Speed ​​change device and speed change module

Abstract

The present invention provides a transmission module, which has a transmission frame, including a torque input end, a transmission unit and a torque output end. In the transmission unit, a planet carrier is rotatably arranged on the transmission frame, and a sun gear group includes more than two input sun gears and more than one output sun gear. Each sun gear in the sun gear group is coaxially arranged with the planet carrier and can rotate relative to each other. Each planetary gear assembly includes an input planetary gear respectively meshed with the input sun gear, and an output planetary gear respectively meshed with the output sun gear. The input planetary gear and the output planetary gear are coaxially fixedly connected, and the planetary gear assembly is rotatably arranged on the planet carrier. At least one input sun gear is configured with a brake, and each input sun gear is respectively connected to the torque input end through a clutch, and the planet carrier is also configured with a brake. The present invention also provides a transmission device including the above-mentioned transmission module. The above-mentioned transmission module can provide more speed ratios.

Description

Technical Field

[0001] The present invention relates to a speed change module and also to a speed change device comprising the speed change module. Background Art

[0002] In practical applications, there are two types of gear transmissions: fixed-axis transmission and planetary gear transmission, in which the planetary mechanism has a ring gear. For example, the manual transmission (MT) and dual-clutch automatic transmission (DCT) used in vehicles belong to the fixed-axis transmission, while the torque converter automatic transmission (AT) used in vehicles mostly belongs to the planetary gear transmission with a ring gear.

[0003] In the inventor's previous patents, Chinese invention patent CN102155521B discloses a planetary gear mechanism and a mechanical transmission including the planetary gear mechanism, Chinese invention patent CN106594192A discloses a modular combination transmission, and Chinese invention patent CN108286591A discloses a single-input three-speed powertrain system.

[0004] On this basis, the inventors continued to study and found that the common characteristics of the above-mentioned three speed change devices are: a speed change module has only one input sun gear; a speed change module has only one output sun gear; a planetary gear assembly includes two planetary gears connected together and rotating coaxially and synchronously; a speed change module provides at most three speed ratios; if more gears are to be achieved, multiple speed change modules need to be connected in series, which will result in a larger axial dimension; the speed change module has no gear ring, and the gear meshing method is all external meshing gears; there are both fixed-axis and planetary gear transmission modes: when the retaining frame (or planetary frame) is fixed, the above-mentioned three speed change devices are fixed-axis transmission, and when the input or output center sun gear is fixed, the above-mentioned three speed change devices are planetary gear transmission. Therefore, the transmission mode of this type of speed change device represented by the above-mentioned three speed change devices is a hybrid transmission mode; the structure is simple, the manufacturing is easy, the cost is low, and the cost performance is high.

[0005] The inventor hopes to provide an improved planetary gear mechanism, which can continue to retain the advantages of the planetary gear mechanism in the aforementioned patent, such as no ring gear, simple structure and easy manufacturing, and provide more speed ratios on the basis of continuing to adopt a unique hybrid transmission mode (combining fixed-axis transmission and planetary gear transmission). Summary of the invention

[0006] The object of the present invention is to provide a speed change module which can provide more speed ratios.

[0007] The present invention provides a speed change module, which has a transmission frame, including a torque input end, a transmission unit and a torque output end, wherein the torque of the torque input end is transmitted to the torque output end via the transmission unit, and the transmission unit includes a planet carrier, a sun gear set and at least one planetary gear assembly. The planet carrier is rotatably arranged on the transmission frame. The sun gear set includes m input sun gears and k output sun gears, and each sun gear in the sun gear set is coaxially arranged with the planet carrier and can rotate relative to each other, wherein m≥2, k≥1. Each planetary gear assembly includes m input planetary gears respectively meshed with the m input sun gears, and k output planetary gears respectively meshed with the k output sun gears, wherein the input planetary gears and the output planetary gears are coaxially fixedly connected, and the planetary gear assembly is rotatably arranged on the planet carrier. At least one input sun gear is provided with a brake, and each input sun gear is respectively connected to the torque input end by a clutch, and the planet carrier is also provided with a brake. The transmission module is configured to select two elements from m+1 elements consisting of m input sun gears and planet carriers, so that the clutch of one of the two elements is in an engaged state and the brake of the other element is in a braking state, or so that the clutches of the two elements are in an engaged state, thereby forming a power transmission route of the transmission module.

[0008] In one embodiment, the planet carrier is further detachably connected to the torque input end via a clutch.

[0009] In one embodiment, each input sun gear is equipped with a brake.

[0010] In one embodiment, the torque input end includes a torque input shaft, and each clutch includes an inner hub and an outer drum that can be connected in a clutchable manner; the torque input shaft and at least some of the m input sun gears are respectively connected to one and the other of the inner hub and the outer drum of the corresponding clutch.

[0011] In one embodiment, at least some of the m input sun gears are connected to a first transfer gear, and the first transfer gear is meshed with the second transfer gear for transmission. The torque input end includes a torque input shaft, and the torque input shaft is provided with an input transfer gear, and the input transfer gear is meshed with the third transfer gear for transmission. A clutch is provided between the second transfer gear and the third transfer gear, and at least some of the input sun gears are connected to the torque input shaft in a clutchable manner through the first transfer gear, the second transfer gear, the clutch, the third transfer gear and the input transfer gear in sequence.

[0012] In one embodiment, the speed change module includes more than two planetary gear assemblies, and the more than two planetary gear assemblies are evenly distributed along the circumferential direction of the sun gear set.

[0013] In one embodiment, at least some of the sun gears in the sun gear set are held coaxially by a pair of tubes that fit into each other and are rotatable relative to each other.

[0014] In one embodiment, the transmission frame includes a front shaft hole and a rear shaft hole that are coaxial and arranged side by side; the planetary carrier is rotatably supported between the front shaft hole and the rear shaft hole, the torque input end is located on the front side of the front shaft hole, and the torque output end is located on the rear side of the rear shaft hole.

[0015] In one embodiment, the brakes of at least some of the m input sun gears are located at the rear side of the rear axle hole.

[0016] The present invention further provides a speed change device, comprising the above-mentioned two or more speed change modules, wherein the torque output end of a preceding speed change module among the two or more speed change modules is transmission-connected with the torque input end of a succeeding speed change module.

[0017] The above-mentioned speed change module provides an improved planetary gear mechanism, wherein the planetary gear mechanism has the advantages of no ring gear, simple structure and easy manufacturing, and can provide many speed ratios based on the unique hybrid transmission mode (combining fixed-axis transmission and planetary gear transmission).

[0018] In the transmission module of the present invention, a transmission module has at least two input sun gears; a transmission module is not limited to having only one output sun gear, but can have more than two output sun gears; and a planetary gear assembly includes at least three planetary gears. A transmission module of the present invention can produce at least four speed ratios and provide the possibility of producing more speed ratios. For a transmission with the same number of speed ratios, the transmission module required by the present invention is significantly reduced, with a smaller volume, lighter weight, and lower cost. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The above and other features, properties and advantages of the present invention will become more apparent through the following description in conjunction with the accompanying drawings and embodiments, in which:

[0020] Figure 1 It is a schematic diagram of a four-speed transmission module having two input sun gears and one output sun gear.

[0021] Figure 2 It is a schematic diagram of a five-speed transmission module having two input sun gears and one output sun gear.

[0022] Figure 3 It is composed of two Figure 1 Schematic diagram of a speed change device formed by connecting speed change modules in series.

[0023] Figure 4 Is Figure 3 The speed module and Figure 1Schematic diagram of a speed change device formed by connecting speed change modules in series.

[0024] Figure 5 It is a schematic diagram of a seven-speed transmission module having two input sun gears and one output sun gear.

[0025] Figure 6 is another schematic diagram of the arrangement of a seven-speed transmission module having two input sun gears and one output sun gear.

[0026] Figure 7 It is a schematic diagram of the principle of a thirteen-speed transmission module with three input sun gears and one output sun gear.

[0027] Figure 8 It is another schematic diagram of the arrangement of a thirteen-speed transmission module with three input sun gears and one output sun gear.

