CN211039559U

CN211039559U - Speed change device and speed change module

Info

Publication number: CN211039559U
Application number: CN201921653063.1U
Authority: CN
Inventors: 韩文明
Original assignee: Ningbo Beilun Xutai Auto Parts Co ltd
Current assignee: Ningbo Beilun Xutai Auto Parts Co ltd
Priority date: 2019-09-30
Filing date: 2019-09-30
Publication date: 2020-07-17
Anticipated expiration: 2029-09-30

Abstract

The utility model provides a speed changing module, the speed changer frame has, including the moment of torsion input, drive unit and moment of torsion output, in the drive unit, the planet carrier rotatably sets up in the speed changer frame, the sun wheel group includes input sun gear more than two and more than one output sun gear, but each sun gear in the sun wheel group sets up and relative rotation between each other with the planet carrier coaxial line, every planet wheel assembly includes and corresponds the input planet wheel of meshing respectively with input sun gear, and correspond the output planet wheel of meshing respectively with output sun gear, input planet wheel and output planet wheel link firmly coaxially, planet wheel assembly rotatably sets up in the planet carrier. At least one input sun gear is provided with a brake, and each input sun gear is in each case connected to the torque input in a disengageable manner via a clutch, the carrier also being provided with a brake. The utility model discloses still provide the speed change gear including above-mentioned variable speed module. The speed change module can provide more speed ratios.

Description

Speed change device and speed change module

Technical Field

The utility model relates to a speed change module still relates to a speed change gear including this speed change module.

Background

In practice, there are two types of gear transmissions: fixed axis drives and planetary gear drives, wherein the planetary mechanism has a ring gear. For example, a Manual Transmission (MT) and a double clutch automatic transmission (DCT) applied to a vehicle belong to a fixed shaft type transmission, while a torque converter type Automatic Transmission (AT) applied to a vehicle mostly belongs to a planetary gear type transmission with a ring gear.

In the former patent of the inventor, 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 combined transmission, and chinese invention patent CN108286591A discloses a single-input three-gear powertrain system.

The inventor continuously researches on the basis of the above, and finds that the common characteristics of the three speed changing devices are as follows: one speed change module only has one input sun gear; one speed change module only has one output sun gear; a planetary gear assembly comprising two planetary gears connected together for coaxial synchronous rotation; one speed change module provides three speed ratios at most; if more gears are realized, a plurality of speed changing modules need to be connected in series, so that the axial size is large; the speed changing module is free of a gear ring, and all the gear meshing modes are external gears; the transmission mode has two transmission modes of a fixed shaft type and a planetary gear type: the three speed change devices are of a fixed-axis type transmission when the cage (or referred to as a carrier) is stationary, and of a planetary gear type transmission when the input or output central sun gear is stationary, and therefore, the transmission mode of such a speed change device represented by the three speed change devices is a hybrid transmission mode; simple structure, easy manufacture, low cost and high cost performance.

The inventor desires to provide an improved planetary gear mechanism which can continuously retain the advantages of no ring gear, simple structure and easy manufacture of the planetary gear mechanism in the aforementioned patent, and provide more speed ratios on the basis of continuously adopting a unique hybrid transmission mode (a combination of a fixed shaft transmission and a planetary gear transmission).

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing a speed change module can provide more speed ratios.

The utility model provides a speed changing module has the derailleur frame, including moment of torsion input, drive unit and moment of torsion output, the moment of torsion of moment of torsion input transmits to the moment of torsion output via drive unit, and drive unit includes planet carrier, sun gear group and at least one planet wheel assembly. The planet carrier is rotatably arranged on the transmission frame. The sun wheel set comprises m input sun wheels and k output sun wheels, each sun wheel in the sun wheel set and the planet carrier are coaxially arranged and can rotate relative to each other, wherein m is larger than or equal to 2, and k is larger than or equal to 1. Each planet wheel assembly comprises m input planet wheels which are correspondingly meshed with m input sun wheels respectively, and k output planet wheels which are correspondingly meshed with k output sun wheels respectively, wherein the input planet wheels and the output planet wheels are coaxially and fixedly connected, and the planet wheel assembly is rotatably arranged on a planet carrier. At least one input sun gear is provided with a brake, and each input sun gear is in each case connected to the torque input in a disengageable manner via a clutch, the carrier also being provided with a brake. The transmission module is configured to select two elements from m +1 elements of the m input sun gears and the planet carrier such 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 such that the clutches of the two elements are in an engaged state, thereby forming one power transmission route of the transmission module.

In one embodiment, the planet carrier is also connected to the torque input in a clutchable manner via a clutch.

In one embodiment, each input sun is configured with a brake.

In one embodiment, the torque input comprises a torque input shaft, each clutch comprising a clutchably connected inner hub and outer drum; at least some of the torque input shaft and the m input sun gears are connected to one and the other of the inner hub and the outer drum of the corresponding clutch, respectively.

In one embodiment, at least some of the m input sun gears are connected with a first transfer gear, and the first transfer gear is in mesh transmission with a second transfer gear. The torque input end comprises a torque input shaft, the torque input shaft is provided with an input switching gear, and the input switching gear is in meshing transmission with the third switching gear. A clutch is arranged between the second switching gear and the third switching gear, and at least part of the input sun gear can be connected to the torque input shaft in a clutchable manner through the first switching gear, the second switching gear, the clutch, the third switching gear and the input switching gear in sequence.

In one embodiment, the transmission module includes two or more planetary gear assemblies evenly distributed along a circumferential direction of the sun gear set.

In one embodiment, at least some of the sun gears of the sun gear set are held coaxially and rotatably relative to each other by tube pairs that nest with each other.

In one embodiment, the transmission housing includes a front shaft bore and a rear shaft bore that are coaxial and arranged side-by-side; the planet carrier is rotatably supported between the front axle hole and the rear axle hole, the torque input end is positioned at the front side of the front axle hole, and the torque output end is positioned at the rear side of the rear axle hole.

In one embodiment, at least some of the m input sun gears are configured with brakes located rearward of the rear axle aperture.

The utility model also provides a speed change gear, including foretell more than two speed change modules, the moment of torsion output of the preceding speed change module in the more than two speed change modules is connected with the moment of torsion input transmission of a back speed change module.

The speed change module provides an improved planetary gear mechanism which has the advantages of no gear ring, simple structure, easy manufacture and the like, and can provide a plurality of speed ratios on the basis of adopting a unique hybrid transmission mode (both a fixed shaft type transmission and a planetary gear type transmission).

