CN106884938A - Automatic transmission and vehicle - Google Patents

Abstract

The automatic transmission provided by the invention can have six forward gears and one reverse gear by controlling two brakes and three clutches through reasonable layout. Since only two brakes are used by directly fixing the third sun gear on the case, on the one hand, the structure of the automatic transmission is made more compact; of loading conditions. Relatively speaking, reducing the number of brakes and increasing the number of clutches, on the one hand, can make the automatic transmission more compact through nested arrangement, on the other hand, it can also increase the utilization rate of clutches and cut off and shorten the idling transmission route, thereby reducing idling planetary row The drag torque reduces the oil churning loss of the belt row and improves the transmission efficiency.

Description

Automatic transmissions and vehicles

technical field

The invention relates to the field of automatic transmission, in particular to an automatic transmission and a vehicle with the automatic transmission.

Background technique

Automatic transmissions generally include multiple planetary gear sets, brakes and clutches, and multiple planetary gear sets, brakes and clutches are connected together in a certain way. When the torque generated by the engine enters the automatic transmission, the automatic transmission can multi- The torque entering it is changed step by step, and the changed torque is output outward. Generally speaking, the more gears an automatic transmission has, the better the car's power performance and fuel economy. However, as the number of gears increases, the number of planetary gear sets, brakes and clutches will increase, satisfying the theoretical level. The design of the ratio is even more difficult to realize. The major vehicle manufacturers and vehicle research institutes have been looking for an automatic transmission with less planetary gear sets, clutches and brakes that meets the performance requirements of the vehicle, has a more compact structure, and is more efficient. .

At this stage, the six-speed automatic transmissions currently used in the passenger car market mainly include the following types:

1. Aisin, ZF, and Geely (DSI) used the Lape Laijie solution;

2. The scheme used by Hyundai A6MF and A6LF series;

3. The scheme used by the general 6T series;

4. The 6-speed scheme used by Mazda Chuangchi Lantian.

Among them, the Lepe Leger solution is realized by adding a row of planetary gear sets on the basis of the Lavina 4-speed automatic transmission. There is no direct gear, too many components, and a complex structure, which is not conducive to lightweight.

The common and modern schemes are both implemented with three planetary gear sets. The difference lies in the position of the clutches. They both use a combination of two clutches and three brakes to control the realization of each gear. In this automatic transmission, the number of brakes The number of clutches is more than the number of clutches. Since the brake is generally fixed on the box, the increase of the brake increases the difficulty of processing and manufacturing the automatic transmission box, increases the requirements for the strength of the box, and creates a problem for the lightweight design of the box. Difficulty further increases the volume and weight of the automatic transmission.

In the modern mass production series A6MF and A6LF, one planetary gear set uses a double planetary gear structure, which is not conducive to the compactness of the structure and increases the weight and cost compared with the single planetary gear.

The 6-speed scheme used by Chuangchi Lantian is derived from the horizontal layout of the scheme used by the American ALLISON company on large vehicles. It has inherently insufficient characteristics in terms of matching with gasoline engines and in the achievable speed ratio configuration.

Contents of the invention

The object of the present invention is to provide an automatic transmission and a vehicle with the automatic transmission. The automatic transmission can be equipped with six forward gears and one reverse gear by changing the connection modes of planetary gear sets, brakes and clutches. Under the premise of reducing the number of brakes and increasing the number of clutches, the structure of the automatic transmission is more compact and the transmission efficiency is higher.

The present invention provides an automatic transmission, comprising an input shaft, a case body, a first planetary gear set, a second planetary gear set, a third planetary gear set, a first brake, a second brake, a first clutch, a second clutch, a second Three clutches and output shaft;

The first planetary gear set includes a first sun gear, a first planetary gear, a first ring gear and a first planetary carrier, the first planetary gear is rotatably supported on the first planetary carrier, and the The first planetary gear is located between the first sun gear and the first ring gear, and meshes with the first sun gear and the first ring gear;

The second planetary gear set includes a second sun gear, a second planetary gear, a second ring gear and a second planetary carrier, the second planetary gear is rotatably supported on the second planetary carrier, and the The second planetary gear is located between the second sun gear and the second ring gear, and meshes with the second sun gear and the second ring gear;