[0028] Fig. 9 It is a schematic diagram of the principle of a thirteen-speed transmission module with two input sun gears and two output sun gears.

[0029] Fig.10 It is a schematic diagram of the principle of a twenty-five-speed transmission module with three input sun gears and two output sun gears. DETAILED DESCRIPTION

[0030] The present invention is further described below in conjunction with specific implementation methods and accompanying drawings. More details are elaborated in the following description to facilitate a full understanding of the present invention. However, the present invention can obviously be implemented in a variety of other ways different from this description. Those skilled in the art can make similar generalizations and deductions based on actual application situations without violating the connotation of the present invention. Therefore, the scope of protection of the present invention should not be limited by the content of this specific implementation method.

[0031] For example, a first feature subsequently described in the specification is formed above or on a second feature, and may include an implementation in which the first and second features are formed by direct connection, and may also include an implementation in which an additional feature is formed between the first and second features, so that the first and second features may not be directly connected. Further, when a first element is described in a manner connected or combined with a second element, the description includes implementations in which the first and second elements are directly connected or combined with each other, and also includes the use of one or more other intervening elements to indirectly connect or combine the first and second elements. In addition, the expressions "more than N", "not less than N" or "at least N" in the text all include N itself, for example, "more than two" includes "two" itself.

[0032] First Embodiment (m=2, k=1)

[0033] See also Figure 1, Figure 1 The speed change module 10 according to the first embodiment is shown. The speed change module 10 has a transmission frame BOX. The transmission frame BOX may be a transmission case that supports a planet carrier 9, a torque input shaft S0, etc., which will be described later.

[0034] The speed change module 10 includes a torque input terminal IP, a transmission unit 20 and a torque output terminal OP. The torque at the torque input terminal IP is transmitted to the torque output terminal OP via the transmission unit 20 .

[0035] The transmission unit 20 includes a planet carrier 9 , a sun gear set 30 and at least one planetary gear assembly 8 .

[0036] The planet carrier 9 is rotatably disposed on the transmission frame BOX. Figure 1 In the transmission frame BOX, the transmission frame BOX includes a coaxial line ( Figure 1 The planet carrier 9 is rotatably supported between the front shaft hole H1 and the rear shaft hole H2, for example, by a rotating bearing. The torque input end IP is located at the front side of the front shaft hole H1, and the torque output end OP is located at the rear side of the rear shaft hole H2. For the convenience of description, Figure 1 And the front-to-back directions are shown in subsequent figures.

[0037] The sun gear set 30 includes m input sun gears (eg, Figure 1 ) and k output sun gears, where m≥2, k≥1. Figure 1 In the above formula, m=2, k=1, the m input sun gears are input sun gears 1 and 2, and the k output sun gears are output sun gear 7. Each sun gear in the sun gear set 30 (including input sun gears 1 and 2 and output sun gear 7) is coaxial with the planet carrier 9 ( Figure 1 In other words, the k output sun gears are rotatable relative to each other (if k>1), the m input sun gears are rotatable relative to each other, and the output sun gears and the input sun gears are rotatable relative to each other.

[0038] Each planetary gear assembly 8 includes m input planetary gears (eg, Figure 1 The input planetary gears 81, 82) and k output planetary gears (such as Figure 1 The output planetary gear 87 in the embodiment). The m input planetary gears are meshed with the m input sun gears respectively. For example, Figure 1 In the embodiment, the input planetary gear 81 meshes with the input sun gear 1, and the input planetary gear 82 meshes with the input sun gear 2. The k output planetary gears mesh with the k output sun gears respectively. For example, Figure 1In the embodiment, the output planetary gear 87 meshes with the output sun gear 7. The number of planetary gears included in each planetary gear assembly 8 is the sum of the number of input sun gears and output sun gears, that is, the number of input sun gears m+the number of output sun gears k.

[0039] The input planetary gears 81, 82 and the output planetary gear 87 are coaxially connected. Figure 1 The transmission module 10 may include more than two (eg, two, three, four or more) planetary gear assemblies 8, which are evenly distributed along the circumferential direction of the sun gear set 30. Figure 1 In the embodiment, the transmission module 10 includes two planetary gear assemblies 8, and the two planetary gear assemblies 8 are evenly distributed at 180° relative to the rotation axis X0 of the input sun gear 1, 2 or the output sun gear 7. Alternatively, the planetary gear assemblies 8 are arranged circumferentially relative to the rotation axis X0 of the planet carrier 9, for example, they can be evenly distributed circumferentially relative to the rotation axis X0 of the planet carrier 9.

[0040] Among the m input sun gears, at least one input sun gear is equipped with a brake Bx. Figure 1 Bx in the subsequent figures represents a brake, and x can be any positive integer such as 1, 2, 3 or 9. The planet carrier 9 is also equipped with a brake B9. Figure 1 In the middle, it is located closest to the torque input terminal IP ( Figure 1 The input sun gear 2 at the front side is provided with a brake B2. Figure 1 , the brake Bx can be divided into a rotatable part BR and a non-rotatable part BS. Taking the brake B2 as an example, the non-rotatable part BS of the brake B2 can be directly or indirectly connected to the transmission frame Box, and the rotatable part BR of the brake B2 is directly or indirectly connected to the input sun gear 2. When the brake Bx is in a braking state (or stated as, the brake Bx is engaged), the corresponding input sun gear 2 or planetary carrier 9 equipped with the brake Bx is prevented from rotating, and when the brake Bx is not started (or stated as, the brake Bx is disengaged), the corresponding input sun gear 2 or planetary carrier 9 equipped with the brake Bx is allowed to rotate.

[0041] Furthermore, each of the input sun gears 1 and 2 (that is, each of the m input sun gears) is detachably connected to the torque input port IP via a clutch Cx. Figure 1 And Cx in the subsequent figures represents a clutch, and x can be any positive integer such as 1, 2, 3 or 9. Figure 1 In the middle, it is located closest to the torque input terminal IP ( Figure 1 The input sun gear 2 at the front side is provided with a brake B2. Figure 1The clutch Cx can be divided into an active part CA and a driven part CI. Taking the clutch C2 as an example, the active part CA of the clutch C2 is directly or indirectly connected to the torque input terminal IP, and the driven part CI of the clutch C2 is directly or indirectly connected to the input sun gear 2. In other embodiments below, the planet carrier 9 can also be configured with a clutch C9. In other words, the planet carrier 9 is also connected to the torque input terminal IP through the clutch C9. When the clutch Cx is in an engaged state (or expressed as, the clutch Cx is engaged), the torque is transmitted from the torque input terminal IP to the corresponding input sun gear 1, 2 or the planet carrier 9 configured with the clutch Cx, and when the clutch Cx is not started (or expressed as, the clutch Cx is disengaged), the torque transmission to the corresponding input sun gear 2 or the planet carrier 9 configured with the brake Bx is interrupted. The clutch Cx and the brake Bx can constitute a shift actuator. The clutch Cx can be, for example, a multi-plate wet clutch, and the brake B2 can, for example, adopt a structure similar to that of the clutch Cx.

[0042] The speed change module 10 is configured to receive m+1 ( Figure 1 In the embodiment, two elements are selected from the three elements so that the clutch Cx of one of the two elements is in an engaged state and the brake Bx of the other element is in a braking state, or the clutches Cx of the two elements are in an engaged state, thereby forming a power transmission route of the speed change module.

[0043] Figure 1 In the embodiment, the torque input end IP includes a torque input shaft S0. Each clutch Cx includes an inner hub and an outer drum that can be connected in a clutchable manner. Taking the clutch C2 using a multi-plate wet clutch as an example, the active part CA of the clutch C2 includes an inner hub with an external spline ( Figure 1 The clutch C2 is composed of a tube S01, and also includes a first friction element with an internal spline, which can be connected to the inner hub S01 by the cooperation of the internal spline and the external spline; the driven part CI of the clutch C2 includes an outer drum with an internal spline ( Figure 1 The inner hub S01 and the outer drum 21 are in the form of a coaxial pair of tubes, and the first friction element with internal splines and the second friction element with external splines are arranged between the inner hub S01 and the outer drum 21. The friction elements are pressed to fit each other to transmit torque. In this way, the inner hub S01 and the outer drum 21 of the clutch C2 can be connected in a clutchable manner.

