A variant CR-CR gear mechanism nine-speed automatic transmission and automobile

Abstract

The present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission and automobile, including an input shaft, an output shaft, a planetary gear row group, a coupling member group and a torque transmission group; the planetary gear row group includes four planetary gear rows installed in sequence from front to back, each planetary gear row includes a sun gear, a planet carrier, planetary gears and a ring gear, and the torque transmission group includes a first brake, a second brake, a third brake, a first clutch, a second clutch and a third clutch. By selectively engaging the first brake, the second brake, the third brake, the first clutch, the second clutch and the third clutch, the sun gear, the planet carrier, the planetary gears and the ring gear are rotated or fixed, thereby establishing nine forward speed ratios and one reverse speed ratio between the input shaft and the output shaft. The present invention has relatively simple control, a more compact structure, a small size, stronger movement stability and a longer service life.

Description

Technical Field

[0001] The present invention relates to the technical field of automobile transmission, and in particular to a variant CR-CR gear mechanism nine-speed automatic transmission and an automobile. Background Art

[0002] The automatic transmission is a core component of automatic transmission vehicles, and its performance directly impacts the vehicle's drivability and safety. The complexity of the automatic transmission's structure and its importance to the vehicle's shifting function have made it a hot topic of research within the automotive industry and academia.

[0003] Generally speaking, the more gears an automatic transmission has, the smoother the shifts, the less shift shock, and the lower fuel consumption. Clearly, multi-speed automatic transmissions will be the future trend, but currently, most automatic transmissions on the market have between four and eight gears, with nine-speed automatic transmissions relatively scarce. Furthermore, existing nine-speed transmissions often utilize multiple (generally four or more) clutches or brakes, making shift control relatively complex.

[0004] In addition, with the development of the automobile industry and people's increasing pursuit of automobile comfort, automatic transmissions, in addition to meeting basic speed shifting requirements, should also meet new requirements such as smaller structural size, larger speed ratio range and stable step ratio, which the existing nine-speed transmissions are difficult to fully meet.

[0005] Therefore, it is very necessary to research and develop a new automatic transmission transmission structure with a more compact structure, a larger transmission ratio range and a more stable step ratio and a high number of gears. Summary of the Invention

[0006] In view of the deficiencies in the prior art, the purpose of the present invention is to provide a variant CR-CR gear mechanism nine-speed automatic transmission and a vehicle, which has a more compact structure, a smaller volume, stronger movement stability and a longer service life.

[0007] In order to solve the above technical problems, the technical solution adopted by the present invention is:

[0008] A variant CR-CR gear mechanism nine-speed automatic transmission includes a transmission housing and an input shaft, an output shaft, a planetary gear set, a coupling member set, and a torque transmission set installed inside the transmission housing;

[0009] a planetary gear row assembly, comprising a first planetary gear row, a second planetary gear row, a third planetary gear row, and a fourth planetary gear row, arranged in sequence from front to back, the first planetary gear row comprising a first ring gear, a first planetary gear, a first planetary carrier, and a first sun gear; the second planetary gear row comprising a second ring gear, a second planetary gear, a second planetary carrier, and a second sun gear; the third planetary gear row comprising a third ring gear, a third planetary gear, a third planetary carrier, and a third sun gear; and the fourth planetary gear row comprising a fourth ring gear, a fourth planetary gear, a fourth planetary carrier, and a fourth sun gear;

[0010] a coupling member group including a first coupling member, a second coupling member, a third coupling member, a fourth coupling member, and a fifth coupling member, wherein the first coupling member interconnects the first ring gear and the second ring gear, the second coupling member interconnects the first planet carrier and the second sun gear, the third coupling member interconnects the second sun gear and the third ring gear, the fourth coupling member interconnects the third planet carrier and the fourth ring gear, and the fifth coupling member interconnects the third sun gear and the fourth sun gear;

[0011] The torque transmission group includes a first brake, a second brake, and a third brake fixed to the transmission housing, and a first clutch, a second clutch, and a third clutch connected to the input shaft, respectively. The first clutch interconnects the input shaft with the first sun gear, and the second clutch interconnects the input shaft with the first ring gear; the third clutch interconnects the input shaft with the third planet carrier, the first brake interconnects the second planet carrier with the transmission housing, the second brake interconnects the second ring gear with the transmission housing, and the third brake interconnects the fourth sun gear with the transmission housing;