The third planetary gear set includes a third sun gear, a third planetary gear, a third ring gear and a third planetary carrier, the third planetary gear is rotatably supported on the third planetary carrier, and the The third planetary gear is located between the third sun gear and the third ring gear, and meshes with the third sun gear and the third ring gear;

The input shaft is connected to the second sun gear, the first planet carrier is connected to the second ring gear, and the second planet carrier is connected to the third ring gear through the third clutch, so The first ring gear is connected to the third planet carrier, the third sun gear is connected to the case, and the output shaft is connected to the third planet carrier;

The first sun gear is connected to the casing through the first brake, and the first planet carrier and the second ring gear are connected to the casing through the second brake;

The input shaft is connected to the first sun gear through the first clutch, and the second clutch selectively rotates the second planetary gear set as a whole.

Further, the input end of the input shaft and the output end of the output shaft are respectively arranged on both sides of the first planetary gear set, the second planetary gear set and the third planetary gear set, and the input The power transmission direction of the shaft and the power transmission direction of the output shaft are parallel to each other.

Further, the output shaft is connected to the first ring gear and the third planet carrier, and is located between the first ring gear and the third planet carrier, and the power transmission direction of the input shaft is the same as that of the The power transmission directions of the output shafts are perpendicular to each other, and the input shaft is connected with the second sun gear.

Further, the first planetary gear set, the second planetary gear set and the third planetary gear set are arranged in sequence.

Further, the first brake, the second brake and the first clutch are all located on the side of the first planetary gear set away from the second planetary gear set, and the third clutch is located on the side of the second planetary gear set. Between the second planetary gear set and the third planetary gear set.

Further, the input shaft is connected to the first planetary carrier and the second ring gear through the second clutch, and the second clutch is arranged on the first planetary gear set away from the second planetary gear The side the group is on.

Further, the second clutch is connected between the second planet carrier and the second sun gear, or between the second ring gear and the second planet carrier.

Further, the second clutch is located between the first planetary gear set and the second planetary gear set, or between the second planetary gear set and the third planetary gear set.

Further, when the automatic transmission is in the first gear, the third clutch and the second brake are in the closed state; when the automatic transmission is in the second gear, the third clutch and the first brake are in the closed state. Closed state; when the automatic transmission is in the third gear, the first clutch and the third clutch are in the closed state; when the automatic transmission is in the fourth gear, the second clutch and the third clutch are in the closed state Closed state; when the automatic transmission is in the fifth gear, the first clutch and the second clutch are in the closed state; when the automatic transmission is in the sixth gear, the second clutch and the first brake are in the closed state Closed state: when the automatic transmission is in reverse gear, the first clutch and the second brake are in a closed state.

The present invention also provides a vehicle, which includes the automatic transmission provided by the present invention.

To sum up, the automatic transmission provided by the present invention can have six forward gears and one reverse gear by controlling two brakes and three clutches through reasonable layout. Because two brakes are used and the third sun gear is directly fixed on the box body, the number of brakes used is reduced. On the one hand, the processing and manufacturing of internal teeth on the box body are reduced, which is beneficial to the weight reduction of the box body and makes the whole The automatic transmission is more compact; on the other hand, the utilization rate of the brake is improved, the impact of the brake on the box during the shifting process is reduced, and the load on the box is improved. Simultaneously, using more clutches in the present invention, on the one hand, is beneficial to the nesting design of clutch, makes automatic transmission more compact; Relationship, so that the redundant planetary gear sets do not participate in the rotation, reduce the drag torque, reduce the oil churning loss of the belt row, and improve the transmission efficiency. Furthermore, the setting of more clutches can also benefit the future development of the automatic transmission by adding planetary gear sets or adding more operating elements to make the automatic transmission have more gears.

The above description is only an overview of the technical solution of the present invention. In order to better understand the technical means of the present invention, it can be implemented according to the contents of the description, and in order to make the above and other purposes, features and advantages of the present invention more obvious and understandable , the following preferred embodiments are specifically cited below, and are described in detail as follows in conjunction with the accompanying drawings.