[0044] The input sun gears 1 and 2 and the torque input shaft S0 are connected to one or the other of the inner hub and the outer drum of the corresponding clutch, that is, for one clutch, the input sun gear may be connected to the inner hub of the clutch and the torque input shaft S0 may be connected to the outer drum of the clutch, or the input sun gear may be connected to the inner hub of the clutch and the torque input shaft S0 may be connected to the inner hub of the clutch. In this way, the input sun gears 1 and 2 are detachably connected to the torque input shaft S0 through the clutches C1 and C2. Figure 1 In the embodiment, a clutch C1 is provided between the input sun gear 1 and the torque input shaft S0. Figure 1 In the embodiment, the torque input shaft S0 has a tubular shaft or tube S01 along the rotation axis X0, the tube S01 is connected to or constitutes the outer drum of the clutch C1, and the input sun gear 1 has a tube 11 extending along the rotation axis X0, the tube 11 is connected to or constitutes the inner hub of the clutch C1, and the clutch C1 is composed of the tube S01 of the torque input shaft S0 and the tube 11 of the input sun gear 1, and the tube S01 is externally mounted on the tube 11. For the clutch C1, the input sun gear 1 is connected to the inner hub of the clutch C1, and the torque input shaft S0 is connected to the outer drum of the clutch C1. Similarly, as Figure 1 As shown, a clutch C2 is provided between the input sun gear 2 and the torque input shaft S0. In the clutch C2, the tube 21 of the input sun gear 2 is outermostly fitted on the tube S01 of the torque input shaft S0. The tube 21 is connected to or constitutes the outer drum of the clutch C2, and the tube S01 is connected to or constitutes the inner hub of the clutch C2. For the clutch C2, the input sun gear 2 is connected to the outer drum of the clutch C2, and the torque input shaft S0 is connected to the inner hub of the clutch C1. It should be understood that the tube constituting the inner hub or outer drum of the clutch is not limited to a hollow tube. For example, the tube 11 may not be a hollow tube as shown in FIG. Figure 1 The hollow cylinder shown may instead be a solid shaft.

[0045] Figure 1In the sun gear set 30, the input sun gear 1 and the input sun gear 2 are kept coaxial (rotation axis X0) by the mutually fitting tube pair S12 and can rotate relative to each other. The input sun gear 1 has a tube 12 in the shape of a solid shaft extending along the rotation axis X0, and the input sun gear 2 has a tube 22 extending along the rotation axis X0. The tube 22 of the input sun gear 2 is fitted onto the tube 12 of the input sun gear 1. For example, a rotary bearing can also be provided between the tube 22 and the tube 12. In this way, the input sun gear 1 and the input sun gear 2 are kept coaxial and can rotate relative to each other. The input sun gear 1 and the output sun gear 3 are also kept coaxial (rotation axis X0) and can rotate relative to each other by the mutually fitting tube pair S17. The output sun gear 3 has a tube 71 extending to the rear side along the rotation axis X0, and a solid shaft-shaped tube 72 is connected to the rear side of the tube 71. The front end of the tube 12 of the input sun gear 1 passes through the tube 22 of the input sun gear 2 and is connected to the tube 11, while the rear end of the tube 12 of the input sun gear 1 is inserted into the tube 71 of the output sun gear 3 to form a tube pair S17. Hereinafter, for a clearer description, the tubes shown in the figure as solid shafts (e.g., tube 12, tube 72, etc.) are all referred to as the connecting shafts of the corresponding sun gears (e.g., input sun gear 1, output sun gear 7, etc.), and the tubes shown in the figure as hollow tubes (e.g., tube 22, tube 71, etc.) are all referred to as the tubular shafts of the corresponding sun gears (e.g., input sun gear 2, output sun gear 7). It can be that some of the sun gears in the sun gear set 30 are kept coaxial by such mutually fitting tube pairs and can rotate relative to each other.

[0046] Figure 1 The diagram shows a schematic diagram of a four-speed transmission module in which m=2, k=1 and only one input sun gear 2 is equipped with a brake B2.

[0047] Figure 1 In the speed change module 10 , each planetary gear assembly 8 includes three planetary gears 81 , 82 and 87 . The planetary gears 81 , 82 and 87 are fixedly connected as a whole, coaxially and synchronously rotate, and are rotatably mounted on the planet carrier 9 through the planetary shaft 89 .

[0048] The input sun gears 1 and 2 are arranged side by side with the output sun gear 7 and have the same rotation axis X0 as the planet carrier 9, wherein the input sun gear 1 is arranged between the input sun gear 2 and the output sun gear 7. The input sun gear 2 is sleeved on the connecting shaft of the input sun gear 1 through its tubular shaft. The connecting shafts (or tubular shafts) of the input sun gears 1 and 2 both extend out of the center hole 93 of the planet carrier 9 in the direction of one side of the input sun gear. The connecting shaft of the output sun gear 7 extends out of the center hole 94 of the planet carrier 9 in the direction away from the input sun gear 1. The input sun gears 1 and 2, the output sun gear 7 and the input sun gear 1 or 2, and the input sun gear 1, 2 or the output sun gear 7 and the planet carrier 9 can rotate relative to each other. The input sun gear 1 is meshed with the planet gear 81, the input sun gear 2 is meshed with the planet gear 82, and the planet gear 87 is meshed with the output sun gear 7. A clutch C1 is provided between the input sun gear 1 and the torque input shaft S0, and a clutch C2 is provided between the input sun gear 2 and the torque input shaft S0. A brake B2 is provided between the input sun gear 2 and the transmission frame Box, and a brake B9 is provided between the planet carrier 9 and the transmission frame Box.

[0049] Figure 1 The number of gears of the transmission module is calculated as follows:

[0050] C1 and B9 are engaged to form a power transmission route, which is 1st gear;

[0051] C2 and B9 are engaged to form a power transmission route, which is 1st gear;

[0052] C1 and B2 are engaged to form a power transmission route, which is 1st gear;

[0053] C1 and C2 are engaged to form a power transmission route with a transmission ratio of 1, which is 1st gear;

[0054] Total number of gears:

[0055] n=4

[0056] The points where the sun gear meshes with the corresponding planet gears are called pitch points. In particular, Figure 1 In the illustrated embodiment, the pitch circle radius of the gear pair formed by the input sun gear 1 and the planetary gear 81 is R1, the pitch circle radius of the gear pair formed by the input sun gear 2 and the planetary gear 82 is R2, and the pitch circle radius of the gear pair formed by the output sun gear 7 and the planetary gear 87 is R7, and the pitch circle radius = center distance * number of teeth / sum of the number of teeth. It can be set that R1 < R2 < R7, at this time, the clutch C1 of the input sun gear 1 is engaged, and the brake B2 of the input sun gear 2 is engaged, and a reverse gear can be formed.

[0057] Second Embodiment (m=2, k=1)

[0058] As mentioned above, at least one of the m input sun gears is equipped with a brake Bx. In the first embodiment, only one input sun gear 2 is equipped with a brake B2. However, each of the m input sun gears may be equipped with a brake Bx. For example, in the second embodiment, the input sun gear 1 is also equipped with a brake B1.

[0059] Figure 2 The schematic diagram of the principle of a five-speed transmission module 10a is shown, in which m=2, k=1 and the input sun gears 1 and 2 are both equipped with brakes. The present embodiment and subsequent embodiments all use the component numbers and some contents of the previous embodiment, wherein the same number is used to represent the same or similar components, and the description of the same technical contents is selectively omitted. The description of the omitted parts can refer to the previous embodiment, and the present embodiment and subsequent embodiments will not be repeated.

[0060] Figure 2 In the transmission module 10a, the two planetary gear assemblies 8 are evenly spaced 180 degrees relative to the rotation axis X0 of the input sun gear 1 or 2, and each planetary gear assembly 8 includes three planetary gears 81, 82 and 87. The planetary gears 81, 82 and 87 are fixedly connected as a whole, coaxially and synchronously rotate, and are rotatably mounted on the planet carrier 9 through the planetary shaft 89.