[0012] The third brake, the first brake, and the first clutch are engaged to establish a first gear ratio between the input shaft and the output shaft; the third brake, the second brake, and the first clutch are engaged to establish a second gear ratio between the input shaft and the output shaft; the third brake, the first clutch, and the second clutch are engaged to establish a third gear ratio between the input shaft and the output shaft; the third brake, the first clutch, and the third clutch are engaged to establish a fourth gear ratio between the input shaft and the output shaft; the first clutch, the second clutch, and the third clutch are engaged to establish a fifth gear ratio between the input shaft and the output shaft; the first clutch, the second brake, and the third clutch are engaged to establish a sixth gear ratio between the input shaft and the output shaft; the first clutch, the first brake, and the third clutch are engaged to establish a seventh gear ratio between the input shaft and the output shaft; the first brake, the second brake, and the third clutch are engaged to establish an eighth gear ratio between the input shaft and the output shaft; the first brake, the second clutch, and the third clutch are engaged to establish a ninth gear ratio between the input shaft and the output shaft; and reverse gear is established between the input shaft and the output shaft by engaging the first brake, the third brake, and the second clutch.

[0013] Further, the first planetary gear row, the second planetary gear row, the third planetary gear row and the fourth planetary gear row are arranged between the input shaft and the output shaft.

[0014] Further, the distance between the first planetary gear row and the second planetary gear row, the distance between the second planetary gear row and the third planetary gear row, and the distance between the third planetary gear row and the fourth planetary gear row remain consistent.

[0015] Furthermore, the first planetary gear is rotatably supported on the first planetary carrier via a rolling bearing or a sliding bearing, the second planetary gear is rotatably supported on the second planetary carrier via a rolling bearing or a sliding bearing, the third planetary gear is rotatably supported on the third planetary carrier via a rolling bearing or a sliding bearing, and the fourth planetary gear is rotatably supported on the fourth planetary carrier via a rolling bearing or a sliding bearing.

[0016] Furthermore, the K value of the first planetary gear row is K1, the K value of the second planetary gear row is K2, the K value of the third planetary gear row is K3, and the K value of the fourth planetary gear row is K4;

[0017] The transmission ratio of the first gear is (K1K2+K1+K2)(K4+1)(K3+1) / K2K3K4;

[0018] The second gear ratio is (K1+1)(K3+1)(K4+1) / K3K4;

[0019] The third gear ratio is (K3+1)(K4+1) / K3K4;

[0020] The fourth gear ratio is (K4+1) / K4;

[0021] The fifth gear ratio is 1;

[0022] The sixth gear ratio is (K1K2+K1+K2)(K4+1) / (K1K2+K1+K2)(K4+1)+(K2+1)K1K3;

[0023] The seventh gear ratio is 1+[(K1K2+K1+K2)(K4+1) / (K2+1)K1K3];

[0024] The eighth gear ratio is (K4+1) / 1+K3+K4;

[0025] The ninth gear ratio is (K4+1) / 1+K2K3+K3+K4;

[0026] The reverse gear ratio is (K3+1)(K4+1) / K2K3.

[0027] Furthermore, the first clutch, the second clutch and the third clutch are multi-plate wet clutches or dog clutches.

[0028] Furthermore, the first brake, the second brake and the third brake are drum brakes or multi-disc wet brakes.

[0029] Furthermore, the power of the input shaft is provided by an engine.

[0030] A car uses a nine-speed automatic transmission with a CR-CR gear mechanism of any of the above variants.

[0031] Compared with the prior art, the present invention has the following advantages and beneficial effects:

[0032] 1. The present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission and automobile, which utilizes a planetary gear train with four planetary gear rows. Its structural layout is clear, and it also employs a novel structure that connects the internal components of the first three planetary rows (the first row planet carrier, the second row sun gear, and the third row ring gear) as an integral whole. While meeting the requirements for gear number adjustment, it also achieves a more compact structure, a smaller size, enhanced motion stability, and a longer service life.