In the speed change module of the utility model, one speed change module has at least two input sun wheels; one speed change module is not limited to only one output sun gear, and more than two output sun gears can be provided; the number of the planet gears included in one planet gear assembly is not less than three. The utility model discloses a speed change module can produce four speed ratios at least to provide probably for producing more speed ratios. To the derailleur that velocity ratio quantity is the same, the utility model discloses required variable speed module is showing and is reducing, and the volume is littleer, weight is lighter, the cost is lower.

Drawings

The above and other features, properties and advantages of the present invention will become more apparent from the following description of the embodiments with reference to the accompanying drawings, in which:

FIG. 1 is a schematic diagram of a four speed transmission module having two input sun gears and one output sun gear.

FIG. 2 is a schematic diagram of a five speed transmission module having two input sun gears and one output sun gear.

Fig. 3 is a schematic diagram of a transmission formed by two transmission modules of fig. 1 connected in series.

Fig. 4 is a schematic diagram of a transmission formed by connecting the transmission module of fig. 3 and the transmission module of fig. 1 in series.

FIG. 5 is a schematic diagram of a seven speed transmission module having two input sun gears and one output sun gear.

FIG. 6 is another schematic layout of a seven speed transmission module having two input sun gears and one output sun gear.

FIG. 7 is a schematic diagram of a thirteen-speed transmission module having three input sun gears and one output sun gear.

FIG. 8 is another schematic layout of a thirteen-speed transmission module having three input sun gears and one output sun gear.

FIG. 9 is a schematic diagram of a thirteen-speed transmission module having two input sun gears and two output sun gears.

FIG. 10 is a schematic diagram of a twenty-five speed transmission module having three input sun gears and two output sun gears.

Detailed Description

The present invention will be further described with reference to the following detailed description and the accompanying drawings, wherein the following description sets forth more details for the purpose of providing a thorough understanding of the present invention, but it is obvious that the present invention can be implemented in many other ways different from those described herein, and those skilled in the art can make similar generalizations and deductions based on the practical application without departing from the spirit of the present invention, and therefore, the scope of the present invention should not be limited by the contents of the detailed description.

For example, a first feature described later in the specification may be formed over or on a second feature, and may include embodiments in which the first and second features are formed in direct contact, and may also include embodiments in which additional features may be formed between the first and second features, such that the first and second features may not be in direct contact. Further, when a first element is described as being coupled or coupled to a second element, the description includes embodiments in which the first and second elements are directly coupled or coupled to each other, as well as embodiments in which one or more additional intervening elements are added to indirectly couple or couple the first and second elements to each other. In addition, references herein to "more than N", "not less than N", or "at least N" each include N by themselves, e.g., "more than two" includes "two" by themselves.

First embodiment (m 2, k 1)

Referring to fig. 1, fig. 1 shows a transmission module 10 according to a first embodiment. The transmission module 10 has a transmission chassis BOX. The transmission housing BOX may be a transmission case, and provides support for a carrier 9, a torque input shaft S0, and the like, which will be described later.

The transmission module 10 comprises a torque input IP, a transmission unit 20 and a torque output OP, the torque of the torque input IP being transmitted via the transmission unit 20 to the torque output OP.

The transmission unit 20 comprises a planet carrier 9, a sun gear set 30 and at least one planet wheel assembly 8.

The carrier 9 is rotatably provided to the transmission housing BOX. In fig. 1, the transmission housing BOX includes a front shaft hole H1 and a rear shaft hole H2 that are coaxial (in fig. 1, the rotation axis X0) and arranged side by side. The carrier 9 is rotatably supported between the front shaft hole H1 and the rear shaft hole H2, for example, by a rotary bearing. The torque input end IP is located at the front side of the front axle hole H1, and the torque output end OP is located at the rear side of the rear axle hole H2. For convenience of description, the front-rear direction is shown in fig. 1 and subsequent drawings.

The sun gear set 30 includes m input sun gears (e.g., as in FIG. 1) and k output sun gears, where m ≧ 2 and k ≧ 1. In fig. 1, m is 2, k is 1, m

input sun gears

1 and 2 are input sun gears, and k output sun gears 7 are output sun gears. The sun gears (including the

input sun gears

1, 2 and the output sun gear 7) in the sun gear set 30 are disposed coaxially with the carrier 9 (in fig. 1, the rotation axis X0) and are rotatable relative to each other. 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 gear and the input sun gear are rotatable relative to each other.

Each planetary gear set 8 includes m input planetary gears (e.g., input

planetary gears

81, 82 in fig. 1) and k output planetary gears (e.g., output planetary gear 87 in fig. 1). The m input planetary gears are respectively meshed with the m input sun gears, for example, in fig. 1, the input planetary gear 81 is meshed with the input sun gear 1, and the input planetary gear 82 is meshed with the input sun gear 2. The k output planets are respectively in mesh with k output sun gears, e.g. in fig. 1, the output planet gear 87 is in mesh with the output sun gear 7. Each planetary gear assembly 8 includes the number of planetary gears which is the sum of the number of input sun gears and the number of output sun gears, that is, the number of input sun gears m + the number of output sun gears k.

The input

planetary gears

81, 82 and the output planetary gear 87 are coaxially secured, and the planetary gear assembly 8 (in fig. 1, around the axis X1) is rotatably provided to the planet carrier 9. The transmission module 10 may include more than two (e.g., two, three, four, or more) planetary wheel assemblies 8, with the more than two planetary wheel assemblies 8 being evenly distributed along the circumferential direction of the sun gear set 30. In fig. 1, the transmission module 10 comprises two planetary wheel assemblies 8, the two planetary wheel assemblies 8 being arranged 180 ° apart with respect to the axis of rotation X0 of the

input sun wheel

1, 2 or of the output sun wheel 7. Alternatively, the planetary wheel assemblies 8 are arranged circumferentially with respect to the axis of rotation X0 of the planet carrier 9, for example, they may be uniformly distributed with respect to the axis of rotation X0 of the planet carrier 9.

At least one of the m input sun gears is provided with a brake Bx, wherein Bx in fig. 1 and subsequent figures represents a brake, and x can be any positive integer such as 1, 2, 3, or 9. The carrier 9 is also provided with a brake B9. In fig. 1, the input sun gear 2 located closest to the torque input end IP (the foremost side in fig. 1) is provided with a brake B2. For example, referring to fig. 1, brake Bx can be divided into a rotatable portion BR and a non-rotatable portion BS, and taking brake B2 as an example, the non-rotatable portion BS of brake B2 can be directly or indirectly connected to transmission housing Box, and the rotatable portion BR of brake B2 is directly or indirectly connected to input sun gear 2. When the brake Bx is in the braking state (or stated as brake Bx is engaged), the respective input sun gear 2 or carrier 9 configured with the brake Bx is prevented from rotating, whereas when the brake Bx is not activated (or stated as brake Bx is disengaged), the respective input sun gear 2 or carrier 9 configured with the brake Bx is allowed to rotate.