[0061] The input sun gears 1 and 2 are arranged side by side with the output sun gear 7 and have the same rotation axis X0 as the planet carrier 9, wherein the input sun gear 1 is arranged between the input sun gear 2 and the output sun gear 7. The input sun gear 2 is sleeved on the connecting shaft of the input sun gear 1 through its tubular shaft. The connecting shafts (or tubular shafts) of the input sun gears 1 and 2 both extend out of the center hole 93 of the planet carrier 9 in the direction of one side of the input sun gear, and the connecting shaft of the output sun gear 7 extends out of the center hole 94 of the planet carrier 9 in the direction away from the input sun gear 1. The input sun gears 1 and 2, the output sun gear 7 and the input sun gear 1 or 2, and the input sun gear 1, 2 or the output sun gear 7 and the planet carrier 9 can rotate relative to each other. The input sun gear 1 is meshed with the planet gear 81, the input sun gear 2 is meshed with the planet gear 82, and the planet gear 87 is meshed with the output sun gear 7. A clutch C1 is provided between the input sun gear 1 and the torque input shaft S0, and a clutch C2 is provided between the input sun gear 2 and the torque input shaft S0. A brake B2 is provided between the input sun gear 2 and the transmission frame Box, and a brake B9 is provided between the planet carrier 9 and the transmission frame Box.

[0062] Figure 2In the embodiment, the brake B1 is located at the rear side of the rear axle hole H2. The input sun gear 1 has an extension shaft 13 in the direction of the output sun gear 7. The output sun gear 7 is sleeved on the extension shaft 13 of the input sun gear 1 through its tubular shaft. The input sun gear 1 and the output sun gear 7 can rotate relative to each other, and the output sun gear 7 outputs torque outward through its tubular shaft. A brake B1 is arranged between the extension shaft 13 of the input sun gear 1 and the transmission frame Box, so that the brake B1 can be arranged between the input sun gear 1 and the transmission frame Box. When the brake B1 is engaged, the input sun gear 1 is braked to prevent it from rotating; when the brake B1 is disengaged, the input sun gear 1 and the transmission frame Box can rotate relative to each other. According to the arrangement requirements, the brakes configured for some or all of the m input sun gears can be located at the rear side of the rear axle hole H2.

[0063] Figure 2 The number of gears of the transmission module is calculated as follows:

[0064] C1 and B9 are engaged to form a power transmission route, which is 1st gear;

[0065] C2 and B9 are engaged to form a power transmission route, which is 1st gear;

[0066] C1 and B2 are engaged to form a power transmission route, which is 1st gear;

[0067] C2 and B1 are engaged to form a power transmission route, which is 1st gear;

[0068] C1 and C2 are engaged to form a power transmission route with a transmission ratio of 1, which is 1st gear;

[0069] Total number of gears:

[0070] n=5

[0071] In particular, Figure 2 In the illustrated embodiment, the pitch circle radius of the gear pair formed by the input sun gear 1 and the planetary gear 81 is R1, the pitch circle radius of the gear pair formed by the input sun gear 2 and the planetary gear 82 is R2, and the pitch circle radius of the gear pair formed by the output sun gear 7 and the planetary gear 87 is R7. It can be set that R1<R2<R7. At this time, when C1 and B2 are engaged, a reverse gear is formed; and when C2 and B1 are engaged, an overdrive gear is formed.

[0072] Figure 3 Shown are two Figure 1 The transmission device 100 is formed by connecting four speed transmission modules 10 in series. In the transmission device 100, the torque output terminal OP1 of the preceding speed transmission module 10 is drivingly connected to the torque input terminal IP2 of the following speed transmission module. Figure 3In the figure, the torque input terminals IP1 and IP2 of the speed change module 10 are torque input shafts, and the torque output terminals OP1 and OP2 are torque output shafts extending from the center of the output sun gear 7 to the rear side. The torque output shaft of the previous speed change module 10 is connected to the torque input shaft of the next speed change module.

[0073] Figure 3 The calculation of the number of gears of the transmission 100 shown is as follows:

[0074] n = 4 × 4 = 16

[0075] Although Figure 3 What is shown in FIG. 1 is a case where two speed change modules 10 are connected in series. However, the speed change device may include more than two speed change modules, and the number of gears in the speed change device is the product of the number of gears of the speed change modules included therein.

[0076] The transmission device may also include different transmission modules. Figure 4 It is shown that Figure 1 The four-speed transmission module 10 and Figure 2 A transmission device 100a is formed by connecting five speed transmission modules 10a in series.

[0077] Figure 4 In the embodiment, the tubular shaft of the output sun gear of the front transmission module 10a (or the torque output end OPa of the five-speed transmission module 10a) is connected to the transfer gear D4, and the torque is transmitted outwardly through the transfer gear D4. The torque input shaft of the rear transmission module 10 (or the torque input end IP2 of the four-speed transmission module 10) is connected to the transfer gear D1. A transfer intermediate shaft SI is also provided, which is parallel to the torque input shafts of the two transmission modules. The transfer intermediate shaft SI is fixedly connected to two transfer gears D2 and D3. The transfer gear D1 is meshed with the transfer gear D2, and the transfer gear D3 is meshed with the transfer gear D4. In particular, for the case where the brake B1 is provided at the rear side of the rear axle hole H2, this arrangement can conveniently bypass the brake B1.

[0078] Figure 4 The number of gears of the illustrated transmission 100a is calculated as follows:

[0079] n=5×4=20

[0080] Third Embodiment (m=2, k=1)

[0081] As mentioned above, the planet carrier 9 may also be provided with a clutch. In the third embodiment, the difference from the second embodiment is at least that the planet carrier 9 is provided with a clutch C9.

[0082] Figure 5 The schematic diagram of the transmission module 10 b is shown in which m=2, k=1 and the input sun gears 1, 2 and the planet carrier 9 are all equipped with brakes and clutches.

[0083] Figure 5 In the transmission module 10b, the two planetary gear assemblies 8 are evenly spaced 180° relative to the rotation axis X0 of the input sun gear 1 or 2, and each planetary gear assembly 8 includes three planetary gears 81, 82 and 87. The planetary gears 81, 82 and 87 are fixedly connected as a whole, coaxially and synchronously rotate, and are rotatably mounted on the planet carrier 9 through the planetary shaft 89.

[0084] The input sun gears 1 and 2 are arranged side by side with the output sun gear 7 and have the same rotation axis X0 as the planet carrier 9, wherein the input sun gear 1 is arranged between the input sun gear 2 and the output sun gear 7. The input sun gear 2 is sleeved on the connecting shaft of the input sun gear 1 through its tubular shaft. The connecting shafts (or tubular shafts) of the input sun gears 1 and 2 both protrude from the center hole 93 of the planet carrier 9 in the direction of one side of the input sun gear. The connecting shaft of the output sun gear 7 protrudes from the center hole 94 of the planet carrier 9 in the direction away from the input sun gear 1. The input sun gears 1 and 2, the output sun gear 7 and the input sun gear 1 or 2, and the input sun gear 1, 2 or the output sun gear 7 and the planet carrier 9 can rotate relative to each other. The input sun gear 1 is meshed with the planet gear 81, the input sun gear 2 is meshed with the planet gear 82, and the planet gear 87 is meshed with the output sun gear 7. A clutch C1 is provided between the input sun gear 1 and the torque input shaft S0, a clutch C2 is provided between the input sun gear 2 and the torque input shaft S0, and a clutch C9 is provided between the planet carrier 9 and the torque input shaft S0. A brake B1 is provided between the input sun gear 1 and the transmission frame Box, a brake B2 is provided between the input sun gear 2 and the transmission frame Box, and a brake B9 is provided between the planet carrier 9 and the transmission frame Box.

[0085] Figure 5 In the embodiment, the brakes B1, B2, B9 of the input sun gear 1, the input sun gear 2 and the planetary carrier 9 are all located at the front side of the front shaft hole H1.