[0033] 2. The present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission and automobile, which utilizes a combination of single planetary gears and planetary gear rows. The manufacturing process is mature, and each gear position requires only three control elements (clutches or brakes). Shifting between adjacent gear positions requires only the engagement and disengagement of a pair of torque-transmitting components, simplifying control.

[0034] 3. The present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission and automobile, which adopts a compact and reasonable structure and arrangement of four planetary gear rows, and can achieve a relatively large speed ratio range and stable step ratio between gears. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] The accompanying drawings described herein are used to provide a further understanding of the present invention and constitute a part of this application. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the accompanying drawings:

[0036] Figure 1 The present invention is a simplified structural diagram of a variant CR-CR gear mechanism nine-speed automatic transmission.

[0037] Figure 2 This is an equivalent lever diagram corresponding to the structural diagram of a variant CR-CR gear mechanism nine-speed automatic transmission of the present invention.

[0038] Figure 3This is the equivalent lever diagram for first gear.

[0039] Figure 4 This is the equivalent lever diagram for second gear.

[0040] Figure 5 This is the equivalent lever diagram for the third gear.

[0041] Figure 6 This is the equivalent lever diagram for the fourth gear.

[0042] Figure 7 This is the equivalent lever diagram for the fifth gear.

[0043] Figure 8 This is the equivalent lever diagram for the sixth gear.

[0044] Figure 9 This is the equivalent lever diagram for the seventh gear.

[0045] Figure 10 This is the eight-speed equivalent lever diagram.

[0046] Figure 11 This is the equivalent lever diagram for the ninth gear.

[0047] Figure 12 This is the equivalent lever diagram for reverse gear.

[0048] Among them: 1. First planetary gear row; 101, first ring gear; 102, first planet gear; 103, first planet carrier; 104, first sun gear; 2. Second planetary gear row; 201, second ring gear; 202, second planet gear; 203, second planet carrier; 204, second sun gear; 3. Third planetary gear row; 301, third ring gear; 302, third planet gear; 303, third planet carrier; 304, third sun gear; 4. Fourth planetary gear row; 401, fourth ring gear; Ring; 402, fourth planetary gear; 403, fourth planetary carrier; 404, fourth sun gear; 501, first clutch; 502, second clutch; 503, third clutch; 504, first brake; 505, second brake; 506, third brake; 601, first connecting member; 602, second connecting member; 603, third connecting member; 604, fourth connecting member; 605, fifth connecting member; 7, input shaft; 8, output shaft; 9, transmission housing. DETAILED DESCRIPTION

[0049] The technical solutions in the embodiments of the present invention will be described clearly and completely below with reference to the accompanying drawings in the embodiments of the present invention.

[0050] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as limiting the present invention. In addition, the terms "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance or implicitly indicating the number of the indicated technical features. Therefore, features defined as "first", "second", etc. may explicitly or implicitly include one or more of the features. In the description of the present invention, unless otherwise specified, "multiple" means two or more.

[0051] The present invention provides a first planetary gear row 1, a second planetary gear row 2, a third planetary gear row 3 and a fourth planetary gear row 4 as well as three clutches and three brakes installed in sequence, thereby overcoming the problems of the relative lack of existing nine-speed automatic transmissions, or the existing nine-speed transmissions that use four or more clutches or brakes, have relatively complex speed control, are large in size, and are not stable enough.

[0052] The present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission, such as Figure 1 As shown, it includes a transmission housing 9 and an input shaft 7, an output shaft 8, a planetary gear set, a coupling member set and a torque transmission set installed inside the transmission housing 9.