Description of drawings

Fig. 1 is a schematic structural diagram of an automatic transmission provided by a first embodiment of the present invention.

FIG. 2 is a schematic diagram of the transmission line of the automatic transmission shown in FIG. 1 when it is in first gear.

FIG. 3 is a schematic diagram of the transmission line of the automatic transmission shown in FIG. 1 in second gear.

FIG. 4 is a schematic diagram of the transmission route of the automatic transmission shown in FIG. 1 in third gear.

FIG. 5 is a schematic diagram of the transmission line of the automatic transmission shown in FIG. 1 in fourth gear.

FIG. 6 is a schematic diagram of the transmission route of the automatic transmission shown in FIG. 1 in fifth gear.

FIG. 7 is a schematic diagram of the transmission line of the automatic transmission shown in FIG. 1 in sixth gear.

FIG. 8 is a schematic diagram of the transmission line of the automatic transmission shown in FIG. 1 when it is in reverse gear.

Fig. 9 is a schematic structural diagram of the automatic transmission provided by the second embodiment of the present invention.

Fig. 10 is a schematic structural diagram of the automatic transmission provided by the third embodiment of the present invention.

Fig. 11 is a schematic structural diagram of the automatic transmission provided by the fourth embodiment of the present invention.

detailed description

In order to further illustrate the technical means and functions adopted by the present invention to achieve the intended invention purpose, the present invention will be described in detail below in conjunction with the accompanying drawings and preferred embodiments.

The object of the present invention is to provide an automatic transmission and a vehicle with the automatic transmission. The automatic transmission can be equipped with six forward gears and one reverse gear by changing the connection modes of planetary gear sets, brakes and clutches. Under the premise of reducing the number of brakes and increasing the number of clutches, the structure of the automatic transmission is more compact and the transmission efficiency is higher.

Fig. 1 is a schematic structural diagram of an automatic transmission provided by a first embodiment of the present invention. As shown in FIG. 1 , the automatic transmission provided by the first embodiment of the present invention includes an input shaft 11 , a case body 21 , a first planetary gear set 30 , a second planetary gear set 40 , a third planetary gear set 50 , and a first brake 61 , the second brake 62 , the first clutch 71 , the second clutch 72 , the third clutch 73 and the output shaft 12 .

The first planetary gear set 30 includes a first sun gear 31, a first planetary gear 32, a first ring gear 33, and a first planetary carrier 34, and the first planetary gear 32 can be rotatably supported on the first planet by rolling or sliding bearings. The first planetary gear 32 is located between the first sun gear 31 and the first ring gear 33 , and meshes with the first sun gear 31 and the first ring gear 33 .

The second planetary gear set 40 includes a second sun gear 41, a second planetary gear 42, a second ring gear 43, and a second planetary carrier 44. The second planetary gear 42 can be rotatably supported on the second planetary wheel through a rolling or sliding bearing. The second planetary gear 42 is located between the second sun gear 41 and the second ring gear 43 , and meshes with the second sun gear 41 and the second ring gear 43 .

The third planetary gear set 50 includes a third sun gear 51, a third planetary gear 52, a third ring gear 53, and a third planetary carrier 54. The third planetary gear 52 can be rotatably supported on the third planetary gear by rolling or sliding bearings. The third planetary gear 52 is located between the third sun gear 51 and the third ring gear 53 and meshes with the third sun gear 51 and the third ring gear 53 .

The first planet carrier 34 can be directly connected with the second ring gear 43 through splines, welding or integral molding, and the second planet carrier 44 is connected with the third ring gear 53, and the first ring gear 33 can be connected through splines, welding or It is directly connected with the third planetary carrier 54 by way of integral molding or the like. The third sun gear 51 can be directly connected with the casing 21 by means of splines, welding or integral molding, etc., that is, the third sun gear 51 is always a stationary component, and limits one degree of freedom of the third planetary gear set 50, thus eliminating The brakes of the third planetary gear set 50 are restrained.