[0086] A clutch C9 is provided between the planet carrier 9 and the torque input shaft S0. Figure 5 In the embodiment, the torque input shaft S0 includes a tube S02 disposed on the periphery of the tube S01 and coaxial therewith, the tube S02 is the inner hub of the clutch C9, the planet carrier 9 has a tube 91 extending along the rotation axis X0, the tube 91 is the outer drum of the clutch C9, the clutch C9 is composed of the tube S02 of the torque input shaft S0 and the tube 91 of the planet carrier 9 and the friction element therebetween, the tube 91 is outer-mounted on the tube S02, the friction element with internal splines is matched with the external splines of the tube S02, and the friction element with external splines is matched with the internal splines of the tube 91. The friction element with internal splines and the friction element with external splines are arranged between the tube S02 and the tube 91, and the friction elements are pressed to fit each other to transmit torque.

[0087] The planet carrier 9 and the input sun gear 2 are kept coaxial (rotation axis X0) and can rotate relative to each other through the mutually fitting tube pair S29. The planet carrier 9 has a tube 92 extending along the rotation axis X0. The tube 92 of the planet carrier 9 is fitted onto the tube 22 of the input sun gear 2. For example, a rotary bearing can be provided between the tube 92 and the tube 22. In this way, the planet carrier 9 and the input sun gear 2 are kept coaxial together with the input sun gear 1 and can rotate relative to each other. The tube 92 of the planet carrier 9 passes through the front shaft hole H1 and is connected to the tube 91.

[0088] Fourth embodiment (m=2, k=1)

[0089] Figure 6 Also shown is a schematic diagram of a transmission module 10c in which m=2, k=1 and the input sun gears 1, 2 and the planet carrier 9 are all equipped with brakes and clutches. Figure 6 The fourth embodiment shown is Figure 5 The difference between the third embodiment and the fourth embodiment is at least that, in the fourth embodiment, the power transmission path from the torque input shaft S0 to the planet carrier 9 is different.

[0090] The planet carrier 9 is connected with a first transfer gear T91, which is meshed with a second transfer gear T92. The torque input shaft S0 is provided with an input transfer gear T0, which is meshed with a third transfer gear T93.

[0091] A clutch C9 is provided between the second transfer gear T92 and the third transfer gear T93. The second transfer gear T92 has a tube S92 extending along its rotation axis X2, the tube S92 is connected to or constitutes the outer drum of the clutch C9, and the third transfer gear T93 has a tube S93 extending along its rotation axis X2, the tube S93 is connected to or constitutes the inner hub of the clutch C9, and the tube S92 is fitted onto the tube S93. For example, the first friction element with internal splines is matched with the outer splines of the inner hub constituted by the tube S93, and the second friction element with external splines is matched with the inner splines of the outer drum constituted by the tube S92. The first friction element with internal splines and the second friction element with external splines are arranged between the inner hub constituted by the tube S93 and the outer drum constituted by the tube S92, and the friction elements are pressed to fit each other to transmit torque.

[0092] The planet carrier 9 is clutchably connected to the torque input shaft S0 via the first transfer gear T91 , the second transfer gear T92 , the clutch C9 , the third transfer gear T93 , and the input transfer gear T0 in sequence.

[0093] Figure 6In the transmission module 10c, a planet carrier transfer shaft SX2 is provided in parallel with the torque input shaft S0. Transfer gears T92 and T93 are respectively mounted on the planet carrier transfer shaft SX2. The transfer gear T93 is meshed with the transfer gear T0, and the transfer gear T92 is meshed with the transfer gear T91 connected to the planet carrier 9. The clutch C9 is provided between the transfer gear T92 and the transfer gear T93. When the clutch C9 is engaged, the torque can be transmitted between the transfer gear T93 and the transfer gear T92; when the clutch C9 is disengaged, the transfer gear T93 and the transfer gear T92 can rotate relative to each other.

[0094] A brake B9 is provided between the transfer gear T92 and the transmission frame Box, and a tube S92 is connected to or constitutes the inner hub of the brake B9, and the outer drum of the brake B9 is connected to the transmission frame Box. When the brake B9 is engaged, the transfer gear T92 is braked to prevent it from rotating, and the transfer gear T91 meshing with the transfer gear T92 is also prevented from rotating, and the planetary carrier 9 connected to the transfer gear T91 is also prevented from rotating; when the brake B9 is disengaged, the parts that are prevented from rotating can rotate relative to the transmission frame Box.

[0095] Furthermore, in the fourth embodiment, the brakes B2, B9 of the input sun gear 2 and the planetary carrier 9 are located on the front side of the front shaft hole H1, while the brake B1 of the input sun gear 1 is located on the rear side of the rear shaft hole H2.

[0096] Figure 6 In the embodiment, the input sun gear 1 has an extension shaft in the direction of one side of the output sun gear 7, and the output sun gear 7 is sleeved on the extension shaft of the input sun gear 1 through its tubular shaft, and the input sun gear 1 and the output sun gear 7 can rotate relative to each other. The output sun gear 7 outputs torque outward through its tubular shaft. A brake B1 is provided between the extension shaft of the input sun gear 1 and the transmission frame Box. When the brake B1 is engaged, the input sun gear 1 is braked to prevent it from rotating; when the brake B1 is disengaged, the input sun gear 1 and the transmission frame Box can rotate relative to each other.

[0097] Figure 6 The structure can facilitate the arrangement of the clutch Cx and the brake Bx.

[0098] Fifth embodiment (m=3, k=1)

[0099] Figure 7 The schematic diagram of the transmission module 10d is shown in which m=3, k=1 and the input sun gears 1, 2, 3 and the planet carrier 9 are all equipped with brakes and clutches.

[0100] Figure 7In the transmission module 10d, the two planetary gear assemblies 8 are evenly spaced 180 degrees relative to the rotation axis X0 of the input sun gear 1, 2 or 3, and each planetary gear assembly 8 includes four planetary gears 81, 82, 83 and 87. The planetary gears 81, 82, 83 and 87 are fixedly connected as a whole, coaxially and synchronously rotate, and are rotatably mounted on the planet carrier 9 through the planetary shaft 89.

[0101] The input sun gears 1, 2, 3 are arranged side by side with the output sun gear 7 and have the same rotation axis X0 as the planet carrier 9, wherein the input sun gear 1 is arranged between the input sun gear 2 and the output sun gear 7, and the input sun gear 3 is arranged on the side of the input sun gear 2 away from the output sun gear 7. The input sun gear 3 is sleeved on the tubular shaft of the input sun gear 2 through its tubular shaft, and the input sun gear 2 is sleeved on the connecting shaft of the input sun gear 1 through its tubular shaft, wherein the input sun gear farthest from the output sun gear is sleeved on the tubular shaft (or connecting shaft) of the adjacent input sun gear close to the output sun gear through its tubular shaft. The tubular shafts (or connecting shafts) of the input sun gears 1, 2, 3 all protrude from the center hole 93 of the planet carrier 9 in the direction of one side of the input sun gear 3. The connecting shaft of the output sun gear 7 protrudes from the center hole 94 of the planet carrier 9 in the direction away from the input sun gear 3. The input sun gears 1, 2, and 3, the output sun gear 7 and the input sun gears 1, 2, or 3, and the input sun gears 1, 2, 3 or the output sun gear 7 and the planet carrier 9 can rotate relative to each other. The input sun gear 1 is meshed with the planet gear 81, the input sun gear 2 is meshed with the planet gear 82, the input sun gear 3 is meshed with the planet gear 83, and the planet gear 87 is meshed with the output sun gear 7. A clutch C1 is provided between the input sun gear 1 and the torque input shaft S0, a clutch C2 is provided between the input sun gear 2 and the torque input shaft S0, a clutch C3 is provided between the input sun gear 3 and the torque input shaft S0, and a clutch C9 is provided between the planet carrier 9 and the torque input shaft S0. A brake B1 is provided between the input sun gear 1 and the transmission frame Box, a brake B2 is provided between the input sun gear 2 and the transmission frame Box, a brake B3 is provided between the input sun gear 3 and the transmission frame Box, and a brake B9 is provided between the planet carrier 9 and the transmission frame Box.

[0102] Figure 7 In the embodiment, the brakes B1, B2, B3, B9 of the input sun gears 1, 2, 3 and the planetary carrier 9 are all located at the front side of the front shaft hole H1.