[0053] The planetary gear set includes a first planetary gear row 1, a second planetary gear row 2, a third planetary gear row 3 and a fourth planetary gear row 4, which are installed in sequence from front to back. The first planetary gear row 1 includes a first ring gear 101, a first planetary gear 102, a first planetary carrier 103 and a first sun gear 104. The first sun gear 104 and the first planetary gear 102 are externally meshed for transmission, and the first planetary gear 102 and the first ring gear 101 are internally meshed for transmission. The first planetary gear 102 is rotatably supported on the first planetary carrier 103 through a rolling bearing or a sliding bearing. The second planetary gear row 2 includes a second ring gear 201, a second planetary gear 202, a second planetary carrier 203 and a second sun gear 204. The second sun gear 204 and the second planetary gear 202 are externally meshed for transmission, and the second planetary gear 202 and the ring gear 201 are internally meshed for transmission. 2 is rotatably supported on the second planet carrier 203 via rolling bearings or sliding bearings. The third planetary gear row 3 includes a third ring gear 301, third planetary gears 302, a third planetary carrier 303, and a third sun gear 304. The third sun gear 304 and the third planetary gears 302 are externally meshed, while the third planetary gears 302 and the third ring gear 301 are internally meshed. The third planetary gears 302 are rotatably supported on the third planet carrier 303 via rolling bearings or sliding bearings. The fourth planetary gear row 4 includes a fourth ring gear 401, fourth planetary gears 402, a fourth planetary carrier 403, and a fourth sun gear 404. The fourth sun gear 404 and the fourth planetary gears 402 are externally meshed, while the fourth planetary gears 402 and the fourth ring gear 401 are internally meshed. The fourth planetary gears 402 are rotatably supported on the fourth planet carrier 403 via rolling bearings or sliding bearings.

[0054] The connecting member group includes a first connecting member 601, a second connecting member 602, a third connecting member 603, a fourth connecting member 604, and a fifth connecting member 605. The first connecting member 601 interconnects the first ring gear 101 and the second ring gear 201, the second connecting member 602 interconnects the first planet carrier 103 and the second sun gear 204, the third connecting member 603 interconnects the second sun gear 204 and the third ring gear 301, the fourth connecting member 604 interconnects the third planet carrier 303 and the fourth ring gear 401, and the fifth connecting member 605 interconnects the third sun gear 304 and the fourth sun gear 404.

[0055] The torque transmission group includes a first brake 504, a second brake 505, and a third brake 506 fixed to the transmission housing 9, and a first clutch 501, a second clutch 502, and a third clutch 503 respectively connected to the input shaft 7. The first clutch 501 interconnects the input shaft 7 with the first sun gear 104, and the second clutch 502 interconnects the input shaft 7 with the first ring gear 101; the third clutch 503 interconnects the input shaft 7 with the third planetary carrier 303, the first brake 504 interconnects the second planetary carrier 203 with the transmission housing 9, the second brake 505 interconnects the second ring gear 201 with the transmission housing 9, and the third brake 506 interconnects the fourth sun gear 404 with the transmission housing 9.

[0056] Through the first clutch 501, the power of the input shaft 7 can be transmitted to the first sun gear 104; through the second clutch 502, the power of the input shaft 7 can be transmitted to the first ring gear 101; through the third clutch 503, the power of the output shaft 8 can be transmitted to the third planetary carrier 303, thereby driving the third planetary gear 302 to rotate.

[0057] The first brake 504 can stop the second planetary carrier 203 and thus the second planetary gear 202 from rotating. The second brake 505 can stop the second ring gear 201 from rotating. The third brake 506 can stop the fourth sun gear 404 from rotating.

[0058] The present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission, which uses a planetary gear train with four planetary gear rows. Its structural layout is clear, and it also adopts a novel structural form that connects the internal components of the first three planetary rows (first row planet carrier, second row sun gear, third row ring gear) as an integral whole. While meeting the requirements for gear number adjustment, its structure is more compact, its volume is smaller, and it has stronger movement stability and longer service life.

[0059] The present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission, which adopts the form of a combination of planetary gear rows with single planetary gears. The manufacturing process is mature, and the control of each gear position only requires the combination of three control elements (clutches or brakes). Shifting between adjacent gear positions only requires the replacement of a pair of torque transmission components to engage and disengage, making the control simple.

[0060] The present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission, which adopts a compact and reasonable structure and arrangement of four planetary gear rows, and can achieve a relatively large speed ratio range and stable step ratio between gears.