The input shaft 11 is connected with the second sun gear 41, and the power is directly input into the second sun gear 41; the output shaft 12 is connected with the third planetary carrier 54, and the power input into the automatic transmission is converted by the gear and passed through the third planetary carrier 54 by the third planetary carrier 54. Output shaft 12 outputs.

In this embodiment, the first planetary gear set 30 , the second planetary gear set 40 and the third planetary gear set 50 are arranged in sequence. It should be noted that this layout is only a preferred layout, and in other embodiments, the order of the first planetary gear set 30, the second planetary gear set 40 and the third planetary gear set 50 can also be determined according to the specific layout. The situation changes, but the connection relationship between the elements in each planetary gear set, and the connection relationship between each clutch and each planetary gear set remain unchanged.

The input end of the input shaft 11 and the output end of the output shaft 12 are located on both sides of the first planetary gear set 30, the second planetary gear set 40 and the third planetary gear set 50 respectively, and the power transmission direction of the input shaft 11 is in the same direction as the output shaft 12. The power transmission directions are parallel to each other, that is, the automatic transmission is arranged longitudinally. But in other embodiments, the automatic transmission can also be arranged horizontally according to needs (as shown in Figure 11).

The first sun gear 31 is connected to the casing 21 through the first brake 61, that is, when the first brake 61 is in a closed state, the first sun gear 31 is a stationary component and limits one degree of freedom of the first planetary gear set 30; When the first brake 61 is not closed, the first sun gear 31 can rotate.

The first planet carrier 34 and the second ring gear 43 are connected to the case 21 through the second brake 62, that is, when the second brake 62 is in the closed state, the first planet carrier 34 and the second ring gear 43 are both stationary components, and One degree of freedom of the first planetary gear set 30 and the second planetary gear set 40 is restricted; when the second brake 62 is in an unclosed state, both the first planet carrier 34 and the second ring gear 43 can rotate.

In this embodiment, the first brake 61 and the second brake 62 may be drum brake bands or multi-plate wet brakes.

The input shaft 11 is connected with the first sun gear 31 by the first clutch 71. When the first clutch 71 was in a closed state, power could enter the first sun gear 31 by the input shaft 11; when the first clutch 71 was in an unclosed state, The input shaft 11 is disconnected from the first sun gear 31 .

The input shaft 11 is connected with the first planet carrier 34 and the second ring gear 43 through the second clutch 72, that is, when the second clutch 72 is in the closed state, since the input shaft 11 is respectively connected with the second ring gear 43 and the second sun gear 41 Combination, that is, the second ring gear 43 and the second sun gear 41 are directly connected, and the second planetary gear set 40 moves as a whole; when the first clutch 71 and the second clutch 72 are both in the closed state, the first sun gear 31 is combined with the first planet carrier 34, the second ring gear 43 is combined with the second sun gear 41, and the first planetary gear set 30 and the second planetary gear set 40 move as a whole.

The third clutch 73 is connected between the second planet carrier 44 and the third ring gear 53 , that is, when the third clutch 73 is in an open state, power transmission between the second planet carrier 44 and the third ring gear 53 is interrupted.

In this embodiment, the first clutch 71 , the second clutch 72 and the third clutch 73 may be multi-plate wet clutches or dog clutches.

In this embodiment, the first brake 61 , the second brake 62 , the first clutch 71 and the second clutch 72 are all located on the side of the first planetary gear set 30 away from the second planetary gear set 40 . The third clutch 73 is located between the second planetary gear set 40 and the third planetary gear set 50 to make the structure of the automatic transmission more compact.

The present invention can make the three interconnected planetary gear sets have six forward gears and one reverse gear through the control of two brakes and three clutches. Table 1 shows the state of the brake and clutch in each gear position. What needs to be explained is that when a black solid circle appears in the table, it means that the clutch or brake is in a closed state. When the table is blank, the clutch or brake is not closed.

