage with the gear (4) of input shaft (1), the transmission speed ratio of jack shaft (9) is z4/z10; When synchronizer (15) slide downward makes the gear of jack shaft (9) (11) engage with the gear (5) of input shaft (1), the transmission speed ratio of jack shaft (9) is z5/z11.
Because output shaft (3) is connected with jack shaft (9) with jack shaft (6) respectively with constant mesh gear (13) by constant mesh gear (12), so 4 kinds of speed that jack shaft (6) and jack shaft (9) transmit are delivered to output shaft by constant mesh gear (12) and constant mesh gear (13).Due to jack shaft (6) and jack shaft (9) unequal to the centre distance of input shaft (1), and output shaft and input shaft are on same axis, so z4/z7, z5/z8z4/z10 and z5/z11 are unequal mutually, the 4 kind rotating speeds different from input shaft (1) just can be obtained at output shaft (3).
The beneficial effects of the utility model are: the two intermediate-shaft speed changing box of non-equidistant sharing input shaft gear, because the change gear of 2 jack shafts shares the change gear of input shaft, so after the change gear diameter of input shaft and the number of teeth are determined, the change of speed depends primarily on the centre distance of 2 jack shafts and input shaft.By the centre distance of non-isometric change 2 jack shafts and input shaft, the most reasonable optimized speed change just can be obtained differential.
Adopt center of asymmetry to arrange apart from two intermediate shaft structure, the length only having 2 pairs of gear shift gears meshing lays out 4 different speed ratios.Have the mechanical property more more superior than single intermediate shaft structure, corresponding gear, main shaft structure, quality can more lightweights; Assembly length of installation is short, quality is light, more can meet the requirement generally adopting rearmounted mixed power or pure electric bus automotive transmission installing space and gear at present, make motor, motor always works in more efficient operation interval, reach the requirement of energy-saving and emission-reduction.
Whole transmission system of the present utility model also has following characteristics:
1, the axial length not changing second gear case realizes fourth gear box function, meets new-energy automobile requirements of installation space;
2, take the two intermediate shaft structure of the non-equidistant of shared input shaft gear, according to speed ratio characteristic Selection Center distance, housing structure and assembly weight can be optimized to the full extent, be more conducive to energy-conservation, reduction of discharging;
3, each gear synchronizer is assemblied on jack shaft, and have the rotary inertia overcome needed for gear shift little, gear shift is lighter, and the sync response time is faster, and the synchronizer under equal conditions has longer working life.
4, two intermediate shaft structure, make the mechanical property of main shaft (input shaft, output shaft) more superior, safety coefficient is higher.
5, decrease the gear selecting process of many grades of casees, direct gear shift, make gearshift control more fast simple and convenient.
Accompanying drawing explanation
Below in conjunction with drawings and Examples, the utility model is further illustrated.
Fig. 1 is structure principle chart of the present utility model
Fig. 2 is one grade of gear transmission route schematic diagram of the present utility model
Fig. 3 is intermediate gear drive path schematic diagram of the present utility model
Fig. 4 is three-range transmission drive path schematic diagram of the present utility model
Fig. 5 is fourth gear drive path schematic diagram of the present utility model
Fig. 6 is assembly structure figure of the present utility model
Embodiment
Embodiment is described with reference to accompanying drawing.
In the embodiment in figure 1, input shaft (1) is connected by bearing (2) with output shaft (3), change gear (4) and change gear (5) input shaft (1) be equipped with, change gear (7) and change gear (8) jack shaft (6) be equipped with, jack shaft (9) has change gear (10) and change gear (11), output shaft (3) is connected with jack shaft (9) with jack shaft (6) with constant mesh gear (13) respectively by constant mesh gear (12).The centre distance of jack shaft (6) and jack shaft (9) and input shaft (1) is unequal, change gear (4), change gear (5), change gear (7), change gear (8), change gear (10), diameter and the number of teeth of change gear (11) are all unequal, by control synchro (14) and synchronizer (15), change gear (4) and change gear (7) can be made respectively, change gear (5) and change gear (8), change gear (4) and change gear (10), change gear (5) and change gear (11) engage separately, the 4 kind rotating speeds different from input shaft (1) are obtained at output shaft (3).
In the embodiment in figure 1, by increasing jack shaft and the number of synchronizer and the logarithm of constant mesh gear, more kinds of rotating speed different from input shaft can also be obtained at output shaft.
Specific embodiments is as follows: jack shaft and synchronizer are increased to 3 by 2, constant mesh gear is right to being increased to 3 by 2, 3 jack shafts are all installed 2 change gears and share 2 change gears of input shaft, the centre distance of 3 jack shafts and input shaft is all unequal, the diameter of all change gears and the number of teeth are all unequal, according to the transmission principle of the two jack shaft of the non-equidistant of aforementioned shared input shaft gear, by controlling 3 synchronizers, 8 change gears of input shaft and 3 jack shafts can be made respectively to be combined into 6 kinds of independent engagements, the 6 kind rotating speeds different from input shaft are obtained at output shaft.