[0061] like Figure 2As shown, the present invention provides a variant CR-CR gear mechanism nine-speed automatic transmission, and establishes an equivalent lever diagram. In order to facilitate the analysis of the speed ratio of the reducer, the equivalent lever diagram is a common tool for speed reducer performance analysis. It is separately proposed here to illustrate how the speed ratio in the last Table 1 is obtained. Among them, according to the structural characteristics of the variant CR-CR gear mechanism nine-speed automatic transmission of the present invention, the planetary gear row is converted into a lever and three fulcrums, and the three fulcrums represent the planet carrier P, the sun gear S and the ring gear R, respectively. In the first planetary gear row 1, P1 is the first planet carrier 103, S1 is the first sun gear 104, and R1 is the first ring gear 101; in the second planetary gear row 2, P2 is the second planet carrier 203, S2 is the second sun gear 204, and R2 is the second ring gear 201; in the third planetary gear row 3, P3 is the third planet carrier 303, S3 is the third sun gear 304, and R3 is the third ring gear 301; in the fourth planetary gear row 4, P4 is the fourth planet carrier 403, S4 is the fourth sun gear 404, and R4 is the fourth ring gear 401.

[0062] The transmission ratio can be adjusted by setting the K value of the first planetary gear row 1 to K1, the K value of the second planetary gear row 2 to K2, the K value of the third planetary gear row 3 to K3, and the K value of the fourth planetary gear row 4 to K4. The K value represents a characteristic parameter of the planetary gear row, that is, the transmission coefficient among the sun gear, planet gears, and ring gear within the same planetary gear row.

[0063] Specifically, if Figure 2 As shown, the distance from the first ring gear 101 to the first planet carrier 103 is g, and the distance from the first sun gear 104 to the first planet carrier 103 is h, K1 = g / h; the distance from the second ring gear 201 to the second planet carrier 203 is e, and the distance from the second sun gear 204 to the second planet carrier 203 is f, K2 = e / f; the distance from the third ring gear 301 to the third planet carrier 303 is c, and the distance from the third sun gear 304 to the third planet carrier 303 is d, K3 = c / d; the distance from the fourth ring gear 401 to the fourth planet carrier 403 is a, and the distance from the fourth sun gear 404 to the fourth planet carrier 403 is b, K4 = a / b.

[0064] The third brake 506, the first brake 504 and the first clutch 501 are engaged to establish a first gear ratio between the input shaft 7 and the output shaft 8, as shown in FIG. Figure 1 、 Figure 2 and Figure 3As shown, specifically, the first brake 504 and the third brake 506 are engaged to connect the second planet carrier 203 and the fourth sun gear 404 to the transmission housing 9, respectively, preventing the second planet carrier 203 and the fourth sun gear 404 from rotating relative to the transmission housing 9. The first clutch 501 is engaged to connect the input shaft 7 and the first sun gear 104 to rotate together. As a result, a first gear ratio is established between the input shaft 7 and the output shaft 8.

[0065] By engaging the third brake 506, the second brake 505 and the first clutch 501, a second gear ratio is established between the input shaft 7 and the output shaft 8, as shown in FIG. Figure 1 、 Figure 2 and Figure 4 As shown, specifically, the second brake 505 and the third brake 506 are engaged to connect the first sun gear 104 and the fourth sun gear 404 to the transmission housing 9, respectively, preventing the first sun gear 104 and the fourth sun gear 404 from rotating relative to the transmission housing 9. The first clutch 501 is engaged to connect the input shaft 7 and the first ring gear 101 to rotate together. As a result, a second gear ratio is established between the input shaft 7 and the output shaft 8.

[0066] By engaging the third brake 506, the first clutch 501 and the second clutch 502, a third gear ratio is established between the input shaft 7 and the output shaft 8, as shown in FIG. Figure 1 、 Figure 2 and Figure 5 As shown, specifically, the third brake 506 is engaged to connect the fourth sun gear 404 to the transmission housing 9, preventing the fourth sun gear 404 from rotating relative to the transmission housing 9. The first clutch 501 and the second clutch 502 are engaged to connect the input shaft 7 to the first sun gear 104 and the first ring gear 101, respectively, for rotation, thereby establishing a third gear ratio between the input shaft 7 and the output shaft 8.

