CN203477204U - Double-clutch gearbox - Google Patents
Double-clutch gearbox Download PDFInfo
- Publication number
- CN203477204U CN203477204U CN201320504095.1U CN201320504095U CN203477204U CN 203477204 U CN203477204 U CN 203477204U CN 201320504095 U CN201320504095 U CN 201320504095U CN 203477204 U CN203477204 U CN 203477204U
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- gear
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- driving
- gears
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/006—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion power being selectively transmitted by either one of the parallel flow paths
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Abstract
The utility model discloses a double-clutch gearbox. The double-clutch gearbox is provided with seven forward gears, a reverse gear, four synchronizers and a duplicate gear meshing structure. The double-clutch gearbox has the advantages that the design of a specific tooth-connection reverse gear structure is adopted, an idler shaft and an auxiliary gear in a traditional gearbox are omitted, the internal structure of the gearbox is simplified, the manufacturing cost is reduced, and the gearbox space is saved; a reverse tooth-connection gear reduces the difficulty of matching of the reverse gear speed and the number of teeth, and meanwhile the requirement for volume of the synchronizers is reduced; the gearbox structure with the seven forward gears enables an engine to be economical and good in dynamic property; the arrangement of the seven forward gears and the reverse gear is more reasonable; each synchronizer is thoroughly utilized; duplicate gears are adopted by the fourth gear and the sixth gear, so that the axial distance of the whole gearbox is shortened and the balance of matching selection of the wheel base and the number of teeth is increased.
Description
Technical field
The utility model relates to a kind of double clutch gearbox, relates in particular to a kind of specific seven forward gears double clutch gearboxes that connect tooth reverse gear structure and have duplicate gear that adopt.
Background technique
The concept of dual-clutch transmission (DCT) has had the history of 60 or seven ten years up till now.As far back as nineteen thirty-nine Germany Kegresse.A first applied for the patent of dual-clutch transmission, proposed manual transmission to be divided into two-part design concept, a part is transmitted odd number shelves, another part transmits even number shelves, and its transmission of power is by two input shafts of two clutch couplings, the driven gear of adjacent each grade interlocks and two input shaft gears engagements, coordinate the control of two clutches, can realize transmission ratio in the situation that not cutting off power, thereby shorten shift time, effectively improve property of automatic shft.
The automobile market of China will develop the change of important meaning in the coming years: rules and market pressure require to improve fuel consumption and emission; Keen competition brings larger cost pressure to car load factory; The increase of city automobile recoverable amount and some crowded regions also require to improve the travelling comfort of driving.Double clutch gearbox has produced exactly under this background.It is short that double clutch gearbox has shift time, engages and carry out the advantages such as suitable, so double clutch gearbox (especially on B level car and SUV) on a lot of cars has application more and more widely.
In prior art, as mentioned a kind of known double clutch gearbox in CN1621715, this double clutch gearbox is six advance gear designs, and adopts short idler shaft configuration reverse gear and three groups of duplicate gear meshing engagement structures.Six advance the design of gear compared to seven gears that advance, and Economy and power character are lower, and engine efficiency loss is high; The design of short idler shaft affects the balance of gearbox integral body, makes inhomogeneous, the whole irregularity of its internal placement, takies gearbox inner space larger, and manufacture cost is higher; Three groups of dual gears have increased the difficulty of number of teeth proportioning, are difficult to realize the requirement of car load speed ratio.
Model utility content
The purpose of this utility model is to solve above-mentioned technical problem, proposes a kind of double clutch gearbox.
