A thirteen-speed planetary gear transmission

Abstract

The present invention provides a thirteen-speed planetary gear transmission. The transmission comprises four planetary gear rows arranged sequentially from the input shaft to the output shaft. A clutch in the torque transfer device connects the input shaft and the planetary gear train, while a brake in the torque transfer device connects the transmission housing and the planetary gear train. Two combinations of each clutch and brake selectively engage to establish thirteen forward speed ratios and one reverse speed ratio between the input and output shafts. The transmission utilizes a single planetary gear planetary gear row transmission. The four planetary gear rows are simple, compact, and compact, utilizing a common Simpson coupling mechanism with other planetary gear rows, resulting in a mature manufacturing process. Seven torque transfer components (clutches or brakes) are employed, reducing the transmission's control difficulty and size. Controlling each gear position requires only two torque transfer components, and shifting between adjacent gear positions requires only the engagement and disengagement of a pair of torque transfer components, simplifying control.

Description

Technical Field

[0001] The present invention belongs to the technical field of vehicle transmission, and in particular relates to a thirteen-speed planetary gear transmission. Background Art

[0002] Automatic transmissions have gradually replaced manual transmissions in the automotive market and are widely used in modern vehicles. As one of the most complex automotive assemblies, the design of automatic transmission shifting mechanisms has always been a hot topic in the international scientific community. Currently, most automatic transmissions on the market have gears between 4 and 9, with only a few high-end vehicles using 10 or more. Generally speaking, the more gears an automatic transmission has, the denser the gear ratios, resulting in less jerkiness during shifting, smoother acceleration, and relatively lower fuel consumption. Therefore, automatic transmissions that can achieve more gears with fewer planetary gears and fewer clutch elements will be the future development trend of automatic transmissions.

[0003] The planetary gear transmission with the highest number of gears currently available for mass production on the market is the 10-speed planetary gear transmission, which mainly includes Toyota's AWR10L65 series and the GM / Ford jointly developed 10R80 series.

[0004] Currently, there are several types of planetary gear transmission mechanisms in the invention patents for automatic transmissions using planetary gear mechanisms for high gears.

[0005] Shaanxi Fast Gear Co., Ltd.'s patent CN202010953345.4: An eleven-speed transmission based on a planetary gear system. This invention uses a four-row planetary gear system composed of a Simpson mechanism and two other planetary gears, combined with four brakes, two clutches, and a slip clutch to obtain eleven forward gears and two reverse gears. However, this invention requires the engagement of three coupling elements in each gear position, making the transmission shift control relatively complex. Tongji University's patent CN201410256053.X: An eleven-speed transmission. This invention uses four single-planetary gear planetary gears, combined with two brakes and four clutches, to obtain eleven forward gears and one reverse gear. Only two coupling elements need to be engaged in each gear position.

[0006] Planetary transmissions utilize a planetary gear train, clutch, and brake system to achieve multiple gear ratios. As automobiles become increasingly popular, the demand for automatic transmissions with a high number of gears is also increasing. Therefore, research and development of new transmission structures with high numbers of gears is essential. Summary of the Invention

[0007] The purpose of the present invention is to provide a thirteen-speed planetary gear transmission to address the above-mentioned deficiencies in the prior art.

[0008] To achieve the above object, the present invention adopts the following technical solutions:

[0009] The present invention provides a thirteen-speed planetary gear transmission, comprising a transmission housing, an input shaft, an output shaft, a planetary gear set, and a torque transmission device installed inside the transmission housing, wherein the planetary gear set comprises a first planetary gear set, a second planetary gear set, a third planetary gear set, and a fourth planetary gear set installed in sequence from the input shaft to the output shaft.

[0010] The first planetary gear row consists of a first sun gear, a first planet carrier, first planet gears and a first ring gear. The first sun gear and the first planet gears are externally meshed for transmission, the first planet gears and the first ring gears are internally meshed for transmission, and the first planet gears are rotatably supported on the first planet carrier.

[0011] The second planetary gear row consists of a second sun gear, a second planet carrier, second planet gears and a second ring gear. The second sun gear and the second planet gears are externally meshed for transmission, the second planet gears and the second ring gears are internally meshed for transmission, and the second planet gears are rotatably supported on the second planet carrier.

[0012] The third planetary gear row consists of a third sun gear, a third planet carrier, a third planet gear and a third ring gear. The third sun gear and the third planet gear are externally meshed for transmission, the third planet gear and the third ring gear are internally meshed for transmission, and the third planet gear is rotatably supported on the third planet carrier.