[0067] By engaging the third brake 506, the first clutch 501 and the third clutch 503, a fourth gear ratio is established between the input shaft 7 and the output shaft 8, as shown in FIG. Figure 1 、 Figure 2 and Figure 6 As shown, specifically, the third brake 506 is engaged to connect the fourth sun gear 404 to the transmission housing 9, preventing the fourth sun gear 404 from rotating relative to the transmission housing 9. The first clutch 501 and the third clutch 503 are engaged to connect the input shaft 7 to the first sun gear 104 and the third planet carrier 303, respectively, to rotate together, thereby establishing a fourth gear transmission ratio between the input shaft 7 and the output shaft 8;

[0068] By engaging the first clutch 501, the second clutch 502 and the third clutch 503, a fifth gear ratio is established between the input shaft 7 and the output shaft 8. Figure 1 、 Figure 2 and Figure 7 As shown, specifically, the first clutch 501, the second clutch 502 and the third clutch 503 are engaged so that the input shaft 7 is connected to the first sun gear 104, the first ring gear 101 and the third planet carrier 303 for rotation, respectively, thereby establishing a fifth gear transmission ratio between the input shaft 7 and the output shaft 8, that is, a direct gear, and the fifth gear transmission ratio is 1.00;

[0069] By engaging the first clutch 501, the second brake 505 and the third clutch 503, a sixth gear ratio is established between the input shaft 7 and the output shaft 8, as shown in FIG. Figure 1 、 Figure 2 and Figure 8 As shown, specifically, the second brake 505 is engaged to connect the second ring gear 201 with the transmission housing 9, preventing the second ring gear 201 from rotating relative to the transmission housing 9. The first clutch 501 and the third clutch 503 are engaged to connect the input shaft 7 with the first sun gear 104 and the third planet carrier 303, respectively, to rotate together, thereby establishing a sixth gear ratio between the input shaft 7 and the output shaft 8;

[0070] By engaging the first clutch 501, the first brake 504 and the third clutch 503, a seventh gear ratio is established between the input shaft 7 and the output shaft 8, as shown in FIG. Figure 1 、 Figure 2 and Figure 9 As shown, specifically, the first brake 504 is engaged to connect the second planet carrier 203 and the transmission housing 9, preventing the second planet carrier 203 from rotating relative to the transmission housing 9. The first clutch 501 and the third clutch 503 are engaged to connect the input shaft 7 to the first sun gear 104 and the third planet carrier 303, respectively, to rotate together, thereby establishing a seventh gear ratio between the input shaft 7 and the output shaft 8;

[0071] By engaging the first brake 504, the second brake 505 and the third clutch 503, an eighth gear ratio is established between the input shaft 7 and the output shaft 8, as shown in FIG. Figure 1 、 Figure 2 and Figure 10As shown, specifically, the first brake 504 and the second brake 505 are engaged to connect the second planet carrier 203 and the second ring gear 201 with the transmission housing 9, thereby preventing the second planet carrier 203 and the second ring gear 201 from rotating relative to the transmission housing 9. The third clutch 503 is engaged to connect the input shaft 7 and the third planet carrier 303 to rotate together, thereby establishing an eighth gear ratio between the input shaft 7 and the output shaft 8;

[0072] By engaging the first brake 504, the second clutch 502 and the third clutch 503, a ninth gear ratio is established between the input shaft 7 and the output shaft 8. Figure 1 、 Figure 2 and Figure 11 As shown, specifically, the first brake 504 is engaged to connect the second planet carrier 203 and the transmission housing 9, preventing the second planet carrier 203 from rotating relative to the transmission housing 9. The second clutch 502 and the third clutch 503 are engaged to connect the input shaft 7 to the first ring gear 101 and the third planet carrier 303, respectively, to rotate together, thereby establishing a ninth gear ratio between the input shaft 7 and the output shaft 8;

[0073] By engaging the first brake 504, the third brake 506 and the second clutch 502, a reverse gear ratio is established between the input shaft 7 and the output shaft 8, as shown in FIG. Figure 1 、 Figure 2 and Figure 12 As shown, the first brake 504 and the third brake 506 are engaged to connect the second planet carrier 203 and the fourth sun gear 404 to the transmission housing 9, respectively, thereby preventing the second planet carrier 203 and the fourth sun gear 404 from rotating relative to the transmission housing 9. The second clutch 502 is engaged to connect the input shaft 7 and the first ring gear 101 to rotate together, thereby establishing a reverse gear ratio between the input shaft 7 and the output shaft 8.