The purpose of this utility model, will be achieved by the following technical programs:
A double clutch gearbox, comprising: the first output shaft and the second output shaft that are arranged on first clutch, the second clutch in clutch housing and stretch out in the housing of described gearbox;
Described first clutch is connected with the first input shaft, and described second clutch is connected with the second input shaft and the second input shaft is socketed on the first input shaft, and described the first output shaft, the second output shaft and the first input shaft, the second input shaft are parallel to each other;
Especially,
Described double clutch gearbox is provided with seven advance gear and reverse gear positions,
Described the first input shaft is installed with one grade of driving gear, third speed drive gear, five grades of driving gears and seven grades of driving gears, described one grade of driving gear is arranged between seven grades of driving gears and five grades of driving gears, and described five grades of driving gears are arranged between one grade of driving gear and third speed drive gear;
Described the second input shaft is installed with second gear driving gear and four or six grades of driving gears, and described four or six grades of driving gears are adjacent with third speed drive gear, and described second gear driving gear is adjacent with clutch,
Described the first output shaft is set with first speed driven gear, second gear driven gear, third gear driven gear, fourth gear driven gear and reverse gear and connects gear, and described second gear driven gear connects gear with reverse gear and be coaxially connected,
Described the second output shaft is set with five grades of driven gears, six grades of driven gears, seven grades of driven gears and reverse gear driven gear,
Described first speed driven gear and one grade of driving gear engagement, described second gear driven gear is meshed with second gear driving gear, and described reverse gear connects gear and is meshed with reverse gear driven gear,
Described third gear driven gear and third speed drive gear engagement, described five grades of driven gears and the engagement of five driving gears,
Described fourth gear driven gear and six grades of driven gears and four or six grades of driving gears are duplicate gear meshing engagement structure,
Described seven grades of driven gears and seven grades of driving gear engagements,
On described the first output shaft, be relatively fixed with a third gear synchronizer and two fourth gear synchronizers, a described third gear synchronizer can select to connect first speed driven gear or third gear driven gear, and described two fourth gear synchronizers can select to connect second gear driven gear or fourth gear driven gear;
On described the second output shaft, be relatively fixed with five or seven grades of synchronizers and six reversing-gear synchronizers, described five or seven grades of synchronizers can select to connect five grades of driven gears or seven grades of driven gears, described six reversing-gear synchronizers can select to connect six grades of driven gears and reverse gear driven gear
Preferably, described the first output shaft is also provided with the first main driving gear that subtracts, and described the first master subtracts driving gear and is connected in a differential mechanism.
Preferably, described the second output shaft is also provided with the second main driving gear that subtracts, and described the second master subtracts driving gear and connects described differential mechanism.
Preferably, described the first output shaft and the second output shaft lay respectively at the both sides of described the second input shaft.
The beneficial effects of the utility model are mainly reflected in:
1, the utility model adopts the specific design that connects tooth reverse gear structure, has omitted idler shaft and attached gear in traditional gearbox, has simplified the internal structure of gearbox, has reduced fabricating cost, has saved gearbox space, and integral arrangement is more succinctly smooth-going;
2, reverse gear connects the difficulty that gear has reduced reverse gear ratio number of teeth coupling, has reduced the demand to synchronizer capacity simultaneously;
3, the design of seven forward gears gearbox designs, makes motor have better Economy and power character, and engine efficiency loss is little;
4, seven forward gearss and reverse gear arrange more reasonable, convenient for assembly;
5, each synchronizer is simultaneously effective to two gears, and synchronizer is fully utilized;
6, four or six grades of employing duplicate gears of the present utility model, have shortened the axial distance of gearbox integral body, have reduced the difficulty of number of teeth proportioning simultaneously, increase the balance of wheelbase and the selection of number of teeth proportioning.
Accompanying drawing explanation
Fig. 1 is the structural representation of the utility model double clutch gearbox.
Embodiment
The utility model provides a kind of double clutch gearbox, as shown in Figure 1, comprising: the first output shaft 30 and the second output shaft 40 that are arranged on first clutch 1, the second clutch 2 in clutch housing and stretch out in the housing of gearbox.
First clutch 1 is connected with the first input shaft 10, and second clutch 2 is connected with the second input shaft 20 and the second input shaft 20 and is socketed on the first input shaft 10, the first output shafts 30, the second output shaft 40 and the first input shaft 10, the second input shaft 20 and is parallel to each other.First clutch 1 and second clutch 2 have the transmission of selection Engine torque to the first output shaft 10 and the second output shaft 20.