[0013] The fourth planetary gear row consists of a fourth sun gear, a fourth planet carrier, a fourth planet gear and a fourth ring gear. The fourth sun gear and the fourth planet gear are externally meshed for transmission, the fourth planet gear and the fourth ring gear are internally meshed for transmission, and the fourth planet gear is rotatably supported on the fourth planet carrier.

[0014] The first ring gear is fixedly connected to the transmission housing, the first sun gear is fixedly connected to the input shaft, the second planet carrier is fixedly connected to the third ring gear, the second ring gear is fixedly connected to the third planet carrier, the third planet carrier is fixedly connected to the fourth ring gear, and the third sun gear is fixedly connected to the fourth sun gear;

[0015] The torque transmitting device comprises:

[0016] a first clutch connecting the first planet carrier with the second planet carrier;

[0017] a second clutch connecting the first planet carrier and the second sun gear;

[0018] a third clutch connecting the first planet carrier and the second ring gear;

[0019] a fourth clutch connecting the input shaft to the third planet carrier;

[0020] a fifth clutch connecting the input shaft with the third sun gear;

[0021] a first brake connected to the third ring gear;

[0022] a second brake connected to the fourth sun gear;

[0023] Two combinations of the first clutch, the second clutch, the third clutch, the fourth clutch, the fifth clutch, the first brake, and the second brake are selectively engaged to establish thirteen forward speed ratios and one reverse speed ratio between the input shaft and the output shaft.

[0024] Furthermore, the input shaft is fixedly connected to the first sun gear, the output shaft is connected to the fourth planet carrier, the first planet carrier is connected to the second planet carrier through the first clutch, the first planet carrier is connected to the second sun gear through the second clutch, the first planet carrier is connected to the second ring gear through the third clutch, the input shaft is connected to the third planet carrier through the fourth clutch, and the input shaft is connected to the third sun gear through the fifth clutch.

[0025] Furthermore, the transmission housing is connected to the third ring gear through the first brake, and the transmission housing is connected to the fourth sun gear through the second brake.

[0026] Furthermore, the thirteen-speed planetary gear transmission has thirteen gear ratios of nine reduction gears, one direct gear and three overdrive gears.

[0027] Further, engaging the second clutch and the second brake to establish a first gear ratio between the input shaft and the output shaft;

[0028] establishing a second gear ratio between the input shaft and the output shaft by engaging the first clutch and the second brake;

[0029] establishing a third gear ratio between the input shaft and the output shaft by engaging the third clutch and the second brake;

[0030] establishing a fourth gear ratio between the input shaft and the output shaft by engaging the first clutch and the third clutch;

[0031] establishing a fifth gear ratio between the input shaft and the output shaft by engaging the third clutch and the first brake;

[0032] establishing a sixth gear ratio between the input shaft and the output shaft by engaging the third clutch and the fifth clutch;

[0033] establishing a seventh gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the first brake;

[0034] establishing an eighth gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the first clutch;

[0035] establishing a ninth gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the second clutch;

[0036] establishing a tenth gear ratio between the input shaft and the output shaft by engaging the fifth clutch and the fourth clutch;

[0037] establishing an eleventh gear ratio between the input shaft and the output shaft by engaging the second clutch and the fourth clutch;

[0038] establishing a twelfth gear ratio between the input shaft and the output shaft by engaging the first clutch and the fourth clutch;

[0039] A thirteenth gear ratio is established between the input shaft and the output shaft by engaging the first brake and the fourth clutch.

[0040] Furthermore, a reverse gear ratio is established between the input shaft and the output shaft by engaging the first brake and the second clutch.

[0041] Furthermore, the first clutch, the second clutch, the third clutch, the fourth clutch and the fifth clutch are all multi-plate wet clutches or dog clutches.

[0042] Furthermore, the first brake and the second brake are both multi-disc wet brakes or drum brakes.

[0043] Furthermore, the first brake and the second brake are both fixed on the transmission housing.