[0074] The transmission ratio of a nine-speed automatic transmission vehicle using a variant CR-CR gear mechanism provided by the present invention is shown in the table below. According to the table below, the specific transmission ratio is adjusted by adjusting the K values ​​of the first planetary gear row 1, the second planetary gear row 2, the third planetary gear row 3, and the fourth planetary gear row 4.

[0075]

[0076] In the present invention, in order to enhance stability, the first planetary gear row 1 , the second planetary gear row 2 , the third planetary gear row 3 and the fourth planetary gear row 4 are disposed between the input shaft 7 and the output shaft 8 .

[0077] In order to further enhance stability, the distance between the first planetary gear row 1 and the second planetary gear row 2, the distance between the second planetary gear row 2 and the third planetary gear row 3, and the distance between the third planetary gear row 3 and the fourth planetary gear row 4 are kept consistent. The planetary gears evenly distributed at equal distances can reduce the possible influence of axial deflection during long-term operation and enhance stability. In addition, combined with the connecting member group, the first connecting member 601 interconnects the first ring gear 101 and the second ring gear 201, the second connecting member 602 interconnects the first planet carrier 103 and the second sun gear 204, the third connecting member 603 interconnects the second sun gear 204 and the third ring gear 301, the fourth connecting member 604 interconnects the third planet carrier 303 and the fourth ring gear 401, and the fifth connecting member 605 interconnects the third sun gear 304 and the fourth sun gear 404. The connecting members of the planetary gear rows make the multiple planetary gear rows form a relatively complete whole, reducing the mutual influence between the planetary rows, thereby enhancing stability.

[0078] In order to ensure smooth movement of the planetary gears, the first planetary gear 102 is rotatably supported on the first planetary carrier 103 through rolling bearings or sliding bearings, the second planetary gear 202 is rotatably supported on the second planetary carrier 203 through rolling bearings or sliding bearings, the third planetary gear 302 is rotatably supported on the third planetary carrier 303 through rolling bearings or sliding bearings, and the fourth planetary gear 402 is rotatably supported on the fourth planetary carrier 403 through rolling bearings or sliding bearings.

[0079] In the present invention, the first clutch 501 , the second clutch 502 and the third clutch 503 are multi-plate wet clutches or dog clutches.

[0080] In the present invention, the first brake 504 , the second brake 505 and the third brake 506 are drum brakes or multi-disc wet brakes.

[0081] In the present invention, the power of the input shaft 7 is provided by the engine.

[0082] The present invention also provides a car using any one of the variant CR-CR gear mechanisms of the nine-speed automatic transmission.

[0083] In this document, directional terms such as front, back, top, and bottom are defined based on the positions of components in the accompanying drawings and relative to each other, and are intended only for clarity and convenience in describing the technical solution. It should be understood that the use of these directional terms should not limit the scope of protection claimed in this application.

[0084] In the absence of conflict, the above embodiments and features in the embodiments may be combined with each other.