Each of the input sun gears 1 and 2 (i.e., each of the m input sun gears) is also detachably connected to the torque input end IP via a clutch Cx. Cx in fig. 1 and subsequent figures represents a clutch, and x can be any positive integer such as 1, 2, 3, or 9, etc. In fig. 1, the input sun gear 2 located closest to the torque input end IP (the foremost side in fig. 1) is provided with a brake B2. For example, referring to fig. 1, the clutch Cx can be divided into a driving portion CA and a driven portion CI, and taking the clutch C2 as an example, the driving portion CA of the clutch C2 is directly or indirectly connected to the torque input IP, and the driven portion CI of the clutch C2 is directly or indirectly connected to the input sun gear 2. In the latter variant embodiment, the planet carrier 9 can also be provided with a clutch C9, in other words the planet carrier 9 is also connected to the torque input IP in a clutchable manner via a clutch C9. When the clutch Cx is in the engaged state (or stated otherwise, the clutch Cx is engaged), torque is transmitted from the torque input IP to the respective

input sun gear

1, 2 or carrier 9 provided with the clutch Cx, whereas when the clutch Cx is not activated (or stated otherwise, the clutch Cx is disengaged), the transmission of torque to the respective input sun gear 2 or carrier 9 provided with the brake Bx is interrupted. The clutch Cx and the brake Bx may constitute a shift actuator. The clutch Cx may be, for example, a multi-plate wet clutch, and the brake B2 may be configured similarly to the clutch Cx, for example.

The transmission module 10 is configured to select two elements from m +1 (three in fig. 1) elements of the m input sun gears 1, 2 and the carrier 9 such 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 braked state, or such that the clutch Cx of the two elements is in an engaged state, thereby forming one power transmission route of the transmission module.

In fig. 1, the torque input IP includes a torque input shaft S0. Each clutch Cx includes an inner hub and an outer drum that are clutchably connected. Taking clutch C2 as an example, which is a multi-plate wet clutch, the driving part CA of clutch C2 includes an inner hub (formed by barrel S01 in fig. 1) having external splines, and a first friction element having internal splines, which can be drivingly connected to the inner hub S01 by the engagement of the internal and external splines; the driven portion CI of the clutch C2 includes an outer drum (in fig. 1, constituted by the tube 21) having an internal spline, and also includes a second friction element having an external spline, which can be drivingly connected to the outer drum 21 by the mating of the external spline and the internal spline; the inner hub S01 and the outer drum 21 are in the form of a coaxial tube pair, and a first friction element having an internal spline and a second friction element having an external spline are arranged between the inner hub S01 and the outer drum 21, and the friction elements are pressed to be fitted to each other to transmit torque. In this manner, the inner hub S01 of the clutch C2 and the outer drum 21 are clutchably connected.

The input sun gears 1, 2 and the torque input shaft S0 are connected to one and the other of the inner hub and the outer drum of the corresponding clutch, respectively, that is, one clutch may be configured such that the input sun gear is connected to the inner hub of the clutch and the torque input shaft S0 is connected to the outer drum of the clutch, or the input sun gear is connected to the inner hub of the clutch and the torque input shaft S0 is connected to the inner hub of the clutch. In this manner, the input sun gears 1, 2 are clutchably connected to the torque input shaft S0 through clutches C1, C2. In fig. 1, a clutch C1 is provided between the input sun gear 1 and the torque input shaft S0. In fig. 1, torque input shaft S0 has a tubular shaft or barrel S01 along axis of rotation X0, barrel S01 connects or forms the outer drum of clutch C1, while input sun gear 1 has barrel 11 extending along axis of rotation X0, barrel 11 connects or forms the inner hub of clutch C1, clutch C1 is comprised of barrel S01 of torque input shaft S0 and barrel 11 of input sun gear 1, and barrel S01 is wrapped around barrel 11. For clutch C1, the input sun gear 1 connects the inner hub of clutch C1, and the torque input shaft S0 connects the outer drum of clutch C1. Similarly, as shown in FIG. 1, a clutch C2 is provided between the input sun gear 2 and the torque input shaft S0, and in clutch C2, the barrel 21 of the input sun gear 2 is sleeved over the barrel S01 of the torque input shaft S0. Barrel 21 connects to or forms the outer drum of clutch C2, and barrel S01 connects to or forms the inner hub of clutch C2. For clutch C2, the input sun gear 2 connects the outer drum of clutch C2, while the torque input shaft S0 connects the inner hub of clutch C1. It will be appreciated that the tube constituting the clutch inner hub or outer drum is not limited to a hollow tube, for example, the tube 11 may not be a hollow tube as shown in fig. 1 but may be a solid shaft.

In fig. 1, in the sun gear set 30, the input sun gear 1 and the input sun gear 2 are held coaxially (rotation axis X0) by a tube pair S12 fitted into each other and are rotatable relative to each other. Input sun gear 1 has a tube 12 in the shape of a solid shaft extending along the rotation axis X0, input sun gear 2 has a tube 22 extending along the rotation axis X0, and tube 22 of input sun gear 2 is fitted over tube 12 of input sun gear 1, for example, a rotational bearing may also be provided between tube 22 and tube 12. Thus, the input sun gear 1 and the input sun gear 2 are held coaxially and rotatable relative to each other. The input sun wheel 1 and the output sun wheel 3 are also held coaxially (rotation axis X0) and rotatable relative to each other by a tube pair S17 nested one inside the other. The output sun gear 3 has a tube 71 extending rearward along the rotation axis X0, and a solid shaft-like tube 72 is connected to the rear side of the tube 71. The front end of the pipe tube 12 of the input sun gear 1 passes through the pipe tube 22 of the input sun gear 2 and is connected with the pipe tube 11, and the rear end of the pipe tube 12 of the input sun gear 1 is inserted into the pipe tube 71 of the output sun gear 3 to form a pipe tube pair S17. Hereinafter, for the sake of more clear description, the tubes (e.g., tube 12, tube 72, etc.) shown as solid shafts are all referred to as connecting shafts of the respective sun gears (e.g., input sun gear 1, output sun gear 7, etc.), and the tubes (e.g., tube 22, tube 71, etc.) shown as hollow cylinders are all referred to as tubular shafts of the respective sun gears (e.g., input sun gear 2, output sun gear 7). It is possible that some of the sun gears in the sun gear set 30 are held coaxially and rotatable relative to each other by such pairs of tubes that are nested within each other.

Fig. 1 shows a schematic diagram of a four-speed transmission module in which m is 2, k is 1 and only one input sun gear 2 is provided with a brake B2.