[0103] Figure 7 In the embodiment, clutches C1, C2, C3 and C9 are respectively arranged between the input sun gears 1, 2, 3 and the planet carrier 9 and the torque input shaft S0, so that they can be connected to the torque input shaft S0 in a clutchable manner.

[0104] Sixth embodiment (m=3, k=1)

[0105] Figure 8 Also shown is a schematic diagram of a transmission module 10 e in which m=3, k=1 and the input sun gears 1, 2, 3 and the planet carrier 9 are all equipped with brakes and clutches. Figure 8 The sixth embodiment shown is Figure 7 The difference between the fifth embodiment and the sixth embodiment is at least that, in the sixth embodiment, the power transmission path from the torque input shaft S0 to the planetary carrier 9 and the input sun gear 3 is different.

[0106] Figure 8 The power transmission path of the planet carrier 9 in Figure 6 Similar to . Figure 8 In the embodiment, the planet carrier 9 is connected to the first transfer gear T91, which is meshed with the second transfer gear T92 for transmission. The torque input shaft S0 is provided with an input transfer gear T0, which is meshed with the third transfer gear T93 for transmission. A clutch C9 is provided between the second transfer gear T92 and the third transfer gear T93. The planet carrier 9 is connected to the torque input shaft S0 in a clutchable manner through the first transfer gear T91, the second transfer gear T92, the clutch C9, the third transfer gear T93 and the input transfer gear T0 in sequence.

[0107] Figure 8 In the embodiment, the input sun gear 3 is connected to the first transfer gear T31, which is meshed with the second transfer gear T32. The torque input shaft S0 is provided with an input transfer gear T0, which is meshed with the third transfer gear T33.

[0108] A clutch C3 is provided between the second transfer gear T32 and the third transfer gear T33. The second transfer gear T32 has a tube S32 extending along its rotation axis X3, the tube S32 is connected to or constitutes the outer drum of the clutch C3, and the third transfer gear T33 has a tube S33 extending along its rotation axis X3, the tube S33 is connected to or constitutes the inner hub of the clutch C3, and the tube S32 is externally mounted on the tube S33. For example, the first friction element with internal splines is matched with the external splines of the tube S33 constituting the inner hub of the clutch C3, and the second friction element with external splines is matched with the internal splines of the tube S32 constituting the outer drum of the clutch C3. The first friction element with internal splines and the second friction element with external splines are arranged between the tube S33 and the tube S32, and the friction elements are pressed to fit each other to transmit torque.

[0109] The input sun gear 3 is clutchably connected to the torque input shaft S0 via the first transfer gear T31 , the second transfer gear T32 , the clutch C3 , the third transfer gear T33 , and the input transfer gear T0 in sequence.

[0110] Figure 8In the example, the other input sun gears 1 and 2 are not connected to the transfer gears. Figure 8 In the embodiment, one of the three sun gears, the input sun gear 3, is connected to the first transfer gear T31, and a power transmission path is formed through the transfer gear. It can be that some of the m input sun gears are connected to the first transfer gear, such as Figure 8 As shown. Alternatively, all of the m input sun gears are connected to the first transfer gear. Alternatively, all of the m input sun gears do not receive power through the transfer gear, for example, Figure 1 , Figure 2 and Figure 5 shown.

[0111] Figure 8 In the speed module 10e, a planetary carrier transfer shaft SX2 is arranged parallel to the torque input shaft S0. Transfer gears T92 and T93 are respectively installed on the planetary carrier transfer shaft SX2. The transfer gear T93 is meshed with the transfer gear T0, and the transfer gear T92 is meshed with the transfer gear T91 connected to the planetary carrier 9. The clutch C9 is arranged between the transfer gear T92 and the transfer gear T93. When the clutch C9 is engaged, the torque can be transmitted between the transfer gear T93 and the transfer gear T92; when the clutch C9 is disengaged, the transfer gear T93 and the transfer gear T92 can rotate relative to each other. A brake B9 is arranged between the transfer gear T92 and the transmission frame Box. When the brake B9 is engaged, the transfer gear T92 is braked to prevent it from rotating, the transfer gear T91 meshing with the transfer gear T92 is also prevented from rotating, and the planetary carrier 9 connected to the transfer gear T91 is also prevented from rotating; when the brake B9 is disengaged, the parts that are prevented from rotating can rotate relative to the transmission frame Box.

[0112] An input sun gear transfer shaft SX3 is provided in parallel with the torque input shaft S0 , and a transfer gear T32 and a transfer gear T33 are mounted on the input sun gear transfer shaft SX3 , respectively. The transfer gear T33 is meshed with the transfer gear T0, and the transfer gear T32 is meshed with the transfer gear T31 connected to the input sun gear 3. A clutch C3 is arranged between the transfer gears T33 and T32. When the clutch C3 is engaged, torque can be transmitted between the transfer gears T33 and T32. When the clutch C3 is disengaged, the transfer gear T33 and the transfer gear T32 can rotate relative to each other. A brake B3 is arranged between the transfer gear T32 and the transmission frame Box. When the brake B3 is engaged, the transfer gear T32 is braked to prevent it from rotating, and the transfer gear T31 meshed with the transfer gear T32 is also prevented from rotating, and the input sun gear 3 connected to the transfer gear T31 is also prevented from rotating; when the brake B3 is disengaged, the parts that are prevented from rotating can rotate relative to the transmission frame Box.

[0113] Also, in the sixth embodiment, the brakes B2, B3, B9 of the input sun gears 2, 3 and the planetary carrier 9 are located on the front side of the front shaft hole H1, while the brake B1 of the input sun gear 1 is located on the rear side of the rear shaft hole H2.

[0114] Figure 8 In the embodiment, the input sun gear 1 has an extension shaft in the direction of one side of the output sun gear 7, and the output sun gear 7 is sleeved on the extension shaft of the input sun gear 1 through its tubular shaft, and the input sun gear 1 and the output sun gear 7 can rotate relative to each other, wherein the input sun gear 1 is the input sun gear closest to the output sun gear 7. The output sun gear 7 outputs torque outward through its tubular shaft. A brake B1 is provided between the extension shaft of the input sun gear 1 and the transmission frame Box. When the brake B1 is engaged, the input sun gear 1 is braked to prevent it from rotating; when the brake B1 is disengaged, the input sun gear 1 and the transmission frame Box can rotate relative to each other.

[0115] Figure 8 The structure can facilitate the arrangement of the clutch Cx and the brake Bx.

[0116] Seventh Embodiment (m=2, k=2)

[0117] Fig. 9 The schematic diagram of the transmission module 10f is shown in which m=2, k=2 and the input sun gears 1, 2 and the planet carrier 9 are all equipped with brakes and clutches. Fig. 9 In the seventh embodiment, the two output sun gears 6 and 7 are held coaxially (rotation axis X0) by a pair of tubes S67 that fit into each other and are rotatable relative to each other.

[0118] Fig. 9 In the transmission module 10f, the two planetary gear assemblies 8 are evenly spaced 180 degrees relative to the rotation axis X0 of the input sun gear 1 or 2, and each planetary gear assembly 8 includes four planetary gears 81, 82, 87 and 86. The planetary gears 81, 82, 87 and 86 are fixedly connected as a whole, coaxially and synchronously rotate, and are rotatably mounted on the planet carrier 9 through the planetary shaft 89.

