CN202901186U - Planet gear type manual transmission - Google Patents

Abstract

The utility model discloses a planetary gear type manual transmission, which includes an input shaft, an output shaft, an intermediate shaft arranged between the input shaft and the output shaft, a shaft sleeve, a synchronizer or a brake, and also includes a double-row planetary gear train, a planetary row The double-row planetary gear system includes a small sun gear, a large sun gear, a short planetary gear, a long planetary gear, a front planetary carrier, a front ring gear, a front planetary carrier on a short planetary gear and a long planetary gear, and a small sun gear and a short planetary gear. The planetary gear meshes, the long planetary gear meshes with the big sun gear, the short planetary gear and the front ring gear respectively, and the small sun gear is fixedly connected with the big sun gear; the third planetary gear of the planet row is set on the rear planet carrier, and the third sun gear It meshes with the third planetary gear, which meshes with the rear ring gear. The utility model adopts the Lavina type and single-row planetary gear transmission mechanism, realizes the purpose of five-speed ratio gears with a very small number of gears, reduces the axial and radial dimensions of the transmission, and makes the automobile structure layout design more flexible.

Description

Planetary manual transmission

technical field

The utility model relates to the technical field of automobile transmissions, in particular to a planetary gear type manual transmission. the

Background technique

During the normal driving process of the vehicle, the engine is the link of producing power, the clutch is the hub of transmitting power, and the transmission is the link of realizing the normal operation of the vehicle under different driving conditions, that is, distributing power. The automobile transmission is set up to solve the contradiction between the rotational speed and torque output by the engine and the rotational speed and torque required for driving the vehicle. As the heart of the transmission system, the main task of the transmission is to transmit power, change the transmission ratio of the car, expand the range of driving wheel torque and speed, make the vehicle adapt to various driving conditions, and at the same time make the engine work under ideal conditions , under the premise that the direction of the engine torque remains unchanged, the car can be driven backwards, the neutral gear can be realized, the power transmitted from the engine to the wheels can be interrupted, and the engine can be started and idled. The quality of vehicle driving performance depends not only on the engine, but also depends on the transmission and the matching between the transmission and the engine to a large extent. the

Transmissions are divided into manual transmissions and automatic transmissions, among which manual transmissions are a relatively traditional type of transmission. Manual transmissions must be changed by the driver at any time according to changes in vehicle conditions. It is relatively cumbersome to operate, but it can express the driver more directly. Willingness, so it is loved by those who love driving. The manual transmission is composed of gear sets with different gear ratios, and its working principle is to realize the transformation of gear ratios by switching different gear sets. The gear set is composed of gears with different diameters, and the power transmission effects achieved by different gear ratios are completely different. What we call shifting refers to changing gear ratios. At present, almost all automobile manual transmissions use parallel-shaft transmissions. Front-drive parallel-shaft transmissions need three shafts, and rear-drive parallel-shaft transmissions need four shafts, all of which are three axes. At the same time, the axial and longitudinal dimensions of the transmission are uniform Larger size is not conducive to the structural layout design of the car. the

Utility model content

The technical problem to be solved by the utility model is to provide a manual transmission with a new structure, which can reduce the axial and radial dimensions of the transmission, so as to overcome the deficiencies of the prior art. the

In order to solve the above technical problems, the technical solution adopted by the utility model is: a planetary gear type manual transmission, including an input shaft, an output shaft, an intermediate shaft arranged between the input shaft and the output shaft, a shaft sleeve, and a synchronizer Or brakes, also includes double-row planetary gear system, planetary row, said double-row planetary gear system includes small sun gear, big sun gear, short planetary gear, long planetary gear, front planet carrier, front ring gear, said short planet The front planet carrier is arranged on the wheel and the long planetary gear, the small sun gear meshes with the short planetary gear, the long planetary gear meshes with the big sun gear, the short planetary gear and the front ring gear respectively, and the small sun gear meshes with the big sun gear fixed connection; the planet row includes a third sun gear, a third planet gear, a rear planet carrier, and a rear ring gear, the third planet gear is arranged on the rear planet carrier, and the third sun gear and the third planet gear meshing, the third planetary gear meshes with the rear ring gear. the