By that analogy, according to above-mentioned principle, often increase by 1 and the non-equidistant jack shaft of 2 change gears, 1 pair of constant mesh gear and 1 synchronizer are housed, just can increase by 2 kinds of rotating speeds different from input shaft at output shaft.
In the embodiment in figure 1, by increasing the number of change gear number on input shaft and 2 jack shafts and synchronizer simultaneously, more kinds of rotating speed different from input shaft can also be obtained at output shaft.
Specific embodiments is as follows: the change gear number on input shaft and 2 jack shafts is all increased to 4 by 2, synchronizer is increased to 4 by 2, the change gear diameter increased and the diameter of the number of teeth and other change gear and the number of teeth unequal all mutually, according to the transmission principle of the two jack shaft of the non-equidistant of aforementioned shared input shaft gear, by controlling 4 synchronizers, 12 change gears of input shaft and 2 jack shafts can be made respectively to be combined into 8 kinds of independent engagements, to obtain 8 kinds of rotating speeds different from input shaft at output shaft.
By that analogy, according to above-mentioned principle, the change gear on input shaft and 2 jack shafts all increases by 2 simultaneously, and synchronizer also increases by 2, just can increase by 4 kinds of rotating speeds different from input shaft at output shaft.
If the change gear of input shaft and 2 jack shafts all increases by 1 simultaneously, also need increase by 2 synchronizers, but 2 kinds of different speed ratios can only be increased, so increase change gear is more reasonable in pairs in implementation process at output shaft.
In the embodiment in figure 1, can also by increasing the number of change gear number on input shaft and wantonly 1 jack shaft and synchronizer simultaneously, at the more kinds of rotating speed different from input shaft of output shaft acquisition.
Specific embodiments is as follows: input shaft is all increased to 4 by 2 with the change gear number on wantonly 1 jack shaft, synchronizer is increased to 3 by 2, the change gear diameter increased and the diameter of the number of teeth and other change gear and the number of teeth unequal all mutually, according to the transmission principle of the two jack shaft of the non-equidistant of aforementioned shared input shaft gear, by controlling 3 synchronizers, 10 change gears of input shaft and 2 jack shafts can be made respectively to be combined into 6 kinds of independent engagements, to obtain 6 kinds of rotating speeds different from input shaft at output shaft.
By that analogy, according to above-mentioned principle, all increase by 2 the while of change gear on input shaft and wantonly 1 jack shaft, synchronizer increases by 1, just can increase by 2 kinds of rotating speeds different from input shaft at output shaft.
If the change gear of input shaft and wantonly 1 jack shaft all increases by 1 simultaneously, also need increase by 1 synchronizer, but a kind of different speed ratio can only be increased, so paired increase change gear is more reasonable in implementation process at output shaft.
Fig. 2 is one grade of gear transmission route schematic diagram of the present utility model, see the thick line with arrow in Fig. 2, power is transferred to the gear (10) jack shaft (9) from the gear (4) of input shaft (1), engaged with jack shaft (9) from synchronizer (15) toward gear (10), power is delivered to the constant mesh gear (13) on output shaft (3) again by jack shaft (9), exported outward by output shaft (3).
Fig. 3 is intermediate gear drive path schematic diagram of the present utility model, see the thick line with arrow in Fig. 3, power is transferred to the gear (7) jack shaft (6) from the gear (4) of input shaft (1), engaged with jack shaft (6) from synchronizer (14) toward gear (7), power is delivered to the constant mesh gear (12) on output shaft (3) again by jack shaft (6), exported outward by output shaft (3).
Fig. 4 is three-range transmission drive path schematic diagram of the present utility model, see the thick line with arrow in Fig. 4, power is transferred to the gear (11) jack shaft (9) from the gear (5) of input shaft (1), engaged with jack shaft (9) from synchronizer (15) toward gear (11), power is delivered to the constant mesh gear (13) on output shaft (3) again by jack shaft (9), exported outward by output shaft (3).
Fig. 5 is fourth gear drive path schematic diagram of the present utility model, see the thick line with arrow in Fig. 5, power is transferred to the gear (8) jack shaft (6) from the gear (5) of input shaft (1), engaged with jack shaft (6) from synchronizer (14) toward gear (8), power is delivered to the gear (12) on output shaft (3) again by jack shaft (6), exported outward by output shaft (3).