Table 1: Corresponding relationship between each gear of automatic transmission and each working element

(Wherein C1 represents the first clutch 71, C2 represents the second clutch 72, C3 represents the third clutch 73, B1 represents the first brake 61, B2 represents the second brake 62, k1, k2, k3 are three planetary gear set characteristics parameter, whose value is equal to the ratio of the number of teeth of the ring gear to the sun gear in the planetary gear set)

Fig. 2 is a schematic diagram of the transmission line when the automatic transmission shown in Fig. 1 is in the first gear. As shown in Fig. 2, when the automatic transmission provided by the present invention is in the first gear, the third clutch 73 and the second brake 62 are in closed state, and the The second ring gear 43 is a stationary component at this time, and because the third sun gear 51 is connected with the casing 21, that is, the third sun gear 51 is always a stationary component, so the power is directly transmitted into the second sun gear 41 by the input shaft 11, and The power is transmitted to the third planetary gear set 50 through the second planetary gear set and the third clutch 73 , and the first planetary gear set 30 does not participate in power transmission. The power transmission route of this gear is shown by the thicker black line in Fig. 2 . At this time, the speed ratio is i1=(1+K2)*(1+1/K3). It is worth noting that in this embodiment, in the statement of this gear and the following gears, when it is not mentioned that a certain element is in a closed state, it can be understood that under the control logic of this gear, the Components can be in an unclosed state.

The power transmission route is: input shaft 11→second sun gear 41→second planetary gear 42→second planetary carrier 44→third clutch 73→third ring gear 53→third planetary gear 52→third planetary carrier 54 →Output shaft 12.

Figure 3 is a schematic diagram of the transmission line of the automatic transmission shown in Figure 1 when it is in second gear. When the automatic transmission provided by the present invention is in second gear, the third clutch 73 and the first brake 61 are in a closed state, and the first sun gear 31 is stationary Since the first ring gear 33 is connected to the third planet carrier 54, the first ring gear 33 will rotate together with the third planet carrier 54, and at the same time the first sun gear 31 is a stationary component at this time, and the power passes through the first ring gear 33 enters the first planetary gear set 30, it will be output by the first planet carrier 34, and the first planet carrier 34 and the second ring gear 43 have opposite motion trends, so the first planet carrier 34 and the second ring gear 43 will The second planetary carrier 44 produces a certain propelling effect. In this state, the rotational speed output by the second planetary carrier 44 is higher than the rotational speed output when the second ring gear 43 is in a static state in the first gear, so the second gear can Output higher rpm than first gear. The power transmission route of this gear is shown as the thicker black line in Fig. 3 . In this state, the speed ratio is i2=((1+K1)(1+K2)+K3(1+K1+K2))/(K3(1+K1)).

The power transmission route is: input shaft 11→second sun gear 41→second planetary gear 42→second planetary carrier 44→third clutch 73→third ring gear 53→third planetary gear 52→third planetary carrier 54 → output shaft 12;

At the same time, power can be passed through the input shaft 11→second sun gear 41→second planetary gear 42→second planetary carrier 44→third clutch 73→third ring gear 53→third planetary gear 52→third planetary carrier 54→ The first ring gear 33→the first planetary gear 32→the first planet carrier 34 reaches the second ring gear 43 to provide driving force for the second planet carrier 44 .

Fig. 4 is a schematic diagram of the transmission route of the automatic transmission shown in Fig. 1 when it is in third gear. When the automatic transmission provided by the present invention is in third gear, the first clutch 71 and the third clutch 73 are in a closed state, and the power input by the input shaft 11 is in addition to In addition to entering the second sun gear 41, it can also enter the first sun gear 31 via the first clutch 71. Since the first planet carrier 34 is connected with the second ring gear 43, the first planet carrier 34 will follow the second ring gear 43 At this time, when the first sun gear 31 is used as a driving part to input power to the first planetary gear set 30, the first ring gear 33 can be used as a passive part to output power to the outside. The second gear and the second gear add a power transmission path through the first ring gear 33 to the third planet carrier 54, so it can output a higher speed than the second gear. The power transmission route of this gear is shown by the thicker black line in Figure 4 . In this state, the speed ratio is i3=((1+K1)(1+K2)+K3(1+K1+K2))/(K3(1+K1+K2)).