Preferably, the output shaft is fixedly connected to the rear planetary carrier, an output shaft sleeve is arranged on the output shaft, and the third sun gear is fixed on the output shaft sleeve. the

Preferably, an intermediate shaft sleeve and an outer shaft sleeve are sleeved on the intermediate shaft, the intermediate shaft is fixedly connected to the front planet carrier, the small sun gear is fixed on the intermediate shaft sleeve, and the large sun gear The wheel is fixed on the outer axle sleeve. the

Preferably, a high-speed and reverse gear synchronizer is arranged between the input shaft and the intermediate shaft, and the forward gear synchronizer connects the high-speed and reverse gear synchronizer with the intermediate shaft sleeve, and the reverse gear synchronizer connects the forward gear to synchronize The gear and the outer shaft sleeve, the front brake is set between the outer shaft sleeve and the front planetary carrier, the fifth-speed synchronizer connects the rear ring gear and the third sun gear, and the rear brake is also arranged on the third sun gear. the

Preferably, the front ring gear is fixedly connected to the rear ring gear. the

Preferably, gear teeth are provided on the outer circumferences of the front ring gear and the rear ring gear, and the front ring gear and the rear ring gear are meshedly connected. the

Preferably, the output shaft is arranged on the same side as the input shaft. the

Compared with the prior art, the utility model has the following advantages: the utility model adopts the Lavina type and single-row planetary gear transmission mechanism, and cooperates with multiple synchronizers, so that it can achieve the use of a very small number of gears The goal of five-speed ratio gear is realized, and the axial and radial dimensions of the transmission can be reduced, so that the size of the transmission can be controlled, the structural layout design of the car is more flexible, and the production cost can be reduced at the same time. the

Description of drawings

Fig. 1 is a schematic diagram of the power transmission mechanism of the first embodiment of the planetary gear manual transmission of the present invention. the

Fig. 2 is a running state diagram of the first gear of the first embodiment of the utility model. the

Fig. 3 is a diagram of the second gear running state of the first embodiment of the utility model. the

Fig. 4 is a diagram of the 3rd gear running state of the first embodiment of the utility model. the

Fig. 5 is a diagram of the 4th gear running state of the first embodiment of the utility model. the

Fig. 6 is a diagram of the 5th gear running state of the first embodiment of the utility model. the

Fig. 7 is a diagram of the reverse gear running state of the first embodiment of the utility model. the

Fig. 8 is a schematic diagram of the power transmission mechanism of the second embodiment of the present invention. the

Detailed ways

Below, in conjunction with the drawings and specific embodiments of the description, the technical solution of the present utility model is further described. It should be understood that the specific embodiments described here are only used to explain the present utility model, and do not constitute limitations to the present utility model:

first embodiment

Referring to Fig. 1 to Fig. 7, the planetary gear type manual transmission of the present invention includes an input shaft 11, a plurality of synchronizers or brakes, an intermediate shaft 12, an intermediate shaft sleeve 13, an outer shaft sleeve 14, an output shaft sleeve 15, an output shaft 16, double-row planetary gear train 51, planet row 52.

The double-row planetary gear train 51 adopts a Ravigneaux gear transmission mechanism, which includes a small sun gear 35, a large sun gear 31, a short planetary gear 34, a long planetary gear 32, a front planet carrier 36, a front ring gear 33, a small sun gear 35 is meshed with the short planetary gear 34, and the long planetary wheel 32 is meshed with the large sun gear 31, the short planetary wheel 34 and the front ring gear 33 respectively. the

The planetary row 52 adopts a single planetary row, which includes the third sun gear 40 , the third planetary gear 39 , the rear planet carrier 37 , and the rear ring gear 38 , and the output shaft is fixedly connected to the rear planet carrier 37 . The third sun gear 40 meshes with the third planetary gear 39 , and the third planetary gear 39 meshes with the rear ring gear 38 . the