[0119] The input sun gears 1 and 2 are arranged side by side with the output sun gears 7 and 6 and have the same rotation axis X0 as the planet carrier 9, wherein the input sun gear 1 is arranged between the input sun gear 2 and the output sun gear 7. The input sun gear 2 is sleeved on the connecting shaft of the input sun gear 1 through its tubular shaft. The connecting shafts (or tubular shafts) of the input sun gears 1 and 2 both protrude from the center hole 93 of the planet carrier 9 in the direction of one side of the input sun gear 2. The output sun gear 6 is arranged on the other side of the output sun gear 7 (one side of the output sun gear 7 is the input sun gear 1). The output sun gear 6 is sleeved on the connecting shaft of the output sun gear 7 through its tubular shaft. In other words, the input sun gear far away from the output sun gear is sleeved on the connecting shaft of the adjacent input sun gear close to the output sun gear through its tubular shaft, and the output sun gear far away from the input sun gear is sleeved on the connecting shaft of the adjacent output sun gear close to the input sun gear through its tubular shaft. The connecting shaft (or tubular shaft) of the output sun gears 7 and 6 protrudes from the central hole 94 of the planet carrier 9 to the side away from the input sun gear 1, forming two torque output shafts SP7 and SP6 respectively. The number of output sun gears is the same as the number of torque output shafts. The input sun gears 1 and 2, the output sun gears 7 and 6 and the input sun gear 1 or 2, and the input sun gears 1 and 2, the output sun gears 7 and 6 and the planet carrier 9 can rotate relative to each other. The input sun gear 1 is meshed with the planetary gear 81, the input sun gear 2 is meshed with the planetary gear 82, the planetary gear 87 is meshed with the output sun gear 7, and the planetary gear 86 is meshed with the output sun gear 6. A clutch C1 is provided between the input sun gear 1 and the torque input shaft S0, a clutch C2 is provided between the input sun gear 2 and the torque input shaft S0, and a clutch C9 is provided between the planet carrier 9 and the torque input shaft S0. A brake B1 is provided between the input sun gear 1 and the transmission frame Box, a brake B2 is provided between the input sun gear 2 and the transmission frame Box, and a brake B9 is provided between the planet carrier 9 and the transmission frame Box.

[0120] Eighth Embodiment (m=3, k=2)

[0121] Fig.10 The schematic diagram of the transmission module 10g is shown in which m=3, k=2 and the input sun gears 1, 2, 3 and the planet carrier 9 are all equipped with brakes and clutches.

[0122] Fig.10 In the transmission module 10g, two planetary gear assemblies 8 are evenly spaced 180 degrees relative to the rotation axis X0 of the input sun gear 1, 2 or 3, and each planetary gear assembly 8 includes five planetary gears 81, 82, 83, 87 and 86. The planetary gears 81, 82, 83, 87 and 86 are fixedly connected as a whole, coaxially and synchronously rotate, and are rotatably mounted on the planet carrier 9 through the planetary shaft 89.

[0123] The input sun gears 1, 2, 3 and the output sun gears 7, 6 are arranged side by side and have the same rotation axis X0 as the planet carrier 9, wherein the input sun gear 1 is arranged between the input sun gear 2 and the output sun gear 7, and the input sun gear 3 is arranged on the other side of the input sun gear 2 (one side of the input sun gear 2 is the input sun gear 1). The input sun gear 3 is sleeved on the tubular shaft of the input sun gear 2 through its tubular shaft, and the input sun gear 2 is sleeved on the connecting shaft of the input sun gear 1 through its tubular shaft. The connecting shafts (or tubular shafts) of the input sun gears 1, 2, 3 all protrude from the center hole 93 of the planet carrier 9 in the direction of one side of the input sun gear 3. The output sun gear 6 is arranged on the other side of the output sun gear 7 (one side of the output sun gear 7 is the input sun gear 1), and the output sun gear 6 is sleeved on the connecting shaft of the output sun gear 7 through its tubular shaft. In other words, the input sun gear far from the output sun gear is sleeved on the connecting shaft of the adjacent input sun gear near the output sun gear through its tubular shaft, and the output sun gear far from the input sun gear is sleeved on the connecting shaft of the adjacent output sun gear near the input sun gear through its tubular shaft. The connecting shafts (or tubular shafts) of the output sun gears 7 and 6 extend out of the central hole 94 of the planet carrier 9 toward the side far from the input sun gear 1, forming two torque output shafts SP7 and SP6 respectively. The input sun gears 1, 2, and 3, the output sun gears 7 and 6, and the input sun gears 1, 2, and 3, the output sun gears 7 and 6 and the planet carrier 9 can rotate relative to each other. The input sun gear 1 is meshed with the planetary gear 81, the input sun gear 2 is meshed with the planetary gear 82, the input sun gear 3 is meshed with the planetary gear 83, the planetary gear 87 is meshed with the output sun gear 7, and the planetary gear 86 is meshed with the output sun gear 6. A clutch C1 is provided between the input sun gear 1 and the torque input shaft S0, a clutch C2 is provided between the input sun gear 2 and the torque input shaft S0, a clutch C3 is provided between the input sun gear 3 and the torque input shaft S0, and a clutch C9 is provided between the planet carrier 9 and the torque input shaft S0. A brake B1 is provided between the input sun gear 1 and the transmission frame Box, a brake B2 is provided between the input sun gear 2 and the transmission frame Box, a brake B3 is provided between the input sun gear 3 and the transmission frame Box, and a brake B9 is provided between the planet carrier 9 and the transmission frame Box.

[0124] According to the present invention Figures 5 to 10 In the transmission module, each input sun gear or planet carrier is connected with a clutch Cx and a brake Bx, wherein the number of output sun gears is k and the number of input sun gears is m. The m input sun gears and planet carriers constitute m+1 selectable elements. Figures 5 to 10 The gear position formation of the speed change module is as follows:

[0125] Because each input sun gear or planet carrier is equipped with a clutch Cx and a brake Bx, the number of clutches Cx or brakes Bx is: m+1

[0126] The number of gears for a certain output sun gear is calculated as follows: arbitrarily select one of the aforementioned m+1 elements (input sun gear or planet carrier) to which the clutch Cx is connected to engage (with possible options), and at the same time, the brake Bx connected to another element other than the aforementioned element is selected to engage (the clutch Cx and brake Bx connected to the same element cannot be engaged at the same time, so there is According to the above requirements, one Cx and one Bx are engaged to form a power transmission route, that is, a gear. According to actual needs, the transmission ratio of the power transmission route formed by the engagement of different Cx or different Bx can be different.

[0127] The number of options for the output sun gear is indivual.

[0128] Among all the clutches Cx connected to the input sun gear or the planet carrier, any two selected to be engaged will form a transmission ratio of 1.

[0129] therefore, Figures 5 to 10 The total number of gears of the transmission module can be calculated by the following formula:

[0130]

[0131] Figure 5 or Figure 6 The number of gears of the transmission module (where m=2, k=1) is calculated as follows:

[0132]

[0133] Figure 7 or Figure 8 The number of gears of the transmission module (where m=3, k=1) is calculated as follows:

[0134]

[0135] Fig. 9 The number of gears of the transmission module (where m=2, k=2) is calculated as follows:

[0136]

[0137] Fig.10 The number of gears of the transmission module (where m=3, k=2) is calculated as follows:

[0138]

[0139] Therefore, for a six-speed transmission, only Figure 5 or Figure 6Six forward gear ratios and one reverse gear ratio can be obtained by using the embodiment of Figure 7 or Figure 8 The embodiment can obtain 10 forward gear ratios and 3 reverse gear ratios.

[0140] Therefore, the use of the speed change module or speed change device of the present invention can greatly shorten the axial dimension of the multi-gear transmission. Moreover, the structure is simpler and the weight is lighter. The complex nesting between the traditional planetary gear and the components related to the planetary gear is avoided, thereby eliminating the disadvantages of the complex structure and difficult processing of the components related to the planetary gear mechanism.

[0141] The speed change device of the present invention can also be called a multi-speed, ring-less planetary gear speed change device, and can be applied to vehicles and the like.

[0142] In the above embodiment, all input sun gears and all output sun gears are arranged side by side and have the same rotation axis as the planet carrier, and the input sun gears and the output sun gears are adjacent. The torque input shaft has the same rotation axis as the input sun gears and the planet carrier. The input sun gear far from the output sun gear is sleeved on the connecting shaft (or tubular shaft) of the adjacent input sun gear close to the output sun gear through its tubular shaft, and the connecting shafts (or tubular shafts) of all input sun gears protrude from the center hole of the planet carrier toward the input sun gear side.

[0143] When there is more than one output sun gear, the output sun gear far away from the input sun gear is sleeved on the connecting shaft (or tubular shaft) of the adjacent output sun gear close to the input sun gear through its tubular shaft, and the connecting shafts (or tubular shafts) of all the output sun gears protrude from the center hole of the planet carrier toward one side of the output sun gear.

