CN102720809B - A kind of speed changer and comprise the vehicle of this speed changer - Google Patents

Abstract

A transmission, comprising: a double clutch, a first input shaft, a second input shaft and an output shaft, the double clutch includes a first clutch and a second clutch, the first input shaft is connected to the first clutch, the second input shaft passes through the second The hollow part of an input shaft is connected with the second clutch. The transmission also includes a planetary gear mechanism, a one-way clutch and a gear reduction mechanism. The sun gear is fixed, and the ring gear is fixedly connected with the first input shaft. The one-way clutch is installed on the planet carrier and Power is transmitted between the second input shaft and between the second input shaft and the output shaft through a gear reduction mechanism. The invention also provides a vehicle. The present invention is provided with a planetary gear mechanism and a one-way clutch, so that the second input shaft can transmit the power input by the first clutch in addition to directly transmitting the power input by the second clutch, so an output shaft can be omitted, and the transmission structure can Relatively compact and takes up less space.

Description

A transmission and a vehicle comprising the transmission

technical field

The invention relates to a transmission and a vehicle including the transmission.

Background technique

At present, with the rapid development of vehicle manipulation automation, automotive transmissions are showing a trend of vigorous development. The current automotive automatic transmissions mainly include hydraulic transmissions (AT), continuously variable transmissions (CVT) and electromechanical transmissions (AMT) with high transmission efficiency.

AMT, which is superior to AT and CVT in terms of transmission efficiency and production cost, has been valued by the automotive industry because of its advantages of high fuel economy, low emissions and protection of existing manual transmission production investment required by the development of the automotive industry.

However, during the use of AMT, its shortcomings were gradually discovered: when the vehicle is shifting gears, when the clutch is disengaged, the power of the engine cannot be transmitted to the wheels, resulting in interruption of power, and the driver feels frustrated, which affects the dynamic performance of the vehicle. ride comfort.

In order to solve this problem, precise control of the shifting process is required. Especially in order to reduce the impact of the shifting process, it is necessary to precisely match and control the powertrain composed of the power plant and the transmission in terms of speed difference and torque.

The emergence of DCT (Dual Clutch Transmission) solved this problem. But the DCT has two input shafts and two output shafts, which takes up a lot of space.

Contents of the invention

In order to solve the technical problem that the existing double-clutch transmission occupies a large space, the invention provides a transmission with a small occupation space and a vehicle including the transmission.

One aspect of the present invention provides a transmission, including: a dual clutch, a hollow first input shaft, a second input shaft and an output shaft, the dual clutch includes a first clutch and a second clutch, the first input shaft and The first clutch is connected, and the second input shaft passes through the hollow part of the first input shaft to connect with the second clutch, wherein the transmission also includes a planetary gear mechanism, a one-way clutch and a gear reduction mechanism, so The planetary gear mechanism includes a sun gear, a planet carrier and a ring gear, the sun gear is fixed on the casing of the transmission, the ring gear is fixedly connected to the first input shaft, and the one-way clutch is installed on the planet between the frame and the second input shaft to facilitate one-way power transmission from the planetary gear mechanism to the second input shaft, and the power is transmitted between the second input shaft and the output shaft through a gear reduction mechanism.

Further, the one-way clutch includes an inner ring and an outer ring. When the rotation speed of the outer ring is higher than the rotation speed of the inner ring, the one-way clutch is in a combined state; when the rotation speed of the inner ring is higher than that of the outer ring, the one-way The clutch is in an overrunning state, the inner ring of the one-way clutch is fixed on the second input shaft, and the planet carrier is sleeved on the outer ring of the one-way clutch.

The gear reduction mechanism includes a first gear set, a second gear set and a synchronizer, the first gear set includes a first gear and a second gear that mesh with each other, and the second gear set includes a third gear that meshes with each other and the fourth gear, the first gear and the third gear are fixed on the second input shaft, the second gear and the fourth gear are both hollowly sleeved on the output shaft, the second gear and A synchronizer is installed on the output shaft between the fourth gears.

The gear reduction mechanism also includes a reverse gear set, the reverse gear set includes a fifth gear, an idler gear and a sixth gear, the fifth gear is fixed on the second input shaft, and the sixth gear Fixed on the output shaft, power is transmitted between the fifth gear and the sixth gear through an idler gear.

The transmission also includes a reverse shaft on which the idler gear is mounted.

An output gear is also fixed on the output shaft.