Described double clutch gearbox is provided with seven advance gear and reverse gear positions.The design of seven grades of gearbox designs, makes motor have better Economy and power character, and engine efficiency loss is little.
The first input shaft 10 is installed with one grade of driving gear 101, third speed drive gear 102, five grades of driving gears 103 and seven grades of driving gears 104, one grade of driving gear 101 is arranged between seven grades of driving gears 104 and five grades of driving gears 103, and five grades of driving gears 103 are arranged between one grade of driving gear 101 and third speed drive gear 102.
It is adjacent with third speed drive gear 102 with 202, four six grades of driving gears 202 of four or six grades of driving gears that the second input shaft 20 is installed with second gear driving gear 201, and second gear driving gear 201 is adjacent with clutch.
The first output shaft 30 is set with first speed driven gear 301, second gear driven gear 302, third gear driven gear 303, fourth gear driven gear 304 and reverse gear and connects gear 305, and described second gear driven gear 302 connects gear 305 with reverse gear and is coaxially connected, for the coaxial mode connecting of gear, have a lot, for example, weld or one-body molded etc.
The second output shaft 40 is set with five grades of driven gears 405, six grades of driven gears 406, seven grades of driven gears 407 and reverse gear driven gears 408.
First speed driven gear 301 and one grade of driving gear 101 engagement, second gear driven gear 302 is meshed with second gear driving gear 201, and reverse gear connects gear 305 and is meshed with reverse gear driven gear 408.
102 engagements of third gear driven gear 303 and third speed drive gear, five grades of driven gears 405 mesh with five driving gears 103.
Fourth gear driven gear 304 and six grades of driven gears 406 and four or six grades of driving gears 202 are duplicate gear meshing engagement structure.
Seven grades of driven gears 407 and seven grades of driving gear 103 engagements.
On the first output shaft 30, be relatively fixed with a third gear synchronizer 501 and two fourth gear synchronizers 502, one third gear synchronizer 501 can select to connect first speed driven gear 301 or third gear driven gear 303, two fourth gear synchronizers 502 can select to connect second gear driven gear 302 or fourth gear driven gear 304.
On the second output shaft 40, be relatively fixed with five or seven grades of synchronizers 502 and six reversing-gear synchronizers 504, five or seven grades of synchronizers 502 can select to connect five grades of driven gears 405 or seven grades of driven gear 407, six reversing-gear synchronizers 504 can select to connect six grades of driven gears 406 and reverse gear driven gear 408.
In addition, the first output shaft 30 is also provided with the first main driving gear that subtracts, the first master subtracts driving gear and connects a differential mechanism, the second output shaft 40 is also provided with the second main driving gear that subtracts, the second master subtracts driving gear and connects above-mentioned differential mechanism, differential mechanism is mainly used in first and second output shaft rotating speed to control, and first and second master subtracts driving gear and differential mechanism belongs to prior art, so omit this part in accompanying drawing.
The first above-mentioned output shaft 30 and the second output shaft 40 lay respectively at the both sides of described the second input shaft 20.
Below will be elaborated to each gear switch of the utility model double clutch gearbox:
First the utility model relates to double clutch switching problem, and double clutch switching belongs to prior art, admittedly do not repeat them here, by switching between double clutch, motor drives switching to the first input shaft 10 and the second input shaft 20.
When neutral gear: first clutch and second clutch are all in off state, and engine power is not exported.
In the time of one grade: a third gear synchronizer 501 engages with first speed driven gear 301, engine-driving the first input shaft 10 rotates, the first input shaft 10 drives one grade of driving gear 101 to rotate, one grade of driving gear 101 drives first speed driven gear 301 to rotate, first speed driven gear 301 drives a third gear synchronizer 501 to rotate, and a third gear synchronizer 501 drives the first output shaft 30 to rotate output.