In the transmission module 10 of fig. 1, each planetary gear assembly 8 includes three

planetary gears

81, 82 and 87, and the

planetary gears

81, 82 and 87 are fixedly connected together, coaxially and synchronously rotate, and are rotatably mounted on the planetary carrier 9 through a planetary shaft 89.

The input sun gears 1, 2 are arranged alongside the output sun gear 7 and have the same axis of rotation 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 journalled by its tubular shaft to a connecting shaft of the input sun gear 1. The connecting shafts (or tubular shafts) of the input sun gears 1, 2 project out of the center hole 93 of the carrier 9 in the direction of the input sun gear side. The side of the output sun gear 7 which is connected axially remote from the input sun gear 1 projects out of the central opening 94 of the planet carrier 9. Relative rotation is possible between the input sun gears 1, 2, between the output sun gear 7 and the

input sun gear

1 or 2, and between the

input sun gear

1, 2 or the output sun gear 7 and the carrier 9. Input sun 1 meshes with planet gears 81, input sun 2 meshes with planet gears 82, and planet gears 87 meshes with output sun 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 carrier 9 and the transmission frame Box.

The number of shift module gears of fig. 1 is calculated as follows:

c1 and B9 are jointed to form a power transmission route which is 1 gear;

c2 and B9 are jointed to form a power transmission route which is 1 gear;

c1 and B2 are jointed to form a power transmission route which is 1 gear;

c1 and C2 are jointed to form a power transmission route, the transmission ratio is 1, and the speed is 1 gear;

total gear number:

n＝4

the point of engagement of the sun with a respective planet is referred to as the node. In particular, in the embodiment shown in fig. 1, the pitch circle radius of the gear pair formed by the input sun gear 1 and the planetary gears 81 is R1, the pitch circle radius of the gear pair formed by the input sun gear 2 and the planetary gears 82 is R2, the pitch circle radius of the gear pair formed by the output sun gear 7 and the planetary gears 87 is R7, and the pitch circle radius is the center distance, the number of teeth, and the number of teeth. R1 < R2 < R7 may be provided, where clutch C1 of input sun gear 1 is engaged and brake B2 of input sun gear 2 is engaged, and reverse gear may be established.

Second embodiment (m 2, k 1)

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

Fig. 2 shows a schematic diagram of a five-speed transmission module 10a in which m is 2 and k is 1, and the input sun gears 1 and 2 are each provided with a brake. The same reference numerals and parts of the same reference numerals are used for the same or similar elements in the previous embodiments, and the descriptions of the same technical contents are optionally omitted. For the description of the omitted portions, reference may be made to the foregoing embodiments, and the description of the present embodiment and the following embodiments is not repeated.

In the transmission module 10a of fig. 2, two planetary wheel assemblies 8 are equispaced 180 ° with respect to the axis of rotation X0 of the

input sun wheel

1 or 2, each planetary wheel assembly 8 comprising three

planetary gears

81, 82 and 87. The planet gears 81, 82 and 87 are fixedly connected into a whole, coaxially and synchronously rotate, and are rotatably arranged on the planet carrier 9 through a planet shaft 89.

The input sun gears 1, 2 are arranged alongside the output sun gear 7 and have the same axis of rotation 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 journalled by its tubular shaft to a connecting shaft of the input sun gear 1. The connecting shafts (or tubular shafts) of the input sun gears 1, 2 project out of the center hole 93 of the carrier 9 in the direction of the input sun gear side, and the connecting shaft of the output sun gear 7 projects out of the center hole 94 of the carrier 9 in the direction of the side away from the input sun gear 1. Relative rotation is possible between the input sun gears 1, 2, between the output sun gear 7 and the

input sun gear

1 or 2, and between the

input sun gear

In fig. 2, the stopper B1 is located on the rear side of the rear shaft 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 a tubular shaft, the input sun gear 1 and the output sun gear 7 can rotate relatively, and the output sun gear 7 outputs torque outwards through the tubular shaft. A brake B1 is provided between the extension shaft 13 of the input sun gear 1 and the transmission frame Box, so that it is possible to facilitate the arrangement of the brake B1 between the input sun gear 1 and the transmission frame Box. When brake B1 is engaged, input sun gear 1 is braked, preventing its rotation; when the brake B1 is disengaged, the input sun gear 1 and the transmission frame Box can rotate relative to each other. The brake of some or all of the m input sun gears may be located on the rear side of the rear axle hole H2, depending on the arrangement requirements.

The number of shift module gears of fig. 2 is calculated as follows:

c1 and B9 are jointed to form a power transmission route which is 1 gear;

c2 and B9 are jointed to form a power transmission route which is 1 gear;

c1 and B2 are jointed to form a power transmission route which is 1 gear;

c2 and B1 are jointed to form a power transmission route which is 1 gear;

total gear number:

n＝5

in particular, in the embodiment shown in fig. 2, the pitch circle radius of the gear pair formed by the input sun gear 1 and the planetary gears 81 is R1, the pitch circle radius of the gear pair formed by the input sun gear 2 and the planetary gears 82 is R2, and the pitch circle radius of the gear pair formed by the output sun gear 7 and the planetary gears 87 is R7. R1 < R2 < R7 may be provided. At this time, when C1 and B2 are engaged, reverse gear is formed; and when C2 and B1 are engaged, an overdrive gear is formed.

Fig. 3 shows a transmission 100 in which two four-speed transmission modules 10 of fig. 1 are connected in series. In the transmission 100, the torque output end OP1 of the previous transmission module 10 is in driving connection with the torque input end IP2 of the subsequent transmission module. In fig. 3, the torque input ends IP1, IP2 of the transmission modules 10 are torque input shafts, the torque output ends OP1, OP2 are torque output shafts extending from the center of the output sun gear 7 to the rear side, and the torque output shaft of the previous transmission module 10 is connected to the torque input shaft of the next transmission module.

The number of gears of the transmission 100 shown in fig. 3 is calculated as follows:

n＝4×4＝16

although fig. 3 shows a case where two transmission modules 10 are connected in series, the transmission may include more than two transmission modules, and the number of gears of the transmission is a product of the numbers of gears of the transmission modules included therein.

The transmission may also comprise different transmission modules. Fig. 4 shows a transmission 100a in which the four-speed transmission module 10 of fig. 1 and the five-speed transmission module 10a of fig. 2 are connected in series.