[0144] All input sun gears, all output sun gears and all planetary gears mesh one by one. A clutch Cx is provided between each input sun gear and the torque input shaft S0, and a brake Bx is provided between the input sun gear closest to the torque input shaft S0 and the transmission frame Box. A brake B9 is provided between the planet carrier 9 and the transmission frame Box. Different embodiments can be formed according to whether the brake Bx is added to the input sun gear and whether the clutch Cx is added to the planet carrier.

[0145] The clutch Cx includes an active part and a driven part. The active part of the clutch Cx is directly or indirectly connected to the torque input shaft S0, and the driven part of the clutch Cx is directly or indirectly connected to the input sun gear or planet carrier. When a clutch Cx is engaged, the torque is transferred from the torque input shaft S0 to the corresponding input sun gear or planet carrier; conversely, when a clutch Cx is disengaged, the torque is interrupted. A brake Bx is provided between each input sun gear, planet carrier and transmission frame Box.

[0146] The brake Bx includes a rotatable part and a non-rotatable part. The non-rotatable part of the brake Bx is directly or indirectly connected to the transmission frame Box, and the rotatable part of the brake Bx is directly or indirectly connected to the input sun gear or planet carrier. When a certain brake Bx is engaged, the corresponding input sun gear or planet carrier is prevented from rotating; conversely, when a certain brake Bx is disengaged, the corresponding input sun gear or planet carrier is allowed to rotate.

[0147] Figure 3 In the embodiment, the speed change device includes two speed change modules, the torque output shaft of the first speed change module is connected to the torque input shaft of the second speed change module, the number of speed ratios set for each speed change module is the same, and the specific values ​​of the speed ratios may be different. Each speed change module is provided with two input sun gears and one output sun gear, and the input sun gear away from the output sun gear is sleeved on the connecting shaft of the other input sun gear through its tubular shaft. At the same time, each speed change module is provided with two planetary gear assemblies, and the two planetary gear assemblies are evenly distributed at 180° relative to the rotation axis of the input sun gear. Each planetary gear assembly is provided with three planetary gears, which are respectively meshed with the two input sun gears and one output sun gear. A clutch Cx and a brake Bx are provided on the input sun gear close to the torque input shaft S0, a clutch Cx is provided on the other input sun gear, and a brake Bx is provided on the planet carrier.

[0148] Figure 4In the invention, the speed change device includes two speed change modules, the torque input shafts of the two speed change modules are arranged in parallel or overlapped, and the speed ratio setting of each speed change module is different. Each speed change module is provided with two input sun gears and one output sun gear, and the input sun gear far away from the output sun gear is sleeved on the connecting shaft of another input sun gear through its tubular shaft. At the same time, each speed change module is provided with two planetary gear assemblies, and the two planetary gear assemblies are evenly distributed at 180° relative to the rotation axis of the input sun gear. Each planetary gear assembly is provided with three planetary gears, which are respectively meshed with the two input sun gears and one output sun gear. The two input sun gears of the previous speed change module are both provided with a clutch Cx and a brake Bx, and the brake Bx is provided on the planet carrier. The input sun gear close to the output sun gear has an extension shaft in the direction of the output sun gear, and the output sun gear is sleeved on the extension shaft of the input sun gear through its tubular shaft. The input sun gear and the output sun gear can rotate relative to each other, and a brake is arranged on the extension shaft of the input sun gear, so that it is convenient to arrange the brake on the input sun gear. The tubular shaft of the output sun gear is connected with a transfer gear D4, and the torque is transmitted backwards through the transfer gear D4. The difference between the latter speed module and the former speed module is that: the brake Bx is not set on the input sun gear close to the output sun gear, so the input sun gear does not need to extend the shaft in the direction of the output sun gear, and the output sun gear does not need to be set with a tubular shaft. The rest of the structural settings are similar to the former speed module. A transfer intermediate shaft is provided, and the transfer intermediate shaft is parallel to the torque input shafts of the two speed modules. Two transfer gears D3 and D2 are fixedly connected to the transfer intermediate shaft. The torque input shaft S0 of the latter speed module is connected with a transfer gear D1, and the transfer gear D4 is meshed with the transfer gear D3, and the transfer gear D2 is meshed with the transfer gear D1, so that the brake on the extension shaft of the input sun gear can be avoided.

[0149] In fact, each speed-changing module can be used reversely, and a large speed-changing device composed of a plurality of speed-changing modules can also be used reversely.

[0150] Although the present invention is disclosed as above with preferred embodiments, it is not intended to limit the present invention, and any person skilled in the art may make possible changes and modifications without departing from the spirit and scope of the present invention. For example, the transformation modes under the above various different embodiments may be appropriately combined.

[0151] Any modifications, equivalent changes and modifications made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention shall fall within the protection scope defined by the claims of the present invention.

Claims

1. A speed change module, having a transmission frame, comprising a torque input end, a transmission unit and a torque output end, wherein the torque of the torque input end is transmitted to the torque output end via the transmission unit, characterized in that: The transmission unit comprises: A planet carrier rotatably disposed on the transmission frame; A sun gear set, comprising m input sun gears and k output sun gears, wherein each sun gear in the sun gear set is coaxially arranged with the planet carrier and can rotate relative to each other, wherein m≥2, k≥1; and at least one planetary gear assembly, each of the planetary gear assemblies comprising m input planetary gears respectively meshing with the m input sun gears, and k output planetary gears respectively meshing with the k output sun gears, the input planetary gears and the output planetary gears being coaxially fixedly connected, and the planetary gear assembly being rotatably disposed on the planet carrier; Each of the input sun gears is equipped with a brake, and each of the input sun gears is detachably connected to the torque input end via a clutch, and the planet carrier is also equipped with a brake; The transmission module is configured to select two elements from the m+1 elements consisting of the m input sun gears and the planetary carriers, so that the clutch of one of the two elements is in an engaged state and the brake of the other element is in a braking state, or so that the clutches of the two elements are in an engaged state, thereby forming a power transmission route of the transmission module.

2. The speed change module according to claim 1, characterized in that: The planet carrier is also detachably connected to the torque input end via a clutch.

3. The speed change module according to claim 1, characterized in that: The torque input end includes a torque input shaft, and each clutch includes an inner hub and an outer drum that can be clutched; The torque input shaft and at least some of the m input sun gears are respectively connected to one and the other of the inner hub and the outer drum of the corresponding clutch.

4. The speed change module according to claim 1, characterized in that: At least some of the m input sun gears are connected to a first transfer gear, and the first transfer gear is meshed with a second transfer gear for transmission; The torque input end comprises a torque input shaft, the torque input shaft is provided with an input transfer gear, and the input transfer gear is meshed with the third transfer gear for transmission; A clutch is provided between the second transfer gear and the third transfer gear, and the at least part of the input sun gear is clutchably connected to the torque input shaft through the first transfer gear, the second transfer gear, the clutch, the third transfer gear and the input transfer gear in sequence.

5. The speed change module according to claim 1, characterized in that: The speed change module includes more than two planetary gear assemblies, and the more than two planetary gear assemblies are evenly distributed along the circumferential direction of the sun gear set.

6. The speed change module according to claim 1, characterized in that: At least some of the sun gears in the sun gear set are held coaxially by mutually sleeved tube pairs and are rotatable relative to each other.

7. The speed change module according to claim 1, characterized in that: The transmission frame includes a front axle hole and a rear axle hole that are coaxial and arranged side by side; The planet carrier is rotatably supported between the front shaft hole and the rear shaft hole, the torque input end is located at the front side of the front shaft hole, and the torque output end is located at the rear side of the rear shaft hole.

8. The speed change module according to claim 7, characterized in that: The brakes of at least some of the m input sun gears are located at the rear side of the rear axle hole.

9. A speed change device, characterized in that: It comprises two or more speed change modules according to any one of claims 1 to 8, wherein the torque output end of a preceding speed change module among the two or more speed change modules is drivingly connected to the torque input end of a succeeding speed change module.

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