[0044] Compared with the prior art, the technical solution provided by the present invention has the following beneficial effects:

[0045] (1) The thirteen-speed planetary gear transmission provided by the present invention includes four planetary gear rows arranged in sequence from the input shaft to the output shaft; the clutch in the torque transmission device connects the input shaft and the planetary gear train, and the brake in the torque transmission device connects the transmission housing and the planetary gear train. Two combinations of each clutch and each brake are selectively engaged to establish thirteen forward speed ratios and one reverse speed ratio between the input shaft and the output shaft. The transmission ratios of the various gears are 11.67, 7.37, 4.84, 3.85, 2.76, 2.43, 2.09, 1.63, 1.32, 1.0, 0.90, 0.77, 0.72, and -4.69, respectively. The overdrive step ratio is small, and the gear shifting is more stable when driving at high speed.

[0046] (2) The thirteen-speed planetary gear transmission provided by the present invention adopts a single planetary gear planetary gear transmission. The four planetary gear rows have a simple and compact structure and a small size. The commonly used Simpson gear is combined with other planetary gear rows, and the manufacturing process is mature.

[0047] (3) The thirteen-speed planetary gear transmission provided by the present invention has a small number of torque transmission components, namely seven torque transmission components, which reduces the control difficulty and corresponding volume of the transmission to a certain extent;

[0048] (4) The control of each gear of the thirteen-speed planetary gear transmission provided by the present invention only requires the combination of two torque transmission components (clutches or brakes), and when changing between adjacent gears, only the engagement and disconnection of a pair of torque transmission components need to be replaced, which makes the control simple. BRIEF DESCRIPTION OF THE DRAWINGS

[0049] Figure 1 is a schematic diagram of a thirteen-speed planetary gear transmission of the present invention;

[0050] Figure 2 This is an operational logic diagram of the thirteen-speed planetary gear transmission of the present invention.

[0051] In the figure: 1. input shaft; 2. output shaft; 3. transmission housing; 11. first ring gear; 12. first planetary gear; 13. first planetary carrier; 14. first sun gear; 21. second ring gear; 22. second planetary gear; 23. second planetary carrier; 24. second sun gear; 31. third ring gear; 32. third planetary gear; 33. third planetary carrier; 34. third sun gear; 41. fourth ring gear; 42. fourth planetary gear; 43. fourth planetary carrier; 44. fourth sun gear; C1. first clutch; C2. second clutch; C3. third clutch; C4. fourth clutch; C5. fifth clutch; B1. first brake; B2. second brake. DETAILED DESCRIPTION

[0052] To make the objectives, technical solutions, and advantages of the present invention more apparent, embodiments of the present invention will be further described below with reference to the accompanying drawings. The following describes a preferred embodiment of the present invention among multiple possible embodiments, which is intended to provide a basic understanding of the present invention but is not intended to identify the key or decisive elements of the present invention or to limit the scope of protection.

[0053] In the description of the present invention, it should be noted that, unless otherwise expressly specified or limited, the terms "mounted" and "connected" should be understood broadly. For example, they may refer to fixed connections, detachable connections, or integral connections; mechanical connections, electrical connections, direct connections, indirect connections through an intermediary, and internal connections between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention.

[0054] Please refer to Figure 1 An embodiment of the present invention provides a thirteen-speed planetary gear transmission, including a transmission housing 3, and an input shaft 1, an output shaft 2, a planetary gear set and a torque transmission device installed inside the transmission housing 3.

[0055] The planetary gear set includes the first planetary gear set, the second planetary gear set, the third planetary gear set and the fourth planetary gear set installed in sequence from the input shaft 1 to the output shaft 2:

[0056] The first planetary gear row consists of a first sun gear 14, a first planet carrier 13, a first planetary gear 12 and a first ring gear 11. The first sun gear 14 and the first planetary gear 12 are externally meshed for transmission, the first planetary gear 12 and the first ring gear 11 are internally meshed for transmission, and the first planetary gear 12 is rotatably supported on the first planet carrier 13 via rolling or sliding bearings.

[0057] The second planetary gear row consists of a second ring gear 21, second planetary gears 22, a second planetary carrier 23 and a second sun gear 24. The second sun gear 24 and the second planetary gears 22 are externally meshed for transmission, and the second planetary gears 22 are internally meshed for transmission with the second ring gear 21. The second planetary gears 22 are rotatably supported on the second planetary carrier 23 via rolling or sliding bearings.

[0058] The third planetary gear row consists of a third ring gear 31, third planetary gears 32, a third planet carrier 33 and a third sun gear 34. The third sun gear 34 and the third planetary gears 32 are externally meshed for transmission, while the third planetary gears 32 and the third ring gear 31 are internally meshed for transmission. The third planetary gears 32 are rotatably supported on the third planet carrier 33 via rolling or sliding bearings.