The high speed and reverse gear synchronizer 21 connects the input shaft 11 and the intermediate shaft 12 . The forward gear synchronizer 22 is connected with the high speed and reverse gear synchronizer 21 and the intermediate shaft sleeve 13 . The reverse gear synchronizer 23 connects the forward gear synchronizer 22 and the outer shaft sleeve 14 . The front brake 24 may secure the outer bushing 14 or the front planet carrier 36, respectively. The fifth-speed synchronizer 25 connects the rear ring gear 38 and the third sun gear 40 . The rear brake 26 may secure the third sun gear 40 . the

The shift operation process is as follows:

As shown in FIG. 1 , in the neutral state, the high speed and reverse synchronizer 21 is on the left side, connected with the input shaft 11 and separated from the intermediate shaft 12 . The forward gear synchronizer 22 is on the right side, and is connected with the high-speed and reverse gear synchronizer 21 and the intermediate shaft sleeve 13. The reverse gear synchronizer 23 is on the left side, connected with the forward gear synchronizer 22 and separated from the outer shaft sleeve 14 . The front brake 24 is in the middle and is separated from the outer shaft sleeve 14 and the front planetary carrier 36 . The fifth gear synchronizer 25 is on the left side, connected with the rear ring gear 38 and separated from the third sun gear 40 . The rear brake 26 is on the left side and is connected to the third sun gear 40 to fix it.

高速及倒档同步器21

前进档同步器22

中间轴套13

小太阳轮35

短行星轮34

长行星轮32前齿圈33

后齿圈38

第三行星轮39后行星架37输出轴16。其余同步器处于空档状态时的位置。图2中，粗实线表示动力传递路线。  As shown in FIG. 2 , when the first gear is running, the front brake 24 moves to the right to fix the front planetary carrier 36 . At this time, the power transmission route is: input shaft 11

High speed and reverse synchronizer 21

Forward gear synchronizer 22

Intermediate shaft sleeve 13

Small sun wheel 35

Short planetary gear 34

Long planetary gear 32 Front ring gear 33

Rear gear 38

The third planetary gear 39 Rear planet carrier 37 output shaft 16. The position of the rest of the synchronizers when they are in neutral. In FIG. 2 , thick solid lines indicate power transmission routes.

中间轴套13

小太阳轮35

短行星轮34

长行星轮32

前齿圈33后齿圈38

第三行星轮39

后行星架37

输出轴16，但二档时大太阳轮31固定，前行星架顺时针公转，加快了输出转速。其余同步器处于空档状态时的位置。图3中，粗实线表示动力传递路线。  As shown in Figure 3, when the second gear is running, the front brake 24 moves to the left, the outer shaft sleeve 14 is fixed, and the big sun gear 31 is also fixed simultaneously. The position of the rest of the synchronizers when they are in neutral. At this time, the power transmission route is: its transmission route is basically the same as that of the first gear, and it is also driven by the input shaft 11. High speed and reverse synchronizer 21 Forward gear synchronizer 22

Intermediate shaft sleeve 13

Small sun wheel 35

Short planetary gear 34

Long planetary gear 32

Front ring gear 33 Rear gear 38

The third planetary gear 39

Rear planet carrier 37

Output shaft 16, but during the second gear, the large sun gear 31 is fixed, and the front planet carrier revolves clockwise, which speeds up the output speed. The position of the rest of the synchronizers when they are in neutral. In FIG. 3 , thick solid lines indicate power transmission routes.

前行星架36 

短行星轮34

长行星轮32。  As shown in Figure 4, when the third gear is running, the high-speed and reverse gear synchronizer 21 moves to the right, and the input shaft 11 is connected with the intermediate shaft 12, so that the double-row planetary gear train 51 forms a whole. The rotation of the intermediate shaft 12 drives the front planet carrier 36 to rotate synchronously with the intermediate bushing 13. At this time, the power transmission route is: the input shaft 11 The high-speed and reverse gear synchronizer 21, at this time, separates two branches, and the power route of one of them is: intermediate shaft 12

Front planet carrier 36

Short planetary gear 34

Long planetary wheel 32.

中间轴套13

小太阳轮35

长行星轮32。然后由长行星轮32前齿圈33

后齿圈38

第三行星轮39

后行星架37

输出轴16。  The power route of another branch is: forward gear synchronizer 22

Intermediate shaft sleeve 13

Small sun wheel 35

Long planetary wheel 32. Then by the long planetary wheel 32 Front ring gear 33

Rear gear 38

The third planetary gear 39

Rear planet carrier 37

output shaft 16.