When second gear: two fourth gear synchronizers 502 engage with second gear driven gear 302, motor drives the second input shaft 20 to rotate by driving the first input shaft 10 to switch to, the second input shaft 20 drives second gear driving gear 201 to rotate, second gear driving gear 201 drives second gear driven gear 302 to rotate, second gear driven gear 302 drives two fourth gear synchronizers 502 to rotate, and two fourth gear synchronizers 502 drive the first output shaft 30 to rotate output.
When third gear: a third gear synchronizer 501 engages with third gear driven gear 303, motor drives the first input shaft 10 to rotate by driving the second input shaft 20 to switch to, the first input shaft 10 drives third speed drive gear 102 to rotate, third speed drive gear 102 drives third gear driven gear 303 to rotate, third gear driven gear 303 drives a third gear synchronizer 501 to rotate, and a third gear synchronizer 501 drives the first output shaft 30 to rotate output.
When fourth gear: two fourth gear synchronizers 502 engage with fourth gear driven gear 304, motor drives the second input shaft 20 to rotate by driving the first input shaft 10 to switch to, the second input shaft 20 drives four or six grades of driving gears 202 to rotate, four or six grades of driving gears 202 drive fourth gear driven gear 304 to rotate, fourth gear driven gear 304 drives two fourth gear synchronizers 502 to rotate, and two fourth gear synchronizers 502 drive the first output shaft 30 to rotate output.
In the time of five grades: five or seven grades of synchronizers 503 engage with five grades of driven gears 405, motor drives the first input shaft 10 to rotate by driving the second input shaft 20 to switch to, the first input shaft 10 drives five grades of driving gears 103 to rotate, five grades of driving gears 103 drive five grades of driven gears 405 to rotate, five grades of driven gears 405 drive five or seven grades of synchronizers 503 to rotate, and five or seven grades of synchronizers 503 drive the second output shaft 40 to rotate output.
In the time of six grades: six reversing-gear synchronizers 504 engage with six grades of driven gears 406, motor drives the second input shaft 20 to rotate by driving the first input shaft 10 to switch to, the second input shaft 20 drives four or six grades of driving gears 202 to rotate, four or six grades of driving gears 202 drive six grades of driven gears 406 to rotate, six grades of driven gears 406 drive six reversing-gear synchronizers 504 to rotate, and six reversing-gear synchronizers 504 drive the second output shaft 40 to rotate output.
In the time of seven grades: five or seven grades of synchronizers 503 engage with seven grades of driven gears 407, motor drives the first input shaft 10 to rotate by driving the second input shaft 20 to switch to, the first input shaft 10 drives seven grades of driving gears 104 to rotate, seven grades of driving gears 104 drive seven grades of driven gears 407 to rotate, seven grades of driven gears 407 drive five or seven grades of synchronizers 503 to rotate, and five or seven grades of synchronizers 503 drive the second output shaft 40 to rotate output.
When reverse gear: two fourth gear synchronizers 502 are separated with second gear driven gear 302, six reversing-gear synchronizers 504 engage with reverse gear driven gear 408, motor drives the second input shaft 20 to rotate by driving the first input shaft 10 to switch to, the second input shaft 20 drives second gear driving gear 201 to rotate, second gear driving gear 201 drives second gear driven gear 302 to rotate, reverse gear connects gear 305 and second gear driven gear 302 coaxial rotation, reverse gear connects gear 305 and drives reverse gear driven gear 408 to rotate, reverse gear driven gear 408 rotates and drives six reversing-gear synchronizers 504 to rotate, six reversing-gear synchronizers 504 drive the second output shaft 40 to rotate output.
Above-mentioned specific reverse gear structure is not only for the gearbox that applies to seven forward gearss of the present utility model, and existing all kinds of gearboxes all can adopt, and can possess the advantage of specific reverse gear mechanism equally after adopting.
The utility model still has numerous embodiments, and all employing equivalents or equivalent transformation and all technological schemes of forming, within all dropping on protection domain of the present utility model.