In fig. 4, the tubular shaft of the output sun gear of the previous shift module 10a (or the torque output end OPa of the five-speed shift module 10 a) is connected with the transfer gear D4, and the torque is transmitted to the outside through the transfer gear D4, and the torque input shaft of the subsequent shift module 10 (or the torque input end IP2 of the four-speed shift module 10) is connected with the transfer gear D1. The transmission device is further provided with a switching intermediate shaft SI, the switching intermediate shaft SI is parallel to torque input shafts of the two speed change modules, the switching intermediate shaft SI is fixedly connected with two switching gears D2 and D3, the switching gear D1 is meshed with the switching gear D2, and the switching gear D3 is meshed with the switching gear D4. This arrangement can facilitate bypassing of the brake B1, particularly in the case where the brake B1 is provided on the rear side of the rear shaft hole H2.

The number of gears of the transmission 100a shown in fig. 4 is calculated as follows:

n＝5×4＝20

third embodiment (m 2, k 1)

As mentioned before, the planet carrier 9 may also be provided with a clutch. In the third embodiment, at least, unlike the second embodiment, the carrier 9 is provided with a clutch C9.

Fig. 5 shows a schematic diagram of a transmission module 10b in which m is 2 and k is 1, and the input sun gears 1 and 2 and the carrier 9 are both provided with brakes and clutches.

In the transmission module 10b of fig. 5, two planetary wheel assemblies 8 are equispaced 180 ° with respect to the axis of rotation X0 of the

input sun wheel

1 or 2, each planetary wheel assembly 8 comprising three

planetary gears

input sun gear

1 or 2, and between the

input sun gear

1, 2 or the output sun gear 7 and the carrier 9. Input sun 1 meshes with planet gears 81, input sun 2 meshes with planet gears 82, and planet gears 87 meshes with output sun 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 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 carrier 9 and the transmission frame Box.

In fig. 5, the brakes B1, B2, B9 of the input sun gear 1, the input sun gear 2, and the carrier 9 are all located on the front side of the front shaft hole H1.

A clutch C9 is provided between the carrier 9 and the torque input shaft S0. In fig. 5, torque input shaft S0 includes a tube S02 disposed about and coaxial with tube S01, tube S02 is the inner hub of clutch C9, planet carrier 9 has a tube 91 extending along rotational axis X0, tube 91 is the outer drum of clutch C9, clutch C9 is composed of tube S02 of torque input shaft S0 and tube 91 of planet carrier 9 and the friction elements therebetween, tube 91 is sleeved over tube S02, the friction elements having internal splines are engaged with the external splines of tube S02, and the friction elements having external splines are engaged with the internal splines of tube 91. A friction element with internal splines and a friction element with external splines are arranged between barrel S02 and barrel 91, the friction elements being pressed against each other to transmit torque.

The planet carrier 9 and the input sun gear 2 are held coaxially (rotation axis X0) and relatively rotatable with respect to each other by a tube pair S29 that are nested with each other. The planet carrier 9 has a tube 92 extending along the rotation axis X0, the tube 92 of the planet carrier 9 being fitted over the tube 22 of the input sun wheel 2, for example, a rotational bearing may also be provided between the tube 92 and the tube 22. In this way, the planet carrier 9 and the input sun gear 2 are thus held coaxially with the input sun gear 1 and are rotatable relative to each other. The tube 92 of the planet carrier 9 passes through the front shaft hole H1 and is connected with the tube 91.

Fourth embodiment (m 2, k 1)

Fig. 6 is a schematic diagram of a transmission module 10c in which m is 2 and k is 1, and the input sun gears 1 and 2 and the carrier 9 are both provided with a brake and a clutch. Fig. 6 shows a fourth embodiment which differs from the third embodiment of fig. 5 at least in that the power transmission path from the torque input shaft S0 to the carrier 9 differs.

The planet carrier 9 is connected with a first switching gear T91, and the first switching gear T91 is in meshing transmission with a second switching gear T92. The torque input shaft S0 is provided with an input transfer gear T0, and the input transfer gear T0 is in meshed transmission with a third transfer gear T93.

A clutch C9 is provided between the second transfer gear T92 and the third transfer gear T93. The second transfer gear T92 has a barrel S92 extending along its rotational axis X2, the barrel S92 is connected to or constitutes the outer drum of the clutch C9, the third transfer gear T93 has a barrel S93 extending along its rotational axis X2, the barrel S93 is connected to or constitutes the inner hub of the clutch C9, and the barrel S92 is sleeved on the barrel S93. For example, a first friction element having internal splines is engaged with the external splines of the internal hub formed by barrel S93, and a second friction element having external splines is engaged with the internal splines of the external drum formed by barrel S92. A first friction element with an internal spline and a second friction element with an external spline are arranged between the inner hub formed by the barrel S93 and the outer drum formed by the barrel S92, and the friction elements are pressed to be attached to each other to transmit torque.

The carrier 9 is clutchably connected to the torque input shaft S0 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 this order.

In the shift module 10c of fig. 6, a carrier rotation shaft SX2 is provided in parallel with the torque input shaft S0. The carrier transfer shaft SX2 is provided with transfer gears T92 and T93, respectively. The transfer gear T93 meshes with the transfer gear T0, and the transfer gear T92 meshes with the transfer gear T91 connected to the carrier 9. The clutch C9 is disposed between the transfer gear T92 and the transfer gear T93. When clutch C9 is engaged, torque may be transferred between transfer gear T93 and transfer gear T92; when the clutch C9 is disengaged, relative rotation is possible between the transfer gear T93 and the transfer gear T92.

A brake B9 is provided between the transfer gear T92 and the transmission housing Box, the tube S92 is connected to or constitutes an inner hub of the brake B9, and an outer drum of the brake B9 is connected to the transmission housing Box. When the brake B9 is engaged, the transfer gear T92 is braked and prevented from rotating, the transfer gear T91 meshing with the transfer gear T92 is also prevented from rotating, and the carrier 9 connected to the transfer gear T91 is also prevented from rotating; when the brake B9 is disengaged, the part prevented from rotating and the transmission frame Box can rotate relatively.

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

In fig. 6, the input sun gear 1 has an extension shaft in a direction toward one side of the output sun gear 7, the output sun gear 7 is fitted to the extension shaft of the input sun gear 1 through a tubular shaft thereof, and the input sun gear 1 and the output sun gear 7 are rotatable relative to each other. The output sun wheel 7 outputs torque outwards 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 brake B1 is engaged, input sun gear 1 is braked, preventing its rotation; when the brake B1 is disengaged, the input sun gear 1 and the transmission frame Box can rotate relative to each other.

The configuration of fig. 6 can facilitate the arrangement of the clutch Cx and the brake Bx.

Fifth embodiment (m ═ 3, k ═ 1)

Fig. 7 shows a schematic diagram of a transmission module 10d in which m is 3 and k is 1, and the input sun gears 1, 2, 3 and the carrier 9 are all provided with brakes and clutches.