Fig. 6 is assembly structure figure of the present utility model, assembly layout is left and right jack shaft, tub box construction illustrated, casing is mainly divided into main casing (17) and protecgulum (18) two parts, motor mounting interface when adjunction electric machine support (16) uses as mixed power on main casing; Protecgulum (16) is designed with the tapped hole connected with clutch housing, carries out the connection of motor/motor.
Claims (4)
1. share the two intermediate-shaft speed changing box of non-equidistant of input shaft gear, primarily of input shaft, the jack shaft of non-equidistant discharge, bearing, output shaft, change gear, constant mesh gear, synchronizer forms, it is characterized in that: input shaft (1) is connected by bearing (2) with output shaft (3), input shaft (1) is equipped with change gear (4) and change gear (5), jack shaft (6) is equipped with change gear (7) and change gear (8), jack shaft (9) is equipped with change gear (10) and change gear (11), output shaft (3) is connected with jack shaft (9) with jack shaft (6) with constant mesh gear (13) respectively by constant mesh gear (12), the centre distance of jack shaft (6) and jack shaft (9) and input shaft (1) is unequal, change gear (4), change gear (5), change gear (7), change gear (8), change gear (10), diameter and the number of teeth of change gear (11) are all unequal, synchronizer (14) upward sliding makes the gear of jack shaft (6) (7) engage with the gear (4) of input shaft (1), synchronizer (14) slide downward makes the gear of jack shaft (6) (8) engage with the gear (5) of input shaft (1), synchronizer (15) upward sliding makes the gear of jack shaft (9) (10) engage with the gear (4) of input shaft (1), synchronizer (15) slide downward makes the gear of jack shaft (9) (11) engage with the gear (5) of input shaft (1).
2. the two intermediate-shaft speed changing box of the non-equidistant of shared input shaft gear according to claim 1, it is characterized in that: the number of jack shaft can be greater than 2, the jack shaft increased also is equipped with 2 change gears, the jack shaft increased to the centre distance of input shaft and existing jack shaft unequal mutually to the centre distance of input shaft, change gear diameter on the jack shaft increased and the change gear diameter on the number of teeth and existing jack shaft and the number of teeth unequal mutually, often increase by 1 jack shaft with regard to corresponding increase by 1 pair of constant mesh gear and 1 synchronizer.
3. the two intermediate-shaft speed changing box of the non-equidistant of shared input shaft gear according to claim 1, it is characterized in that: the change gear number of input shaft and 2 jack shafts can be greater than 2 simultaneously, the change gear number that each axle increases simultaneously is equal, the change gear diameter increased and the number of teeth and existing change gear diameter and the number of teeth unequal mutually, the change gear number that each axle increases simultaneously can be odd number, also can be even number, but each axle increase by 1 gear simultaneously or increase by 2 gears all need increase by 2 synchronizers.
4. the two intermediate-shaft speed changing box of the non-equidistant of shared input shaft gear according to claim 1, it is characterized in that: the change gear number of input shaft and wantonly 1 jack shaft can be greater than 2 simultaneously, the change gear number that diaxon increases simultaneously is equal, the change gear diameter increased and the number of teeth and existing change gear diameter and the number of teeth unequal mutually, the change gear number that diaxon increases simultaneously can be odd number, also can be even number, but diaxon increase by 1 gear simultaneously or increase by 2 gears all need increase by 1 synchronizer.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520128607.8U CN204572953U (en) | 2015-03-02 | 2015-03-02 | Share the two intermediate-shaft speed changing box of non-equidistant of input shaft gear |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520128607.8U CN204572953U (en) | 2015-03-02 | 2015-03-02 | Share the two intermediate-shaft speed changing box of non-equidistant of input shaft gear |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN204572953U true CN204572953U (en) | 2015-08-19 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201520128607.8U Expired - Fee Related CN204572953U (en) | 2015-03-02 | 2015-03-02 | Share the two intermediate-shaft speed changing box of non-equidistant of input shaft gear |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN204572953U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105987134A (en) * | 2015-03-02 | 2016-10-05 | 韶关飞翔自动变速箱有限公司 | Gearbox adopting double intermediate shafts capable of sharing gear of input shaft and arranged in non-equidistant manner |
| CN106917848A (en) * | 2017-04-18 | 2017-07-04 | 立马车业集团有限公司 | The many gear actuating units of motor |
-
2015
- 2015-03-02 CN CN201520128607.8U patent/CN204572953U/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105987134A (en) * | 2015-03-02 | 2016-10-05 | 韶关飞翔自动变速箱有限公司 | Gearbox adopting double intermediate shafts capable of sharing gear of input shaft and arranged in non-equidistant manner |
| CN106917848A (en) * | 2017-04-18 | 2017-07-04 | 立马车业集团有限公司 | The many gear actuating units of motor |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20150819 Termination date: 20200302 |
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| CF01 | Termination of patent right due to non-payment of annual fee |