Claims (4)
1. double clutch gearbox, comprising: the first output shaft and the second output shaft that are arranged on first clutch, the second clutch in clutch housing and stretch out in the housing of described gearbox;
Described first clutch is connected with the first input shaft, and described second clutch is connected with the second input shaft and the second input shaft is socketed on the first input shaft, and described the first output shaft, the second output shaft and the first input shaft, the second input shaft are parallel to each other;
It is characterized in that:
Described double clutch gearbox is provided with seven advance gear and reverse gear positions,
Described the first input shaft is installed with one grade of driving gear, third speed drive gear, five grades of driving gears and seven grades of driving gears, described one grade of driving gear is arranged between seven grades of driving gears and five grades of driving gears, and described five grades of driving gears are arranged between one grade of driving gear and third speed drive gear;
Described the second input shaft is installed with second gear driving gear and four or six grades of driving gears, and described four or six grades of driving gears are adjacent with third speed drive gear, and described second gear driving gear is adjacent with clutch,
Described the first output shaft is set with first speed driven gear, second gear driven gear, third gear driven gear, fourth gear driven gear and reverse gear and connects gear, and described second gear driven gear connects gear with reverse gear and be coaxially connected,
Described the second output shaft is set with five grades of driven gears, six grades of driven gears, seven grades of driven gears and reverse gear driven gear,
Described first speed driven gear and one grade of driving gear engagement, described second gear driven gear is meshed with second gear driving gear, and described reverse gear connects gear and is meshed with reverse gear driven gear,
Described third gear driven gear and third speed drive gear engagement, described five grades of driven gears and the engagement of five driving gears,
Described fourth gear driven gear and six grades of driven gears and four or six grades of driving gears are duplicate gear meshing engagement structure,
Described seven grades of driven gears and seven grades of driving gear engagements,
On described the first output shaft, be relatively fixed with a third gear synchronizer and two fourth gear synchronizers, a described third gear synchronizer can select to connect first speed driven gear or third gear driven gear, and described two fourth gear synchronizers can select to connect second gear driven gear or fourth gear driven gear;
On described the second output shaft, be relatively fixed with five or seven grades of synchronizers and six reversing-gear synchronizers, described five or seven grades of synchronizers can select to connect five grades of driven gears or seven grades of driven gears, and described six reversing-gear synchronizers can select to connect six grades of driven gears and reverse gear driven gear.
2. double clutch gearbox according to claim 1, is characterized in that: described the first output shaft is also provided with the first main driving gear that subtracts, and described the first master subtracts driving gear and is connected in a differential mechanism.
3. double clutch gearbox according to claim 2, is characterized in that: described the second output shaft is also provided with the second main driving gear that subtracts, and described the second master subtracts driving gear and connects described differential mechanism.
4. double clutch gearbox according to claim 1, is characterized in that: described the first output shaft and the second output shaft lay respectively at the both sides of described the second input shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320504095.1U CN203477204U (en) | 2013-08-19 | 2013-08-19 | Double-clutch gearbox |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201320504095.1U CN203477204U (en) | 2013-08-19 | 2013-08-19 | Double-clutch gearbox |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203477204U true CN203477204U (en) | 2014-03-12 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201320504095.1U Expired - Fee Related CN203477204U (en) | 2013-08-19 | 2013-08-19 | Double-clutch gearbox |
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| Country | Link |
|---|---|
| CN (1) | CN203477204U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103557276A (en) * | 2013-08-19 | 2014-02-05 | 吉孚动力技术(中国)有限公司 | Double-clutch transmission |
-
2013
- 2013-08-19 CN CN201320504095.1U patent/CN203477204U/en not_active Expired - Fee Related
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103557276A (en) * | 2013-08-19 | 2014-02-05 | 吉孚动力技术(中国)有限公司 | Double-clutch transmission |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| GR01 | Patent grant | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20140312 Termination date: 20140819 |
|
| EXPY | Termination of patent right or utility model |