When the synchronizer is synchronized with the fourth gear: the first clutch is engaged, the second clutch is disengaged, and the planetary gear mechanism cooperates with the second gear set to realize the first gear; the second One clutch is disengaged, the second clutch is engaged, and the second gear set constitutes a second gear.

When the synchronizer is synchronized with the second gear: the first clutch is engaged, the second clutch is disengaged, and the planetary gear mechanism cooperates with the first gear set to realize the third gear; the second One clutch is disengaged, the second clutch is engaged, and the first gear set constitutes a fourth gear.

When the synchronizer is disconnected: the first clutch is engaged, the second clutch is disengaged, and the planetary gear mechanism cooperates with the reverse gear set to realize a low-speed reverse gear; the first clutch is disengaged, The second clutch is combined, and the reverse gear set constitutes a high-speed reverse gear.

Another aspect of the present invention also provides a vehicle, including a power source and a differential, wherein the vehicle also includes the above-mentioned transmission, the power source is connected to the dual clutch of the transmission, and the output shaft of the transmission connected to the differential.

The transmission of the present invention and the vehicle comprising the transmission are provided with a planetary gear mechanism and a one-way clutch, so that the power of the first input shaft can be transmitted to the second input shaft in one direction and then output. The power input by the second clutch can also transmit the power input by the first clutch, so an output shaft can be omitted, thereby making the transmission more compact in structure and occupying less space.

Description of drawings

Fig. 1 is a schematic structural diagram of a transmission provided in an embodiment of the present invention;

Fig. 2 is a schematic diagram of the state of the transmission in the first gear provided by an embodiment of the present invention, wherein the thick solid line represents the power transmission route;

Fig. 3 is a schematic diagram of the state of the transmission in the second gear provided by an embodiment of the present invention, wherein the thick solid line represents the power transmission route;

Fig. 4 is a schematic diagram of the state of the transmission in the third gear provided by an embodiment of the present invention, wherein the thick solid line represents the power transmission route;

Fig. 5 is a schematic diagram of the state of the transmission in the fourth gear provided by an embodiment of the present invention, wherein the thick solid line represents the power transmission route;

Fig. 6 is a schematic diagram of the state of the transmission in a low-speed reverse gear provided by an embodiment of the present invention, wherein the thick solid line represents the power transmission route;

Fig. 7 is a schematic diagram of the state of the transmission in a high-speed reverse gear provided by an embodiment of the present invention, wherein the thick solid line represents the power transmission route;

Fig. 8 is a schematic structural diagram of a vehicle provided by an embodiment of the present invention.

detailed description

In order to make the technical problems, technical solutions and beneficial effects solved by the present invention clearer, the present invention will be further described in detail below in conjunction with the accompanying drawings and embodiments. It should be understood that the specific embodiments described here are only used to explain the present invention, not to limit the present invention.

According to an embodiment of the present invention, as shown in FIG. 1 , a transmission includes: a dual clutch 1, a hollow first input shaft 4, a second input shaft 8 and an output shaft 20, and the dual clutch 1 includes a first clutch 3 and the second clutch 2, the first input shaft 4 is connected with the first clutch 3, the second input shaft 8 passes through the hollow part of the first input shaft 4 and is connected with the second clutch 2, wherein the transmission also includes a planetary gear mechanism 23. One-way clutch 7 and gear reduction mechanism 27. Planetary gear mechanism 23 includes sun gear 22, planet carrier 6 and ring gear 5. Sun gear 22 is fixed on the transmission case (not shown in the figure), and ring gear 5 Fixedly connected with the first input shaft 4, the one-way clutch 7 is installed between the planetary carrier 6 and the second input shaft 8 so as to transfer power from the planetary gear mechanism 23 to the second input shaft 8 in one direction, the second input shaft 8 and Power is transmitted between the output shafts 20 through a gear reduction mechanism 27 .

Generally, in order to install components such as input shafts and output shafts, the transmission includes a housing, a double clutch 1, a first input shaft 14, a second input shaft 8, an output shaft 20, a planetary gear mechanism 23, a one-way clutch 7 and a gear The reduction mechanism 27 is all installed in the housing.

Dual clutch 1 can choose dry dual clutch or wet dual clutch according to needs. There are two clutches in dual clutch 1, that is, the first clutch 3 and the second clutch 2. The first clutch 3 and the second clutch 2 are alternately combined or separated. Power transmission can be controlled.