The position of the rest of the synchronizers when they are in neutral. In FIG. 4 , thick solid lines indicate power transmission routes. the

高速及倒档同步器21

中间轴12

前行星架36长行星轮32

前齿圈33

后齿圈38

第三行星轮39后行星架37

输出轴16。其余同步器处于空档状态时的位置。图5中，粗实线表示动力传递路线。  As shown in Figure 5, when the fourth gear is running, the high-speed and reverse gear synchronizer 21 moves to the right to connect the input shaft 11 with the intermediate shaft 12, the forward gear synchronizer 22 moves to the left to separate from the intermediate shaft sleeve 13, and the front brake 24 moves to the left , the outer shaft sleeve 14 is fixed, and the large sun gear 31 is also fixed simultaneously. At this time, the power transmission route is: input shaft 11

High speed and reverse synchronizer 21

intermediate shaft 12

Front planet carrier 36 Long planetary gear 32

Front ring gear 33

Rear gear 38

The third planetary gear 39 Rear planet carrier 37

output shaft 16. The position of the rest of the synchronizers when they are in neutral. In FIG. 5 , thick solid lines indicate power transmission routes.

高速及倒档同步器21

中间轴12

前行星架36

长行星轮32

前齿圈33。此时，分开两条支路，其中一条支路的动力路线是：后齿圈38

第三行星轮39

后行星架37。  As shown in Figure 6, when the fifth gear is running, the high-speed and reverse gear synchronizer 21 moves to the right to connect the input shaft 11 with the intermediate shaft 12, the forward gear synchronizer 22 is separated from the intermediate shaft sleeve 13, and the front brake 24 moves to the left to Outer axle sleeve 14 is fixed, and big sun gear 31 is also fixed simultaneously. The fifth gear synchronizer 25 moves to the right, and is connected with the rear ring gear 38 and the third sun gear 40 so that it is connected as one, and the rear brake 26 moves to the right, and separates with the third sun gear 40. At this time, the power transmission route is: input shaft 11

High speed and reverse synchronizer 21

intermediate shaft 12

Front planet carrier 36

Long planetary gear 32

Front ring gear 33. At this time, two branch roads are separated, and the power route of one branch road is: rear ring gear 38

The third planetary gear 39

Rear planet carrier 37.

后行星架37。然后由后行星架37传递至输出轴16。  The power route of another branch is: fifth gear synchronizer 25 third sun gear 40

Rear planet carrier 37. Then it is transmitted to the output shaft 16 by the rear planet carrier 37 .

The position of the rest of the synchronizers when they are in neutral. In FIG. 6 , thick solid lines indicate power transmission routes. the

高速及倒档同步器21

前进档同步器22倒档同步器23

外轴套14大太阳轮31

长行星轮32

前齿圈33

后齿圈38

第三行星轮39后行星架37

输出轴16。此时，输入轴11与输出轴16的旋转方向相反。其余同步器处于空档状态时的位置。图7中，粗实线表示动力传递路线。  As shown in Figure 7, during reverse gear operation, the forward gear synchronizer 22 moves left and separates from the intermediate shaft sleeve 13, the reverse gear synchronizer 23 moves right and is connected with the outer shaft sleeve 14, and the front brake 24 fixes the front planetary carrier 36. At this time, the power transmission route is: input shaft 11

High speed and reverse synchronizer 21

Forward gear synchronizer 22 reverse synchronizer 23

Outer sleeve 14 Big Sun Wheel 31

Long planetary gear 32

Front ring gear 33

Rear gear 38

The third planetary gear 39 Rear planet carrier 37

output shaft 16. At this time, the rotation directions of the input shaft 11 and the output shaft 16 are opposite. The position of the rest of the synchronizers when they are in neutral. In FIG. 7 , thick solid lines indicate power transmission routes.