In the transmission module 10d of fig. 7, two planetary wheel assemblies 8 are equispaced 180 ° with respect to the axis of rotation X0 of the

input sun wheel

1, 2 or 3, each planetary wheel assembly 8 comprising four

planetary gears

81, 82, 83 and 87. The

planet wheels

81, 82, 83 and 87 are fixedly connected into a whole, coaxially and synchronously rotate, and are rotatably arranged on the planet carrier 9 through a planet shaft 89.

The input sun gears 1, 2, 3 are arranged alongside the output sun gear 7 and have the same axis of rotation 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 remote from the output sun gear 7. The input sun gear 3 is journalled by its tubular shaft to the tubular shaft of the input sun gear 2, and the input sun gear 2 is journalled by its tubular shaft to the connecting shaft of the input sun gear 1, wherein the input sun gear farthest from the output sun gear is journalled by its tubular shaft to the tubular shaft (or connecting shaft) of the input sun gear adjacent to the output sun gear. The tubular shafts (or connecting shafts) of the input sun gears 1, 2, 3 project out of the center hole 93 of the carrier 9 in the direction of the input sun gear 3 side. The side of the output sun gear 7 which is connected axially remote from the input sun gear 3 projects out of the central opening 94 of the planet carrier 9. Relative rotation is possible between the

input sun gear

1, 2, 3, between the output sun gear 7 and the

input sun gear

1, 2 or 3, and between the

input sun gear

1, 2, 3 or the output sun gear 7 and the planet carrier 9. Input sun 1 meshes with planet gears 81, input sun 2 meshes with planet gears 82, input sun 3 meshes with planet gears 83, and planet gears 87 meshes with output sun 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 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 carrier 9 and the transmission frame Box.

In fig. 7, the brakes B1, B2, B3, B9 of the input sun gears 1, 2, 3 and the carrier 9 are all located on the front side of the front shaft hole H1.

In fig. 7, clutches C1, C2, C3 and C9 are provided between the input sun gears 1, 2, 3 and the carrier 9, respectively, and the torque input shaft S0, so as to be clutchably connected to the torque input shaft S0.

Sixth embodiment (m ═ 3, k ═ 1)

Fig. 8 is a schematic diagram of a transmission module 10e in which m is 3 and k is 1, and the input sun gears 1, 2, and 3 and the carrier 9 are all provided with a brake and a clutch. Fig. 8 shows a sixth embodiment which differs from the fifth embodiment of fig. 7 at least in that the power transmission path from the torque input shaft S0 to the carrier 9 and the input sun gear 3 differs.

The power transmission path of the carrier 9 in fig. 8 is similar to that in fig. 6. In fig. 8, the planet carrier 9 is connected with a first transfer gear T91, and the first transfer gear T91 is in meshing transmission with a second transfer gear T92. The torque input shaft S0 is provided with an input transfer gear T0, and the input transfer gear T0 is in meshed transmission with a third transfer gear T93. A clutch C9 is provided between the second transfer gear T92 and the third transfer gear T93. The carrier 9 is clutchably connected to the torque input shaft S0 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 this order.

In fig. 8, the input sun gear 3 is connected with a first transfer gear T31, and the first transfer gear T31 is in meshing transmission with a second transfer gear T32. The torque input shaft S0 is provided with an input transfer gear T0, and the input transfer gear T0 is in meshed transmission with a third transfer gear T33.

A clutch C3 is provided between the second transfer gear T32 and the third transfer gear T33. The second transfer gear T32 has a barrel S32 extending along its rotational axis X3, the barrel S32 is connected to or constitutes the outer drum of the clutch C3, the third transfer gear T33 has a barrel S33 extending along its rotational axis X3, the barrel S33 is connected to or constitutes the inner hub of the clutch C3, and the barrel S32 is sleeved on the barrel S33. For example, a first friction element having internal splines is engaged with the external splines of barrel S33 constituting the internal hub of clutch C3, and a second friction element having external splines is engaged with the internal splines of barrel S32 constituting the external drum of clutch C3. A first friction element having internal splines and a second friction element having external splines are arranged between barrel S33 and barrel S32, the friction elements being pressed into engagement with each other to transmit torque.

The input sun gear 3 is clutchably connected to the torque input shaft S0 through a first transfer gear T31, a second transfer gear T32, a clutch C3, a third transfer gear T33, and an input transfer gear T0 in this order.

In fig. 8, the other input sun gears 1 and 2 are not connected to the transfer gear. That is, in fig. 8, the first transfer gear T31 is connected to one of the three sun gears 3, and a power transmission path is formed by the transfer gear. It is possible that a part of the m input sun gears is connected with a first transfer gear, as shown in fig. 8. The first transfer gear may be connected to all of the m input sun gears. It is also possible that none of the m input sun gears receive power through the transfer gear, for example, as shown in fig. 1, 2 and 5.

In the shift module 10e of fig. 8, a carrier rotation shaft SX2 is provided in parallel with the torque input shaft S0. A carrier transfer shaft SX2 is provided with transfer gears T92 and T93, respectively. The transfer gear T93 meshes with the transfer gear T0, and the transfer gear T92 meshes with the transfer gear T91 connected to the carrier 9. The clutch C9 is disposed between the transfer gear T92 and the transfer gear T93. When clutch C9 is engaged, torque may be transferred between transfer gear T93 and transfer gear T92; when the clutch C9 is disengaged, relative rotation is possible between the transfer gear T93 and the transfer gear T92. A brake B9 is provided between the transfer gear T92 and the transmission frame Box. When the brake B9 is engaged, the transfer gear T92 is braked and prevented from rotating, the transfer gear T91 meshing with the transfer gear T92 is also prevented from rotating, and the carrier 9 connected to the transfer gear T91 is also prevented from rotating; when the brake B9 is disengaged, the part prevented from rotating and the transmission frame Box can rotate relatively.

An input sun wheel coupling 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 wheel coupling shaft SX3, respectively. The switching gear T33 is meshed with the switching gear T0, the switching gear T32 is meshed with the switching gear T31 connected with the input sun gear 3, a clutch C3 is arranged between the switching gears T33 and T32, when the clutch C3 is connected, torque can be transmitted between the switching gear T33 and the switching gear T32, when the clutch C3 is disconnected, the switching gear T33 and the switching gear T32 can rotate relatively, a brake B3 is arranged between the switching gear T32 and the transmission frame Box, when the brake B3 is connected, the switching gear T32 is braked and prevented from rotating, the switching gear T31 meshed with the switching gear T32 is also prevented from rotating, and the input sun gear 3 connected with the switching gear T31 is also prevented from rotating; when the brake B3 is disengaged, the part prevented from rotating and the transmission frame Box can rotate relatively.