Knownly, the planetary gear mechanism 23 includes the sun gear 22, the planet carrier 6 and the ring gear 5, and the connection between the sun gear 22 and the ring gear 5 is formed by a plurality of, for example, three planet gears, and the planet carrier 6 is connected with all the planet gears, Among the sun gear 22 , the planet carrier 6 and the ring gear 5 , one is fixed, and among the remaining two, one can input power, and the other can output power.

Those skilled in the art can reasonably set the size of the planetary gear mechanism 23 according to needs, and select one of the fixed sun gear 22, the planet carrier 6 and the ring gear 5, so as to form a suitable reduction ratio.

The fixing of any one of the sun gear 22, the planet carrier 6 and the ring gear 5 can be realized by various suitable devices, such as utilizing a brake.

According to one embodiment of the present invention, the sun gear 22 is directly fixed to the casing of the transmission, the ring gear 5 is fixedly connected to the first input shaft 4 as the power input end, and the planet carrier 6 is connected to the one-way clutch 7 as the power output end .

The ring gear 5 can be fixedly connected to the first input shaft 4 in various suitable ways, such as integrally formed or splined.

Further, the one-way clutch 7 includes an inner ring and an outer ring. When the speed of the outer ring is higher than that of the inner ring, the one-way clutch 7 is in a combined state. When the speed of the inner ring is higher than that of the outer ring, the one-way The clutch 7 is in an overrunning state, the inner ring of the one-way clutch 7 is fixed on the second input shaft 8 , and the planet carrier 6 is sleeved on the outer ring of the one-way clutch 7 .

The function of the one-way clutch is to make a certain element only rotate in a certain direction and lock in the other direction. According to the power transmission device (such as roller or wedge) installed between the inner ring and the outer ring, it can be divided into roller type one-way clutch and wedge type one-way clutch. Those skilled in the art can select a suitable type of one-way clutch according to needs.

According to one embodiment of the present invention, when the rotation speed of the outer ring is higher than the rotation speed of the inner ring, the one-way clutch 7 is in the engaged state, and the power can be transmitted from the planetary gear mechanism 23 to the second input shaft 8; when the rotation speed of the inner ring When the rotational speed is higher than that of the outer ring, the one-way clutch 7 is in an overrunning state, and at this time, the power of the second input shaft 8 will not be transmitted to the planetary gear mechanism 23 .

Further, the gear reduction mechanism 27 includes a first gear set 9, a second gear set 11 and a synchronizer 18, the first gear set 9 includes a first gear 21 and a second gear 19 that mesh with each other, and the second gear set 11 includes a mutual The meshing third gear 10 and the fourth gear 17, the first gear 21 and the third gear 10 are all fixed on the second input shaft 8, the second gear 19 and the fourth gear 17 are both hollowly sleeved on the output shaft 20, and the first gear 21 and the third gear 10 are all fixed on the second input shaft 8. A synchronizer 18 is installed on the output shaft 20 between the second gear 19 and the fourth gear 17 .

The first gear 21 and the second gear 19 form a constant mesh, and the third gear 10 and the fourth gear 17 form a constant mesh.

The synchronizer 18 can be synchronized with the second gear 19 to facilitate the transmission of power by the first gear set 9 , and the synchronizer 18 can also be synchronized with the fourth gear 17 to facilitate the transmission of power by the second gear set 11 .

In order to realize the reverse gear, the gear reduction mechanism 27 also includes a reverse gear set 26, the reverse gear set 26 includes the fifth gear 12, the idler gear 13 and the sixth gear 14, the fifth gear 12 is fixed on the second input shaft 8, The sixth gear 14 is fixed on the output shaft 20 , and power is transmitted between the fifth gear 12 and the sixth gear 14 through the idler gear 13 .

In order to mount the idler gear 13, the transmission also includes a reverse gear shaft 15 on which the idler gear 13 is mounted. When it is necessary to reverse the vehicle, the idler gear 13 can be meshed with the fifth gear 12 and the sixth gear 14 at the same time by manipulating the shift lever, thereby completing the power transmission of the reverse gear.

In order to output power, an output gear 16 is also fixed on the output shaft 20 so as to output the power input to the transmission to the wheels (realized through a differential).