The power transmission route is: ①, input shaft 11→second sun gear 41→second planetary gear 42→second planetary carrier 44→third clutch 73→third ring gear 53→third planetary gear 52→third planetary gear Frame 54 → output shaft 12;

②. Input shaft 11→first clutch 71→first sun gear 31→first planetary gear 32→first ring gear 33→third planet carrier 54→output shaft 12.

Figure 5 is a schematic diagram of the transmission line of the automatic transmission shown in Figure 1 in fourth gear. When the automatic transmission provided by the present invention is in fourth gear, the second clutch 72 and the third clutch 73 are in a closed state, because the second clutch 72 is in a closed state. state, so the second planetary gear set 40 rotates as a whole, the power transmission route of this gear is shown by the thicker black line in Figure 5, and its speed ratio is i4=(1+K3)/K3.

Its power transmission route is: input shaft 11→second planetary gear set 40→third clutch 73→third ring gear 53→third planetary gear 52→third planet carrier 54→output shaft 12.

Figure 6 is a schematic diagram of the transmission line of the automatic transmission shown in Figure 1 in fifth gear. When the automatic transmission provided by the present invention is in fifth gear, the first clutch 71 and the second clutch 72 are in a closed state, because the second clutch 72 is in a closed state. state, so the second planetary gear set 40 will rotate as a whole, since the first clutch 71 and the second clutch 72 are both in the closed state, the first planetary gear set 30 and the second planetary gear set 40 will rotate as a whole , since the third clutch 73 is not closed, the power transmission path from the second planetary carrier 44 to the third ring gear 53 is cut off, and the power can only be transmitted to the third planetary carrier 54 through the first ring gear 33, so This gear is a direct gear. The power transmission route of this gear is shown as the thicker black line in Fig. 6, and its speed ratio is i5=1. Since the third clutch 73 is not closed, the third planetary gear set 50 does not participate in power transmission, so the drag torque can be reduced, the oil churning loss can be reduced, and the transmission efficiency can be improved.

Its power transmission route is: input shaft 11 →first planetary gear set 30 and second planetary gear set 40 →third planet carrier 54 →output shaft 12 .

Fig. 7 is a schematic diagram of the transmission line of the automatic transmission shown in Fig. 1 when it is in sixth gear. When the automatic transmission provided by the present invention is in sixth gear, the second clutch 72 and the first brake 61 are in a closed state, because the second clutch 72 is in a closed state. state, the second planetary gear set 40 rotates as a whole, since the first brake 61 is in the closed state, the first sun gear 31 is a stationary part, and since the third clutch 73 is not in the closed state, the second planetary carrier 44 to the third The power transmission path of the ring gear 53 is cut off, and the power can only be transmitted to the third planet carrier 54 through the first ring gear 33 . The power transmission route of this gear is shown as a thicker black line in Fig. 7, and its speed ratio is i6=K1/(1+K1). Same as the fifth gear, in this gear, the third planetary gear set 50 does not participate in power transmission, so the drag torque can be reduced, the oil churning loss can be reduced, and the transmission efficiency can be improved.

Its power transmission route is: input shaft 11→second planetary gear set 40→first planetary carrier 34→first planetary gear 32→first ring gear 33→third planetary carrier 54→output shaft 12.

Fig. 8 is a schematic diagram of the transmission line of the automatic transmission shown in Fig. 1 when it is in reverse gear. When the automatic transmission provided by the present invention is in reverse gear, the first clutch 71 and the second brake 62 are in a closed state, because the first clutch 71 is in a closed state. state, power can enter the first sun gear 31 through the first clutch 71, because the second brake 62 is in the closed state, the first planet carrier 34 and the second ring gear 43 are both stationary parts, and because the third clutch 73 is in the open state , the power transmission between the second planet carrier 44 and the third ring gear 53 is also cut off, so neither the second planetary gear set 40 nor the third planetary gear set 50 participates in power transmission. The power transmission route of this gear is shown in the figure Shown in the thicker black line in 8, its speed ratio is iR=-K1.