[0059] The fourth planetary gear row consists of a fourth ring gear 41, fourth planetary gears 42, a fourth planet carrier 43 and a fourth sun gear 44. The fourth sun gear 44 and the fourth planetary gears 42 are externally meshed for transmission, and the fourth planetary gears 42 and the fourth ring gear 41 are internally meshed for transmission. The fourth planetary gears 42 are rotatably supported on the fourth planet carrier 43 via rolling or sliding bearings.

[0060] Among them, the first ring gear 11 is fixedly connected to the transmission housing 3, the first sun gear 14 is fixedly connected to the input shaft 1, the second planetary carrier 23 is fixedly connected to the third ring gear 31, the second ring gear 21 is fixedly connected to the third planetary carrier 33, the third planetary carrier 33 is fixedly connected to the fourth ring gear 41, and the third sun gear 34 is fixedly connected to the fourth sun gear 44.

[0061] The torque transmission device includes five clutches and two brakes: a first clutch C1, a second clutch C2, a third clutch C3, a fourth clutch C4, and a fifth clutch C5; and a first brake B1 and a second brake B2.

[0062] The first clutch C1 connects the first planet carrier 13 with the second planet carrier 23;

[0063] a second clutch C2 connecting the first planet carrier 13 to the second sun gear 24;

[0064] a third clutch C3 connecting the first planet carrier 13 with the second ring gear 21;

[0065] a fourth clutch C4 connecting the input shaft 1 to the third planet carrier 33;

[0066] a fifth clutch C5 , which connects the input shaft 1 to the third sun gear 34 ;

[0067] a first brake B1 connected to the third ring gear 31;

[0068] a second brake B2 connected to the fourth sun gear 44;

[0069] Two combinations of the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4, the fifth clutch C5, the first brake B1 and the second brake B1 are selectively engaged to establish thirteen forward speed ratios and one reverse speed ratio between the input shaft 1 and the output shaft 2.

[0070] In this embodiment, the input shaft 1 is fixedly connected to the first sun gear 14, the output shaft 2 is connected to the fourth planetary carrier 43, the first planetary carrier 13 is connected to the second planetary carrier 23 via the first clutch C1, the first planetary carrier 13 is connected to the second sun gear 24 via the second clutch C2, the first planetary carrier 13 is connected to the second ring gear 21 via the third clutch C3, the input shaft 1 is connected to the third planetary carrier 33 via the fourth clutch C4, and the input shaft 1 is connected to the third sun gear 34 via the fifth clutch C5.

[0071] In this embodiment, the five clutches and two brakes in the transmission are structurally characterized as follows: the first clutch C1 is connected to the second planetary carrier 23 and the third ring gear 31; the second clutch C2 is connected to the second sun gear 24; the third clutch C3 is connected to the second ring gear 21; the fourth clutch C4 is connected to the third planetary carrier 33; and the fifth clutch C5 is connected to the third sun gear 34 and the fourth sun gear 44. The first brake B1 is connected to the second planetary carrier 23 and the third ring gear 31, respectively; and the second brake B2 is connected to the third sun gear 34 and the fourth sun gear 44.

[0072] Input shaft 1 can be directly connected to the fourth clutch C4 and the fifth clutch C5; both clutches C4 and C5 can serve as input members. In the transmission mechanism, input shaft 1 is directly connected to the first sun gear 14, so power is continuously input to the first sun gear 14 throughout the transmission. Input shaft 1 is connected to the engine via a torque converter, and the engine power is transmitted to the input shaft via the torque converter.

[0073] The output shaft 2 is connected to the drive wheels of a vehicle (automobile, special vehicle, construction machinery) through a differential, and transmits the output power to the drive wheels of the vehicle.

[0074] In this embodiment, the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4 and the fifth clutch C5 are all wet multi-plate clutches or dog clutches. When the active plate and the driven plate of the clutch are compressed under the action of hydraulic pressure, the clutch is engaged and is in a working state. At this time, the movable components connected to the two ends of the clutch are engaged and have the same speed; conversely, when the clutch is in a non-working state, the movable components connected to the two ends of the clutch are separated and have different speeds.

[0075] In this embodiment, the first brake B1 and the second brake B2 are both wet multi-plate brakes or drum brakes, which are used to connect the movable member and the transmission housing. When the brake is in working state, the movable member is engaged with the transmission housing, the movable member cannot rotate, and is in a braking state.