[0085] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A variant CR-CR gear mechanism nine-speed automatic transmission, characterized by: It includes a transmission housing and an input shaft, an output shaft, a planetary gear set, a coupling member set and a torque transmission set installed inside the transmission housing; a planetary gear row assembly, comprising a first planetary gear row, a second planetary gear row, a third planetary gear row, and a fourth planetary gear row, arranged in sequence from front to back, the first planetary gear row comprising a first ring gear, a first planetary gear, a first planetary carrier, and a first sun gear; the second planetary gear row comprising a second ring gear, a second planetary gear, a second planetary carrier, and a second sun gear; the third planetary gear row comprising a third ring gear, a third planetary gear, a third planetary carrier, and a third sun gear; and the fourth planetary gear row comprising a fourth ring gear, a fourth planetary gear, a fourth planetary carrier, and a fourth sun gear; a coupling member group including a first coupling member, a second coupling member, a third coupling member, a fourth coupling member, and a fifth coupling member, wherein the first coupling member interconnects the first ring gear and the second ring gear, the second coupling member interconnects the first planet carrier and the second sun gear, the third coupling member interconnects the second sun gear and the third ring gear, the fourth coupling member interconnects the third planet carrier and the fourth ring gear, and the fifth coupling member interconnects the third sun gear and the fourth sun gear; The torque transmission group includes a first brake, a second brake, and a third brake fixed to the transmission housing, and a first clutch, a second clutch, and a third clutch connected to the input shaft, respectively. The first clutch interconnects the input shaft with the first sun gear, and the second clutch interconnects the input shaft with the first ring gear; the third clutch interconnects the input shaft with the third planet carrier, the first brake interconnects the second planet carrier with the transmission housing, the second brake interconnects the second ring gear with the transmission housing, and the third brake interconnects the fourth sun gear with the transmission housing; Engaging the third brake, the first brake, and the first clutch establishes a first gear ratio between the input shaft and the output shaft; engaging the third brake, the second brake, and the first clutch establishes a second gear ratio between the input shaft and the output shaft; engaging the third brake, the first clutch, and the second clutch establishes a third gear ratio between the input shaft and the output shaft; engaging the third brake, the first clutch, and the third clutch establishes a fourth gear ratio between the input shaft and the output shaft; engaging the first clutch, the second clutch, and the third clutch establishes a fifth gear ratio between the input shaft and the output shaft; engaging the first clutch, the second brake, and the third clutch establishes a sixth gear ratio between the input shaft and the output shaft; engaging the first clutch, the first brake, and the third clutch establishes a seventh gear ratio between the input shaft and the output shaft; engaging the first brake, the second brake, and the third clutch establishes an eighth gear ratio between the input shaft and the output shaft; engaging the first brake, the second clutch, and the third clutch establishes a ninth gear ratio between the input shaft and the output shaft; and engaging the first brake, the third brake, and the second clutch establishes a reverse gear between the input shaft and the output shaft. The K value of the first planetary gear row is K1, the K value of the second planetary gear row is K2, the K value of the third planetary gear row is K3, and the K value of the fourth planetary gear row is K4; The transmission ratio of the first gear is (K1K2+K1+K2)(K4+1)(K3+1) / K2K3K4; The second gear ratio is (K1+1)(K3+1)(K4+1) / K3K4; The third gear ratio is (K3+1)(K4+1) / K3K4; The fourth gear ratio is (K4+1) / K4; The fifth gear ratio is 1.

2. The variant CR-CR gear mechanism nine-speed automatic transmission according to claim 1, characterized in that: The first planetary gear row, the second planetary gear row, the third planetary gear row, and the fourth planetary gear row are sequentially disposed between the input shaft and the output shaft.

3. The variant CR-CR gear mechanism nine-speed automatic transmission according to claim 1, characterized in that: The distance between the first planetary gear row and the second planetary gear row, the distance between the second planetary gear row and the third planetary gear row, and the distance between the third planetary gear row and the fourth planetary gear row are kept consistent.

4. The variant CR-CR gear mechanism nine-speed automatic transmission according to claim 1, characterized in that: The first planetary gear is rotatably supported on the first planetary carrier via a rolling bearing or a sliding bearing, the second planetary gear is rotatably supported on the second planetary carrier via a rolling bearing or a sliding bearing, the third planetary gear is rotatably supported on the third planetary carrier via a rolling bearing or a sliding bearing, and the fourth planetary gear is rotatably supported on the fourth planetary carrier via a rolling bearing or a sliding bearing.

5. The variant CR-CR gear mechanism nine-speed automatic transmission according to claim 1, characterized in that: The first clutch, the second clutch, and the third clutch are multi-plate wet clutches or dog clutches.

6. The variant CR-CR gear mechanism nine-speed automatic transmission according to claim 1, characterized in that: The first brake, the second brake, and the third brake are drum brakes or multi-disc wet brakes.

7. The variant CR-CR gear mechanism nine-speed automatic transmission according to claim 1, characterized in that: The power of the input shaft is provided by the engine.

8. An automobile, characterized in that: A nine-speed automatic transmission using the variant CR-CR gear mechanism according to any one of claims 1 to 7.

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