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

In fig. 8, the input sun gear 1 has an extending shaft in a direction toward one side of the output sun gear 7, the output sun gear 7 is fitted to the extending shaft of the input sun gear 1 through its tubular shaft, and the input sun gear 1 and the output sun gear 7 are relatively rotatable, wherein the input sun gear 1 is the input sun gear closest to the output sun gear 7. The output sun wheel 7 outputs torque outwards 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 brake B1 is engaged, input sun gear 1 is braked, preventing its rotation; when the brake B1 is disengaged, the input sun gear 1 and the transmission frame Box can rotate relative to each other.

The configuration of fig. 8 can facilitate the arrangement of the clutch Cx and the brake Bx.

Seventh embodiment (m 2, k 2)

Fig. 9 shows a schematic diagram of a transmission module 10f in which m is 2 and k is 2, and the input sun gears 1 and 2 and the carrier 9 are both provided with brakes and clutches. In the seventh embodiment of fig. 9, the two

output sun wheels

6, 7 are held coaxially (rotation axis X0) and rotatable relative to each other by a tube pair S67 that are nested into each other.

In the transmission module 10f of fig. 9, two planetary wheel assemblies 8 are equispaced 180 ° with respect to the axis of rotation X0 of the

input sun wheel

1 or 2, each planetary wheel assembly 8 comprising four

planetary gears

81, 82, 87 and 86. The

planet wheels

81, 82, 87 and 86 are fixedly connected into a whole, coaxially and synchronously rotate, and are rotatably arranged on the planet carrier 9 through a planet shaft 89.

The input sun gears 1, 2 are arranged alongside the output sun gears 7, 6 and have the same axis of rotation 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 journalled by its tubular shaft to a connecting shaft of the input sun gear 1. The connecting shafts (or tubular shafts) of the input sun gears 1, 2 project out of the center hole 93 of the carrier 9 in the direction of the input sun gear 2 side. The output sun gear 6 is disposed 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 journalled by its tubular shaft to a connecting shaft of the output sun gear 7. In other words, the input sun gear remote from the output sun gear is journalled by its tubular sleeve to the adjacent connecting shaft of the input sun gear close to the output sun gear, and the output sun gear remote from the input sun gear is journalled by its tubular sleeve to the adjacent connecting shaft of the output sun gear close to the input sun gear. The connecting shafts (or tubular shafts) of the output sun gears 7, 6 project out of the center hole 94 of the carrier 9 on the side away from the input sun gear 1, and form two torque output shafts SP7, SP6, respectively. The number of output sun gears is the same as the number of torque output shafts. Relative rotation is possible between the input sun gears 1, 2, between the output sun gears 7, 6 and the

input sun gear

1 or 2, and between the input sun gears 1, 2, the output sun gears 7, 6 and the carrier 9. Input sun 1 meshes with planet gears 81, input sun 2 meshes with planet gears 82, planet gears 87 meshes with output sun 7, and planet gears 86 meshes with output sun 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 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 carrier 9 and the transmission frame Box.

Eighth embodiment (m ═ 3, k ═ 2)

Fig. 10 shows a schematic diagram of a transmission module 10g in which m is 3 and k is 2, and the input sun gears 1, 2, 3 and the carrier 9 are all provided with brakes and clutches.

In the transmission module 10g of fig. 10, two planetary wheel assemblies 8 are equispaced 180 ° with respect to the axis of rotation X0 of the

input sun wheel

1, 2 or 3, each planetary wheel assembly 8 comprising five

planetary wheels

81, 82, 83, 87 and 86. The

planet wheels

81, 82, 83, 87 and 86 are fixedly connected into a whole, coaxially and synchronously rotate, and are rotatably arranged on the planet carrier 9 through a planet shaft 89.

The input sun gears 1, 2, 3 are arranged side by side with the output sun gears 7, 6 and have the same axis of rotation 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 fitted to the tubular shaft of the input sun gear 2 through its tubular shaft, and the input sun gear 2 is fitted to 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 each protrude out of the center hole 93 of the carrier 9 in the direction of the input sun gear 3 side. The output sun gear 6 is disposed 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 journaled on a connecting shaft of the output sun gear 7 through a tubular shaft thereof. In other words, the input sun gear remote from the output sun gear is journalled by its tubular sleeve to the adjacent connecting shaft of the input sun gear close to the output sun gear, and the output sun gear remote from the input sun gear is journalled by its tubular sleeve to the adjacent connecting shaft of the output sun gear close to the input sun gear. The connecting shafts (or tubular shafts) of the output sun gears 7, 6 project out of the center hole 94 of the carrier 9 on the side away from the input sun gear 1, and form two torque output shafts SP7, 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 relatively. Input sun 1 meshes with planet gears 81, input sun 2 meshes with planet gears 82, input sun 3 meshes with planet gears 83, planet gears 87 meshes with output sun 7, and planet gears 86 meshes with output sun 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 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 carrier 9 and the transmission frame Box.

According to the present invention, in the transmission module of fig. 5 to 10, each input sun gear or planet carrier is connected to 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 the planet carrier constitute optional m +1 elements. The gear formation of the gear change module of fig. 5 to 10 is as follows:

since each input sun gear or carrier is provided with a clutch Cx and a brake Bx, the number of the clutches Cx or the brakes Bx is: m +1

The number of gears for a certain output sun gear is calculated as follows: the clutch Cx (having one of the input sun gear or the carrier) connected to any one of the m +1 elements is engaged

A possible option) while selecting the engagement of the brake Bx connected to another element than the one previously described (the clutch Cx and the brake Bx connected to the same element may not be engaged at the same time, and therefore, there is

One possible selection). According to the above requirement, one Cx and one Bx are engaged to form a power transmission line, i.e. a gear. The transmission ratio of the power transmission line formed by the engagement of different Cx or different Bx can be made different according to actual needs.

The number of choices for the output sun gear is

And (4) respectively.

Any two of the clutches Cx, to which the input sun gear or the carrier is connected, are selected to form the gear ratio 1.

Thus, the total number of gears of the transmission module of fig. 5 to 10 can be calculated by the following formula:

the number of gears in the transmission module of fig. 5 or 6 (where m is 2 and k is 1) is calculated as follows:

the number of gears in the transmission module of fig. 7 or 8 (where m is 3 and k is 1) is calculated as follows:

the number of gears in the transmission module of fig. 9 (where m is 2 and k is 2) is calculated as follows:

the number of gears in the transmission module of fig. 10 (where m is 3 and k is 2) is calculated as follows:

thus, for a six speed transmission, only the embodiment of FIG. 5 or FIG. 6 need be employed to achieve six forward speed ratios and one reverse speed ratio. For a ten speed transmission, only the embodiment of FIG. 7 or FIG. 8 need be employed to achieve 10 forward speed ratios and 3 reverse speed ratios.