In the present invention, through reasonable layout, the automatic transmission can have six forward gears and one reverse gear by controlling two brakes and three clutches. Since only two brakes are used by directly fixing the third sun wheel 31 on the case body 21, on the one hand, the structure of the automatic transmission is made more compact; The loading situation of the box body 21 is shown. Relatively speaking, reducing the number of brakes and increasing the number of clutches, on the one hand, can make the automatic transmission more compact through nested arrangement, on the other hand, it can also increase the utilization rate of clutches and disconnect and shorten the idling transmission route, thereby reducing idling planetary row The drag torque reduces the oil churning loss of the belt and improves the transmission efficiency. Furthermore, the setting of more clutches can also benefit the future development of the automatic transmission by adding planetary gear sets or adding more operating elements to make the automatic transmission have more gears.

It can be understood that in the power transmission route of each gear in the present invention, the main function of the second clutch 72 is to selectively make the second planetary gear set rotate as a whole, so the position of the second clutch 72 is not limited to In the situation shown in the first embodiment, it can be located between any two of the second sun gear 41 , the second planet carrier 44 and the second ring gear 43 of the second planetary gear set 40 .

Fig. 9 is a schematic structural diagram of the automatic transmission provided for the second embodiment of the present invention. As shown in Figure 9, the structure and control logic of the automatic transmission provided by this embodiment are basically the same as those of Embodiment 1, the difference is that in this embodiment, the second clutch 72 is arranged between the second planetary carrier 44 and the first Between the two sun gears 41 , that is, one end of the second clutch 72 is connected with the second sun gear 41 and the input shaft 11 , and the other end is connected with the second planet carrier 44 and the third clutch 73 .

Fig. 10 is a schematic structural diagram of the automatic transmission provided by the third embodiment of the present invention. As shown in FIG. 10 , the structure and control logic of the automatic transmission provided by this embodiment are basically the same as that of Embodiment 1, the difference is that in this embodiment, the second clutch 72 is connected to the second planetary carrier 44 and the first Between the two ring gears 43 , that is, one end of the second clutch 72 is connected with the second ring gear 43 and the first planet carrier 34 , and the other end is connected with the second planet carrier 44 and the third clutch 73 .

In the second embodiment and the third embodiment, preferably, the second clutch 72 is located between the second planetary gear set 40 and the third planetary gear set 50 like the third clutch 73, so that the structure of the automatic transmission clutch is more efficient. compact, but can also be arranged between the first planetary gear set 30 and the second planetary gear set 40 .

Fig. 11 is a schematic structural diagram of the automatic transmission provided by the fourth embodiment of the present invention. As shown in FIG. 11 , the schematic structural diagram of the automatic transmission provided in this embodiment is basically the same as the structure in Embodiment 1, the difference is that the output shaft 12 is connected with the first ring gear 33 and the third planetary carrier 54, and It is arranged between the first ring gear 33 and the third planet carrier 54 , and the power transmission direction of the input shaft 11 and the power transmission direction of the output shaft 12 are perpendicular to each other, that is, the automatic transmission is a transverse type.

To sum up, the automatic transmission provided by the present invention can have six forward gears and one reverse gear by controlling two brakes and three clutches through reasonable layout. Since only two brakes are used by directly fixing the third sun gear on the case, on the one hand, the structure of the automatic transmission is made more compact; of loading conditions. Relatively speaking, reducing the number of brakes and increasing the number of clutches, on the one hand, can make the automatic transmission more compact through nested arrangement, on the other hand, it can also increase the utilization rate of clutches and disconnect and shorten the idling transmission route, thereby reducing idling planetary row The drag torque reduces the oil churning loss of the belt row and improves the transmission efficiency. Furthermore, the setting of more clutches can also benefit the future development of the automatic transmission by adding planetary gear sets or adding more operating elements to make the automatic transmission have more gears.

The present invention also provides a vehicle, which includes the above-mentioned automatic transmission. For other structures of the vehicle, reference may be made to the prior art, which will not be repeated here.

The above description is only a preferred embodiment of the present invention, and does not limit the present invention in any form. Although the present invention has been disclosed as above with preferred embodiments, it is not intended to limit the present invention. Anyone familiar with this field Those skilled in the art, without departing from the scope of the technical solution of the present invention, may use the technical content disclosed above to make some changes or modify them into equivalent embodiments with equivalent changes, but as long as they do not depart from the technical solution of the present invention, the Technical Essence Any simple modifications, equivalent changes and modifications made to the above embodiments still fall within the scope of the technical solution of the present invention.