[0076] The thirteen forward gears of the present invention are nine reduction gears, one direct gear and three overdrive gears, as follows:

[0077] By engaging the second clutch C2 and the second brake B2, a first gear ratio is established between the input shaft 1 and the output shaft 2;

[0078] By engaging the first clutch C1 and the second brake B2, a second gear ratio is established between the input shaft 1 and the output shaft 2;

[0079] By engaging the third clutch C3 and the second brake B2, a third gear ratio is established between the input shaft 1 and the output shaft 2;

[0080] By engaging the first clutch C1 and the third clutch C3, a fourth gear ratio is established between the input shaft 1 and the output shaft 2;

[0081] By engaging the third clutch C3 and the first brake B1, a fifth gear ratio is established between the input shaft 1 and the output shaft 2;

[0082] By engaging the third clutch C3 and the fifth clutch C5, a sixth gear ratio is established between the input shaft 1 and the output shaft 2;

[0083] By engaging the fifth clutch C5 and the first brake B1, a seventh gear ratio is established between the input shaft 1 and the output shaft 2;

[0084] By engaging the fifth clutch C5 and the first clutch C1, an eighth gear ratio is established between the input shaft 1 and the output shaft 2;

[0085] By engaging the fifth clutch C5 and the second clutch C2, a ninth gear ratio is established between the input shaft 1 and the output shaft 2;

[0086] By engaging the fifth clutch C5 and the fourth clutch C4, a tenth gear ratio is established between the input shaft 1 and the output shaft 2;

[0087] By engaging the second clutch C2 and the fourth clutch C4, an eleventh gear ratio is established between the input shaft 1 and the output shaft 2;

[0088] By engaging the first clutch C1 and the fourth clutch C4, a twelfth gear ratio is established between the input shaft 1 and the output shaft 2;

[0089] By engaging the first brake B1 and the fourth clutch C4 , a thirteenth gear ratio is established between the input shaft 1 and the output shaft 2 .

[0090] The transmission of the present invention can also achieve a reverse gear by engaging the first brake B1 and the second clutch C2 to establish a reverse gear ratio between the input shaft and the output shaft.

[0091] The transmission ratio of a planetary gear transmission is the ratio of the rotational speeds of the input and output members. The planetary gear transmission of the present invention can achieve 14 different transmission ratios, or 14 gear positions, including 13 forward gears and one reverse gear. Each gear position is achieved by controlling the operating states of the clutch and brake.

[0092] refer to Figure 1 And such as Figure 2 The operation logic table shown in Figure 2 Note that these numbers are merely illustrative and can be adjusted within a certain range. The speed ratio refers to the ratio of input speed to output speed, and the planetary gear K value refers to the ratio of the number of teeth on the planetary gear ring to the number of teeth on the sun gear. In this embodiment, K1 = -2.8462, K2 = -1.6957, K3 = -1.9091, and K4 = -3.875. The specific implementation of the transmission ratios for each gear is as follows:

[0093] The second clutch C2 and the second brake B2 are engaged to establish a first gear ratio between the input shaft 1 and the output shaft 2. Specifically, the second brake B2 is engaged to connect the fourth sun gear 44 to the transmission housing 3, preventing the fourth sun gear 44 from rotating relative to the transmission housing 3. The second clutch C2 is engaged to connect the first planet carrier 13 and the second sun gear 24 to rotate together. Thus, a first gear ratio of 11.67 is established between the input shaft 1 and the output shaft 2.

[0094] The first clutch C1 and the second brake B2 are engaged to establish a second gear ratio between the input shaft 1 and the output shaft 2. Specifically, the second brake B2 is engaged to connect the fourth sun gear 44 to the transmission housing 3, preventing the fourth sun gear 44 from rotating relative to the transmission housing 3. The first clutch C1 is engaged to connect the first planet carrier 13 and the second planet carrier 23 to rotate together. Thus, a second gear ratio of 7.37 is established between the input shaft 1 and the output shaft 2, with a speed step of 1.58.

[0095] The third clutch C3 and second brake B2 are engaged to establish a third gear ratio between the input shaft 1 and the output shaft 2. Specifically, the second brake B2 is engaged to connect the fourth sun gear 44 to the transmission housing 3, preventing the fourth sun gear 44 from rotating relative to the transmission housing 3. The third clutch C3 is engaged to connect the first planet carrier 13 and the second ring gear 21 for joint rotation. Thus, a third gear ratio of 4.84 is established between the input shaft 1 and the output shaft 2, with a speed step of 1.52.