According to an embodiment of the present invention, when the synchronizer 18 is synchronized with the fourth gear 17: the first clutch 3 is engaged, the second clutch 2 is disengaged, and the planetary gear mechanism 23 cooperates with the second gear set 11 to realize the first gear; The first clutch 3 is disengaged, the second clutch 2 is engaged, and the second gear set 11 constitutes the second gear.

When the synchronizer 18 is synchronized with the second gear 19: the first clutch 3 is combined, the second clutch 2 is separated, and the planetary gear mechanism 23 cooperates with the first gear set 9 to realize the third gear; the first clutch 3 is separated, and the second clutch 2 combined, the first gear set 9 constitutes the fourth gear.

When the synchronizer 18 is disconnected (neither synchronized with the second gear 19 nor synchronized with the fourth gear 17): the first clutch 3 is engaged, the second clutch 2 is disengaged, and the planetary gear mechanism 23 cooperates with the reverse gear set 26 A low-speed reverse gear is realized; the first clutch 3 is separated, the second clutch 2 is combined, and the reverse gear set 26 constitutes a high-speed reverse gear.

The gear switching process of the speed changer of the present invention is described in detail below in conjunction with accompanying drawing:

According to one embodiment of the present invention, as shown in Figure 2, when the synchronizer 18 is synchronized with the fourth gear 17, the first clutch 3 is controlled to be engaged, the second clutch 2 is disengaged, and the power is sequentially input from the first clutch 3, the first Shaft 4, ring gear 5, planet carrier 6, one-way clutch 7 (at this time, the speed of the second input shaft 8 is lower than the speed output by the planet carrier 6, that is, the speed of the outer ring of the one-way clutch 7 is higher than that of the inner ring speed, the one-way clutch 7 is in the engaged state), the second input shaft 8 and the second gear set 11 are transmitted to the output gear 16 on the output shaft 20 . During this process, the planetary gear mechanism 23 and the second gear set 11 jointly form the transmission ratio of the first gear, that is, the switching of the first gear is realized.

According to one embodiment of the present invention, as shown in FIG. 3 , the synchronizer 18 continues to synchronize with the fourth gear 17. At this time, the first clutch 3 is controlled to be disengaged, the second clutch 2 is engaged, and the power will be transferred from the second clutch 2 in sequence. , the second input shaft 8 and the second gear set 11 are transmitted to the output gear 16 on the output shaft 20 . During this process, since the rotation speed of the second input shaft 8 is higher than the rotation speed of the planet carrier 6 (at this time, the rotation speed of the planet carrier 6 can be zero), that is, the rotation speed of the outer ring of the one-way clutch 7 is lower than the rotation speed of the inner ring , the one-way clutch 7 is in the overrunning state. At this time, the power of the second input shaft 8 will not be transmitted to the first input shaft 4, and the planetary gear mechanism 23 will not work. Therefore, the second gear set 11 alone forms the second gear. .

It can be seen that the switching between the first gear and the second gear can be realized only by controlling the first clutch 3 and the second clutch 2 in the dual clutch 1 to alternately engage and disengage, thereby effectively reducing the power during the shifting process. Shock, improve the ride comfort of the vehicle.

According to one embodiment of the present invention, as shown in Figure 4, the synchronizer 18 is synchronized with the second gear 19 (at this time, the synchronizer 18 is switched from the position of synchronizing with the fourth gear 19 to the position of synchronizing with the second gear through the shift lever. gear 19 synchronous position), control the combination of the first clutch 3 and the separation of the second clutch 2, and the power is sequentially transmitted from the first clutch 3, the first input shaft 4, the ring gear 5, the planetary carrier 6, and the one-way clutch 7 (at this time, The speed of the second input shaft 8 is lower than the speed output by the planet carrier 6, that is, the speed of the outer ring of the one-way clutch 7 is higher than the speed of the inner ring, and the one-way clutch 7 is in a combined state), the second input shaft 8 and the second A gear set 9 transmits to an output gear 16 on an output shaft 20 . During this process, the planetary gear mechanism 23 and the first gear set 9 jointly form the transmission ratio of the third gear, that is, the switching of the third gear is realized.