Please refer to the following table for the calculation formula of the transmission ratio of each gear and the size of the transmission ratio:

In the table:

是前齿圈33齿数与大太阳轮31齿数之比，假设

=2

It is the ratio of the number of teeth of the front ring gear 33 to the number of teeth of the big sun gear 31, assuming

=2

is the ratio of 33 teeth of the front ring gear to 35 teeth of the small sun gear, assuming =2.3

是后齿圈38齿数与第三太阳轮40齿数之比，假设

=2

is the ratio of the 38 teeth of the rear ring gear to the 40 teeth of the third sun gear, assuming

=2

second embodiment

Referring to FIG. 8 , the planetary gear type manual transmission of the present invention includes a Lavigne type double-row planetary gear train 51 and a planetary row 52 . The double-row planetary gear train 51 and the planetary gear train 52 are not arranged on the same axis, the input shaft is connected to the double-row planetary gear train 51, the planetary gear train 52 is connected to the output shaft, and the outer circumference of the front gear ring 33 is provided with front gear teeth 60. The outer circumference of the rear ring gear 38 is provided with rear ring gear teeth 61 , and the front ring gear teeth 60 mesh with the rear ring gear teeth 61 to realize power transmission.

The structure of the double-row planetary gear train 51 is the same as that of the first embodiment. The fifth-speed synchronizer 25 connects the rear ring gear 38 and the third sun gear 40. It is arranged on the same side as the rear brake 26. When the output shaft is on the same side as the input shaft , the fifth-gear synchronizer 25 and the rear brake 26 are arranged on the left side of the third sun gear 40 (as shown in FIG. 8 ). Three sun gears on the right side of 40. the

The shifting operation of each gear is the same as that of the first embodiment, and will not be described again here. Partial, non-inventive changes based on the technical solution of the utility model, or equivalent replacement of some technical features of the technical solution of the utility model, all belong to the protection scope of the utility model. the

Claims (7)

1. A planetary gear type manual transmission, comprising an input shaft, an output shaft, an intermediate shaft arranged between the input shaft and the output shaft, a shaft sleeve, a synchronizer or a brake, and is characterized in that: it also includes a double-row planetary gear The double-row planetary gear system includes a small sun gear, a large sun gear, a short planetary gear, a long planetary gear, a front planetary carrier, and a front ring gear. The short planetary gear and the long planetary gear are provided with front The planet carrier, the small sun gear meshes with the short planet gear, the long planet gear meshes with the large sun gear, the short planet gear and the front ring gear respectively, and the small sun gear is fixedly connected with the large sun gear; the planetary row includes the first Three sun gears, a third planetary gear, a rear planetary carrier, and a rear ring gear, the third planetary gear is arranged on the rear planetary carrier, the third sun gear meshes with the third planetary gear, and the third planetary gear and The rear ring gear meshes. 2. The planetary gear type manual transmission according to claim 1, characterized in that: the output shaft is fixedly connected to the rear planetary carrier, an output shaft sleeve is arranged on the output shaft, and the third sun gear is fixed on the on the output shaft sleeve. 3. The planetary gear type manual transmission according to claim 2, characterized in that: the intermediate shaft is sleeved with an intermediate shaft sleeve and an outer shaft sleeve, the intermediate shaft is fixedly connected with the front planetary carrier, the The small sun gear is fixed on the intermediate shaft sleeve, and the large sun gear is fixed on the outer shaft sleeve. 4. The planetary gear type manual transmission according to claim 3, characterized in that: a high-speed and reverse gear synchronizer is arranged between the input shaft and the intermediate shaft, and the forward gear synchronizer connects the high-speed and reverse gear synchronously. The reverse gear synchronizer is connected with the forward gear synchronizer and the outer shaft sleeve, and the front brake is set between the outer sleeve and the front planetary carrier. The fifth gear synchronizer is connected with the rear ring gear and the third sun gear. A rear brake is also arranged on the third sun wheel. 5. The planetary gear type manual transmission according to claim 4, wherein the front ring gear is fixedly connected to the rear ring gear. 6. The planetary gear type manual transmission according to any one of claims 1 to 4, wherein gear teeth are provided on the outer circumferences of the front ring gear and the rear ring gear, and the front ring gear and the rear ring gear Mesh connection. 7. The planetary gear type manual transmission according to claim 6, wherein the output shaft is arranged on the same side as the input shaft.

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