[0096] By engaging the third clutch C3 and the first clutch C1, a fourth gear ratio is established between the input shaft 1 and the output shaft 2. Specifically, the first clutch C1 is engaged, coupling the first planetary carrier 13 and the second planetary carrier 23 for joint rotation. The third clutch C3 is engaged, coupling the first planetary carrier 13 and the second ring gear 21 for joint rotation. This establishes a fourth gear ratio of 3.85 between the input shaft 1 and the output shaft 2, with a speed step of 1.26.

[0097] The third clutch C3 and the first brake B1 are engaged to establish a fifth-speed gear ratio between the input shaft 1 and the output shaft 2. Specifically, the first brake B1 is engaged to connect the second planetary carrier 23 to the transmission housing 3, preventing the second planetary carrier 23 from rotating relative to the transmission housing 3. The third clutch C3 is engaged to connect the first planetary carrier 13 and the second ring gear 21 for joint rotation. This establishes a fifth-speed gear ratio of 2.76 between the input shaft 1 and the output shaft 2, with a speed step of 1.39.

[0098] By engaging the third clutch C3 and the fifth clutch C5, a sixth gear ratio is established between the input shaft 1 and the output shaft 2. Specifically, the fifth clutch C5 is engaged, connecting the input shaft 1 and the third sun gear 34 for joint rotation. The third clutch C3 is engaged, connecting the first planet carrier 13 and the second ring gear 21 for joint rotation. Thus, a sixth gear ratio of 2.43 is established between the input shaft 1 and the output shaft 2, with a speed step of 1.14.

[0099] The fifth clutch C5 and the first brake B1 are engaged to establish a seventh-speed gear ratio between the input shaft 1 and the output shaft 2. Specifically, the first brake B1 is engaged to connect the second planetary carrier 23 to the transmission housing 3, preventing the second planetary carrier 23 from rotating relative to the transmission housing 3. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 34 for joint rotation. Consequently, a seventh-speed gear ratio of 2.09 is established between the input shaft 1 and the output shaft 2, with a speed step of 1.16.

[0100] By engaging the fifth clutch C5 and the first clutch C1, an eighth-speed gear ratio is established between the input shaft 1 and the output shaft 2. Specifically, the first clutch C1 is engaged to connect the first planetary carrier 13 and the second planetary carrier 23 for rotation. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 34 for rotation. Thus, an eighth-speed gear ratio of 1.63 is established between the input shaft (1) and the output shaft (2), with a speed step of 1.28.

[0101] The fifth clutch C5 and the second clutch C2 are engaged to establish a ninth gear ratio between the input shaft 1 and the output shaft 2. Specifically, the second clutch C2 is engaged to connect the first planet carrier 13 and the second sun gear 24 for joint rotation. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 34 for joint rotation. This establishes a ninth gear ratio between the input shaft 1 and the output shaft 2, with a ninth gear ratio of 1.32 and a speed step of 1.23.

[0102] The fifth clutch C5 and the fourth clutch C4 are engaged to establish a tenth-speed gear ratio between the input shaft 1 and the output shaft 2. Specifically, the fourth clutch C4 is engaged to connect the input shaft 1 and the third planetary carrier 33 for joint rotation. The fifth clutch C5 is engaged to connect the input shaft 1 and the third sun gear 34 for joint rotation. Thus, a tenth-speed gear ratio of 1.0 is established between the input shaft 1 and the output shaft 2, with a speed step of 1.32.

[0103] The second clutch C2 and the fourth clutch C4 are engaged to establish an eleventh-speed gear ratio between the input shaft 1 and the output shaft 2. Specifically, the fourth clutch C4 is engaged to connect the input shaft 1 and the third planetary carrier 33 for joint rotation. The second clutch C2 is engaged to connect the first planetary carrier 13 and the second sun gear 24 for joint rotation. This establishes an eleventh-speed gear ratio between the input shaft 1 and the output shaft 2, with a gear ratio of 0.90 and a speed step of 1.11.