According to one embodiment of the present invention, as shown in Figure 5, the synchronizer 18 continues to synchronize with the second gear 19. At this time, the first clutch 3 is controlled to be disengaged, the second clutch 2 is engaged, and the power will be transferred from the second clutch 2 in sequence. , the second input shaft 8 and the first gear set 9 are transmitted to the output gear 16 on the output shaft 20 . During this process, since the rotation speed of the second input shaft 8 is higher than the rotation speed of the planet carrier 6 (at this time, the rotation speed of the planet carrier 6 can be zero), that is, the rotation speed of the outer ring of the one-way clutch 7 is lower than the rotation speed of the inner ring , the one-way clutch 7 is in the overrunning state. At this time, the power of the second input shaft 8 will not be transmitted to the first input shaft 4, and the planetary gear mechanism 23 will not work. Therefore, the first gear set 9 alone forms the fourth gear. .

It can be seen that the switch between the third gear and the fourth gear can be realized only by controlling the first clutch 3 and the second clutch 2 in the dual clutch 1 to alternately engage and separate, thereby effectively reducing the power during the shifting process. Shock, improve the ride comfort of the vehicle.

According to one embodiment of the present invention, as shown in Figure 6, the synchronizer 18 is in the initial position (that is, the synchronizer is disconnected), that is, the synchronizer 18 is neither synchronized with the second gear 19, nor synchronized with the fourth gear 17 syncs. Control the combination of the first clutch 3 and the separation of the second clutch 2, and the power is sequentially transferred from the first clutch 3, the first input shaft 4, the ring gear 5, the planetary carrier 6, and the one-way clutch 7 (at this time, the speed of the second input shaft 8 be lower than the rotational speed output by the planetary carrier 6, that is, the rotational speed of the outer ring of the one-way clutch 7 is higher than the rotational speed of the inner ring, and the one-way clutch 7 is in a combined state), the second input shaft 8 and the reverse gear set 26 (at this time , by manipulating the shift lever to switch to reverse gear, the idler gear 13 meshes with the fifth gear 12 and the sixth gear 14 at the same time) is transmitted to the output gear 16 on the output shaft 20 . During this process, the planetary gear mechanism 23 and the reverse gear set 26 jointly form the transmission ratio of the low-speed reverse gear, that is, the switching of the low-speed reverse gear is realized.

According to one embodiment of the present invention, as shown in FIG. 7 , the synchronizer 18 continues to be in the initial position, the first clutch 3 is controlled to be disengaged, the second clutch 2 is engaged, and the power will be sequentially transmitted from the second clutch 2 and the second input shaft 8 and the second gear set 11 to the output gear 16 on the output shaft 20 . During this process, since the rotation speed of the second input shaft 8 is higher than the rotation speed of the planet carrier 6 (at this time, the rotation speed of the planet carrier 6 can be zero), that is, the rotation speed of the outer ring of the one-way clutch 7 is lower than the rotation speed of the inner ring , the one-way clutch 7 is in the overrunning state. At this time, the power of the second input shaft 8 will not be transmitted to the first input shaft 4, and the planetary gear mechanism 23 will not work. Therefore, the reverse gear set 26 alone forms a high-speed reverse gear bit.

It can be seen from this that the switch between the low-speed reverse gear and the high-speed reverse gear can be realized only by controlling the first clutch 3 and the second clutch 2 in the dual clutch 1 to be alternately combined and separated, thereby effectively reducing the gear shifting process. The dynamic shock improves the ride comfort of the vehicle.

When both the first clutch 3 and the second clutch 2 are disengaged, the power is interrupted, and neutral gear can be realized at this moment.

According to an embodiment of the present invention, as shown in FIG. 8 , another aspect of the present invention also provides a vehicle, including a power source 24 and a differential 25, wherein the vehicle also includes the above-mentioned transmission, and the power source 24 It is connected with the dual clutch 1 of the transmission, and the output shaft 20 of the transmission is connected with the differential 25 .

The power source 24 can be powered by an engine or a motor as required, and the power source 24 and the dual clutch 1 can be fixed together by various suitable methods such as welding and riveting.

The output shaft 20 is connected to the differential gear 25, more specifically, the output shaft 20 is provided with an output gear 16, and the output gear 16 meshes with the planet carrier (differential gear case) of the differential gear 25 to realize power transmission.

The transmission of the present invention and the vehicle comprising the transmission are provided with a planetary gear mechanism and a one-way clutch, so that the power of the first input shaft can be transmitted to the second input shaft in one direction and then output. The power input by the second clutch can also transmit the power input by the first clutch, so an output shaft can be omitted, thereby making the transmission more compact in structure and occupying less space.

In addition, a gear reduction mechanism is provided between the second input shaft and the output shaft, and the gear reduction mechanism cooperates with the planetary gear mechanism to realize multiple gears, thereby improving the power line and economy of the power source, especially the engine.