Claims (10)

1. An automatic transmission, characterized in that it includes an input shaft, a casing, a first planetary gear set, a second planetary gear set, a third planetary gear set, a first brake, a second brake, a first clutch, a second Clutch, third clutch and output shaft; The first planetary gear set includes a first sun gear, a first planetary gear, a first ring gear and a first planetary carrier, the first planetary gear is rotatably supported on the first planetary carrier, and the The first planetary gear is located between the first sun gear and the first ring gear, and meshes with the first sun gear and the first ring gear; The second planetary gear set includes a second sun gear, a second planetary gear, a second ring gear and a second planetary carrier, the second planetary gear is rotatably supported on the second planetary carrier, and the The second planetary gear is located between the second sun gear and the second ring gear, and meshes with the second sun gear and the second ring gear; The third planetary gear set includes a third sun gear, a third planetary gear, a third ring gear and a third planetary carrier, the third planetary gear is rotatably supported on the third planetary carrier, and the The third planetary gear is located between the third sun gear and the third ring gear, and meshes with the third sun gear and the third ring gear; The input shaft is connected to the second sun gear, the first planet carrier is connected to the second ring gear, and the second planet carrier is connected to the third ring gear through the third clutch, so The first ring gear is connected to the third planet carrier, the third sun gear is connected to the case, and the output shaft is connected to the third planet carrier; The first sun gear is connected to the casing through the first brake, and the first planet carrier and the second ring gear are connected to the casing through the second brake; The input shaft is connected to the first sun gear through the first clutch, and the second clutch selectively rotates the second planetary gear set as a whole. 2. The automatic transmission according to claim 1, characterized in that: the input end of the input shaft and the output end of the output shaft are respectively arranged on the first planetary gear set, the second planetary gear set and On both sides of the third planetary gear set, the power transmission direction of the input shaft and the power transmission direction of the output shaft are parallel to each other. 3. The automatic transmission according to claim 1, wherein the output shaft is connected to the first ring gear and the third planet carrier, and is located between the first ring gear and the third planet carrier Between, the power transmission direction of the input shaft and the power transmission direction of the output shaft are perpendicular to each other. The input shaft is connected with the second sun gear. 4. The automatic transmission according to claim 1, wherein the first planetary gear set, the second planetary gear set and the third planetary gear set are arranged in sequence. 5. The automatic transmission according to claim 4, characterized in that: the first brake, the second brake and the first clutch are all located in the first planetary gear set away from the second planetary gear set On the side where it is located, the third clutch is located between the second planetary gear set and the third planetary gear set. 6. The automatic transmission according to claim 4, wherein the input shaft is connected with the first planet carrier and the second ring gear through the second clutch, and the second clutch is arranged on the The side where the first planetary gear set is away from the second planetary gear set. 7. The automatic transmission according to claim 4, wherein the second clutch is connected between the second planet carrier and the second sun gear, or connected between the second ring gear and the second sun gear. between the second planet carrier. 8. The automatic transmission according to claim 7, wherein the second clutch is located between the first planetary gear set and the second planetary gear set, or between the second planetary gear set and the second planetary gear set. Between the third planetary gear set. 9. The automatic transmission according to claim 1, characterized in that: when the automatic transmission is in the first gear, the third clutch and the second brake are in a closed state; when the automatic transmission is in the second gear , the third clutch and the first brake are in the closed state; when the automatic transmission is in the third gear, the first clutch and the third clutch are in the closed state; when the automatic transmission is in the fourth gear , the second clutch and the third clutch are in a closed state; when the automatic transmission is in the fifth gear, the first clutch and the second clutch are in a closed state; when the automatic transmission is in the sixth gear , the second clutch and the first brake are in a closed state; when the automatic transmission is in reverse gear, the first clutch and the second brake are in a closed state. 10. A vehicle, characterized by comprising the automatic transmission according to any one of claims 1-9.