[0104] By engaging the first clutch C1 and the fourth clutch C4, a twelfth-speed gear ratio is established between the input shaft 1 and the output shaft 2. Specifically, the fourth clutch C4 is engaged, coupling the input shaft 1 and the third planetary carrier 33 for joint rotation. The first clutch C1 is engaged, coupling the first planetary carrier 13 and the second planetary carrier 23 for joint rotation. This establishes a twelfth-speed gear ratio of 0.77 between the input shaft 1 and the output shaft 2, with a speed step of 1.16.

[0105] By engaging the first brake B1 and the fourth clutch C4, a thirteenth-speed gear ratio is established between the input shaft 1 and the output shaft 2. Specifically, the fourth clutch C4 is engaged, coupling the input shaft 1 and the third planetary carrier 33 for joint rotation. The first brake B1 is engaged, coupling the second planetary carrier 23 to the transmission housing 3, preventing the second planetary carrier 23 from rotating relative to the transmission housing 3. Thus, a thirteenth-speed gear ratio of 0.72 is established between the input shaft 1 and the output shaft 2, with a speed step of 1.08.

[0106] A reverse gear ratio is established between the input shaft 1 and the output shaft 2 by engaging the first brake B1 and the second clutch C2. Specifically, the second clutch C2 is engaged, coupling the first planet carrier 13 and the second sun gear 24 for joint rotation. The first brake B1 is engaged, coupling the second planet carrier 23 to the transmission housing 3, preventing the second planet carrier 23 from rotating relative to the transmission housing 3. Consequently, a reverse gear ratio of 4.69 is established between the input shaft 1 and the output shaft 2.

[0107] In this embodiment, the first clutch C1, the second clutch C2, the third clutch C3, the fourth clutch C4, and the fifth clutch C5 are multi-plate wet clutches or dog clutches, and the first brake B1 and the second brake B2 are drum brakes or multi-plate wet brakes.

[0108] The present invention simplifies the control of the clutch and brake working states. When each gear is switched, only two control elements are required, which reduces the control difficulty of the transmission. The step ratio between gears is stable, and the gear shifting is smooth.

[0109] In the absence of conflict, the above embodiments and features in the embodiments may be combined with each other.

[0110] 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 thirteen-speed planetary gear transmission, comprising a transmission housing and an input shaft, an output shaft, a planetary gear set, and a torque transmission device installed inside the transmission housing, wherein the planetary gear set comprises a first planetary gear set, a second planetary gear set, a third planetary gear set, and a fourth planetary gear set installed in sequence along the direction from the input shaft (1) to the output shaft (2), and is characterized in that: The first planetary gear row is composed of a first sun gear (14), a first planet carrier (13), a first planet gear (12) and a first ring gear (11); the first sun gear (14) and the first planet gear (12) are externally meshed for transmission, the first planet gear (12) and the first ring gear (11) are internally meshed for transmission, and the first planet gear (12) is rotatably supported on the first planet carrier (13); The second planetary gear row consists of a second sun gear (24), a second planetary carrier (23), a second planetary gear (22) and a second ring gear (21); the second sun gear (24) and the second planetary gear (22) are externally meshed for transmission, the second planetary gear (22) and the second ring gear (21) are internally meshed for transmission, and the second planetary gear (22) is rotatably supported on the second planetary carrier (23); The third planetary gear row is composed of a third sun gear (34), a third planetary carrier (33), a third planetary gear (32) and a third ring gear (31); the third sun gear (34) and the third planetary gear (32) are externally meshed for transmission, the third planetary gear (32) and the third ring gear (31) are internally meshed for transmission, and the third planetary gear (32) is rotatably supported on the third planetary carrier (33); The fourth planetary gear row is composed of a fourth sun gear (44), a fourth planetary carrier (43), a fourth planetary gear (42) and a fourth ring gear (41); the fourth sun gear (44) and the fourth planetary gear (42) are externally meshed for transmission, the fourth planetary gear (42) and the fourth ring gear (41) are internally meshed for transmission, and the fourth planetary gear (42) is rotatably supported on the fourth planetary carrier (43); The first ring gear (11) is fixedly connected to the transmission housing (3), the first sun gear (14) is fixedly connected to the input shaft (1), the second planet carrier (23) is fixedly connected to the third ring gear (31), the second ring gear (21) is fixedly connected to the third planet carrier (33), the third planet carrier (33) is fixedly connected to the fourth ring gear (41), and the third sun gear (34) is fixedly connected to the fourth sun gear (44); The torque transmitting device comprises: a first clutch (C1) connecting the first planet carrier (13) and the second planet carrier (23); a second clutch (C2) connecting the first planet carrier (13) and the second sun gear (24); a third clutch (C3) connecting the first planet carrier (13) and the second ring gear (21); a fourth clutch (C4) connecting the input shaft (1) with the third planet carrier (33); a fifth clutch (C5) connecting the input shaft (1) with the third sun gear (34); a first brake (B1) connected to the third ring gear (31); a second brake (B2) connected to the fourth sun gear (44); Two combinations of the first clutch (C1), the second clutch (C2), the third clutch (C3), the fourth clutch (C4), the fifth clutch (C5), the first brake (B1) and the second brake (B2) are selectively engaged to establish thirteen forward speed ratios and one reverse speed ratio between the input shaft and the output shaft.