At the same time, switching between the odd and even gears (such as the first gear and the second gear, the third gear and the fourth gear) formed by the same gear set can be realized by controlling the dual clutch, thus effectively reducing the gear shifting process. The dynamic impact can realize uninterrupted shifting and improve the ride comfort of the vehicle.

Moreover, when the synchronizer is synchronized with a gear set, two gears can be realized by controlling the first clutch and the second clutch in the double clutch to alternately combine and separate, so through the control of the double clutch, one synchronizer can realize four gears. It is beneficial to simplify the structure of the transmission, make the transmission more compact, and simplify the operation of shifting gears.

The above descriptions are only preferred embodiments of the present invention, and are not intended to limit the present invention. Any modifications, equivalent replacements and improvements made within the spirit and principles of the present invention should be included in the protection of the present invention. within range.

Claims (10)

1. a speed changer, comprise: double clutch, first input shaft of hollow, second input shaft and output shaft, described double clutch comprises first clutch and second clutch, described first input shaft is connected with first clutch, described second input shaft is connected with described second clutch through the hollow space of described first input shaft, it is characterized in that, described speed changer also comprises planetary gears, overrunning clutch and reduction gears mechanism, described planetary gears comprises sun gear, planet carrier and gear ring, described sun gear is fixed on the housing of speed changer, described gear ring is fixedly connected with described first input shaft, and the transmission of power of described first input shaft is to the second input shaft and then output, described overrunning clutch is arranged between described planet carrier and the second input shaft so that from planetary gears to the second input shaft unidirectional delivery power, by reduction gears mechanism transferring power between described second input shaft and output shaft,

Described overrunning clutch comprises inner ring and outer ring, and the inner ring of described overrunning clutch is fixed on described second input shaft, and described planet carrier is sleeved on the outer ring of described overrunning clutch.

2. speed changer as claimed in claim 1, is characterized in that, when rotating speed higher than inner ring of the rotating speed of outer ring, overrunning clutch is in bonding state, and when rotating speed higher than outer ring of the rotating speed of inner ring, overrunning clutch is in and surmounts state.

3. speed changer as claimed in claim 1, it is characterized in that, described reduction gears mechanism comprises the first gear train, the second gear train and synchronizer, described first gear train comprises intermeshing first gear and the second gear, described second gear train comprises intermeshing 3rd gear and the 4th gear, described first gear and the 3rd gear are all fixed on described second input shaft, described second gear and the equal empty set of the 4th gear, on described output shaft, the output shaft between described second gear and the 4th gear are provided with synchronizer.

4. speed changer as claimed in claim 3, it is characterized in that, described reduction gears mechanism also comprises reverse gear group, described reverse gear group comprises the 5th gear, idle pulley and the 6th gear, described 5th gear is fixed on described second input shaft, described 6th gear is fixed on described output shaft, by idle pulley transferring power between described 5th gear and the 6th gear.

5. speed changer as claimed in claim 4, it is characterized in that, described speed changer also comprises reverse gear shaft, and described idle pulley is arranged on described reverse gear shaft.

6. speed changer as claimed in claim 4, is characterized in that, described output shaft is also fixed with output gear.

7. speed changer as claimed in claim 3, is characterized in that, when described synchronizer and described 4th gear synchronous: described first clutch is combined, and described second clutch separation, described planetary gears coordinates with described second gear train and realizes the first gear; Described first clutch is separated, and described second clutch combines, and described second gear train forms the second gear.

8. speed changer as claimed in claim 7, is characterized in that, when described synchronizer and described second gear synchronous: described first clutch is combined, and described second clutch separation, described planetary gears coordinates with described first gear train and realizes third gear position; Described first clutch is separated, and described second clutch combines, and described first gear train forms fourth gear position.

9. speed changer as claimed in claim 4, is characterized in that, when described synchronizer disconnects: described first clutch combines, described second clutch is separated, and described planetary gears and described reverse gear assembly are closed and realized low speed and to reverse gear gear; Described first clutch is separated, and described second clutch combines, and described reverse gear group forms the gear that reverses gear at a high speed.

10. a vehicle, comprise power source and differential mechanism, it is characterized in that, described vehicle also comprises the speed changer in claim 1-9 described in any one, described power source is connected with the double clutch of described speed changer, and the output shaft of described speed changer is connected with described differential mechanism.