2. The thirteen-speed planetary gear transmission according to claim 1, characterized in that: The input shaft (1) is fixedly connected to the first sun gear (14), the output shaft (2) is connected to the fourth planet carrier (43), the first planet carrier (13) is connected to the second planet carrier (23) through the first clutch (C1), the first planet carrier (13) is connected to the second sun gear (24) through the second clutch (C2), the first planet carrier (13) is connected to the second ring gear (21) through the third clutch (C3), the input shaft (1) is connected to the third planet carrier (33) through the fourth clutch (C4), and the input shaft (1) is connected to the third sun gear (34) through the fifth clutch (C5).

3. The thirteen-speed planetary gear transmission according to claim 2, characterized in that: The transmission housing (3) is connected to the third ring gear (31) via the first brake (B1), and the transmission housing (3) is connected to the fourth sun gear (44) via the second brake (B2).

4. The thirteen-speed planetary gear transmission according to claim 3, characterized in that: The thirteen-speed planetary gear transmission has thirteen gear ratios, namely, nine reduction gears, one direct gear and three overdrive gears.

5. The thirteen-speed planetary gear transmission according to claim 4, characterized in that: establishing a first gear ratio between the input shaft (1) and the output shaft (2) by engaging the second clutch (C2) and the second brake (B2); establishing a second gear ratio between the input shaft (1) and the output shaft (2) by engaging the first clutch (C1) and the second brake (B2); By engaging the third clutch (C3) and the second brake (B2), a third gear ratio is established between the input shaft (1) and the output shaft (2); By engaging the first clutch (C1) and the third clutch (C3), a fourth gear ratio is established between the input shaft (1) and the output shaft (2); establishing a fifth gear ratio between the input shaft (1) and the output shaft (2) by engaging the third clutch (C3) and the first brake (B1); By engaging the third clutch (C3) and the fifth clutch (C5), a sixth gear ratio is established between the input shaft (1) and the output shaft (2); By engaging the fifth clutch (C5) and the first brake (B1), a seventh gear ratio is established between the input shaft (1) and the output shaft (2); By engaging the fifth clutch (C5) and the first clutch (C1), an eighth gear ratio is established between the input shaft (1) and the output shaft (2); By engaging the fifth clutch (C5) and the second clutch (C2), a ninth gear ratio is established between the input shaft (1) and the output shaft (2); By engaging the fifth clutch (C5) and the fourth clutch (C4), a tenth gear ratio is established between the input shaft (1) and the output shaft (2); By engaging the second clutch (C2) and the fourth clutch (C4), an eleventh gear ratio is established between the input shaft (1) and the output shaft (2); By engaging the first clutch (C1) and the fourth clutch (C4), a twelfth gear ratio is established between the input shaft (1) and the output shaft (2); By engaging the first brake (B1) and the fourth clutch (C4), a thirteenth gear ratio is established between the input shaft (1) and the output shaft (2).

6. The thirteen-speed planetary gear transmission according to claim 5, characterized in that: A reverse gear ratio is established between the input shaft (1) and the output shaft (2) by engaging the first brake (B1) and the second clutch (C2).

7. The thirteen-speed planetary gear transmission according to claim 1, characterized in that: The first clutch (C1), the second clutch (C2), the third clutch (C3), the fourth clutch (C4) and the fifth clutch (C5) are all multi-plate wet clutches or dog clutches.

8. The thirteen-speed planetary gear transmission according to claim 1, wherein: The first brake (B1) and the second brake (B2) are both multi-disc wet brakes or drum brakes.

9. The thirteen-speed planetary gear transmission according to claim 1, wherein: The first brake (B1) and the second brake (B2) are both fixed on the transmission housing (3).

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