Therefore, adopt the utility model discloses a speed change module or speed change gear can make the derailleur axial dimension who keeps off the position many shorten greatly. Moreover, the structure is simpler and the weight is lighter. Complex nesting between the traditional planet row and the related components of the planet row is also avoided, so that the defects of complex structure and difficult processing of the related components of the planetary gear mechanism are eliminated.

The utility model discloses a speed change gear can also be called as multispeed, no ring gear's planetary gear speed change gear, can be applied to vehicles etc..

In the above embodiment, all the input sun gears and all the output sun gears are arranged side by side and have the same rotational axis as the carrier, the input sun gears and the output sun gears being adjacent. The torque input shaft has the same axis of rotation as the input sun gear and the carrier. The input sun gear far away from the output sun gear is sleeved on the adjacent connecting shaft (or tubular shaft) of the input sun gear close to the output sun gear through the tubular shaft, and the connecting shafts (or tubular shafts) of all the input sun gears extend out of the central hole of the planet carrier towards one side of the input sun gear.

When more than one output sun gear is arranged, the output sun gear far away from the input sun gear is sleeved on the adjacent connecting shaft (or tubular shaft) of the output sun gear close to the input sun gear through the tubular shaft, and the connecting shafts (or tubular shafts) of all the output sun gears extend out of the central hole of the planet carrier towards one side of the output sun gear.

All the input sun gears and all the output sun gears are meshed with all the planet gears 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 carrier 9 and the transmission frame Box. Different embodiments can be formed depending on whether the brake Bx is added to the input sun gear and the clutch Cx is added to the carrier.

The clutch Cx includes a driving portion that is directly or indirectly connected to the torque input shaft S0 and a driven portion that is directly or indirectly connected to the input sun gear or the carrier. When a certain clutch Cx is engaged, torque is transmitted from the torque input shaft S0 to the corresponding input sun gear or carrier; conversely, when a certain clutch Cx is disengaged, the transmission of torque is interrupted. A brake Bx is arranged between each input sun gear, the planet carrier and the transmission frame Box or is arranged between each input sun gear, the planet carrier and the transmission frame Box.

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

In fig. 3, the transmission device includes two transmission modules, the torque output shaft of the former transmission module is connected with the torque input shaft of the latter transmission module, the number of speed ratios set in each transmission 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 far away from the output sun gear is sleeved on a connecting shaft of the other input sun gear through a tubular shaft of the input sun gear. Meanwhile, each speed changing module is provided with two planet wheel assemblies which are uniformly distributed at an angle of 180 degrees relative to the rotation axis of the input sun wheel, and each planet wheel assembly is provided with three planet wheels which are respectively meshed with the two input sun wheels and one output sun wheel one by one. The input sun gear near the torque input shaft S0 is provided with a clutch Cx and a brake Bx, the other input sun gear is provided with the clutch Cx, and the carrier is provided with the brake Bx.

In fig. 4, the transmission includes two transmission modules with their torque input shafts arranged in parallel or coincident, and the speed ratio settings of each transmission module are 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 a connecting shaft of the other input sun gear through a tubular shaft of the input sun gear. Meanwhile, each speed changing module is provided with two planet wheel assemblies which are uniformly distributed at 180 degrees relative to the rotation axis of the input sun wheel, and each planet wheel assembly is provided with three planet wheels which are respectively meshed with the two input sun wheels and one output sun wheel one by one. Two input sun gears of the previous speed changing module are both provided with a clutch Cx and a brake Bx, and the planet carrier is provided with the brake Bx. An extending shaft is arranged in the direction from the input sun gear close to the output sun gear, the output sun gear is sleeved on the extending shaft of the input sun gear through a tubular shaft, the input sun gear and the output sun gear can rotate relatively, and a brake is arranged on the extending shaft of the input sun gear, so that the brake can be conveniently arranged on the input sun gear. A transfer gear D4 is connected to the tubular shaft of the output sun gear, and torque is transmitted rearward through the transfer gear D4. The difference between the latter speed-changing module and the former speed-changing module is that: the input sun gear, which is adjacent to the output sun gear, does not have a brake Bx, so that the input sun gear does not need to have an extension shaft in the direction of the output sun gear, and the output sun gear does not need to have a tubular shaft. The rest of the structural arrangement is similar to the previous speed changing module. The transmission device is provided with a switching intermediate shaft, the switching intermediate shaft is parallel to torque input shafts of two speed change modules, two switching gears D3 and D2 are fixedly connected to the switching intermediate shaft, a switching gear D1 is connected to a torque input shaft S0 of the latter speed change module, the switching gear D4 is meshed with a switching gear D3, and a switching gear D2 is meshed with a switching gear D1, so that a brake on an extension shaft of an input sun gear can be avoided.

In fact, each transmission module can be used upside down, and a large transmission device combined by a plurality of transmission modules can also be used upside down.

Although the present invention has been described with reference to the preferred embodiments, it is not intended to limit the present invention, and those skilled in the art can make various changes and modifications without departing from the spirit and scope of the present invention. For example, the modifications in the various embodiments described above may be combined as appropriate.

Any modification, equivalent changes and modifications of the above embodiments according to the technical spirit of the present invention, which do not depart from the technical scope of the present invention, fall within the protection scope defined by the claims of the present invention.

Claims

1. A transmission module having a transmission frame including a torque input, a transmission unit and a torque output, torque of the torque input being transmitted to the torque output via the transmission unit, characterized in that the transmission unit comprises:

a planet carrier rotatably provided to the transmission frame;

the sun wheel set comprises m input sun wheels and k output sun wheels, each sun wheel in the sun wheel set and the planet carrier are coaxially arranged and can rotate relative to each other, wherein m is more than or equal to 2, and k is more than or equal to 1; and

at least one planetary gear assembly, each planetary gear assembly comprising m input planetary gears respectively and correspondingly meshed with the m input sun gears and k output planetary gears respectively and correspondingly meshed with the k output sun gears, the input planetary gears and the output planetary gears being coaxially and fixedly connected, the planetary gear assembly being rotatably arranged on the planetary carrier;

at least one of the input sun gears is provided with a brake, and each of the input sun gears is respectively connected with the torque input end in a clutchable way through 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 of the m input sun gears and the planet carrier such that the clutch of one of the two elements is in an engaged state and the brake of the other element is in a braked state, or such that the clutches of the two elements are in an engaged state, thereby forming one power transmission route of the transmission module.

2. The transmission module of claim 1,

the planet carrier is also connected to the torque input in a clutchable manner via a clutch.

3. The transmission module of claim 1,

each of the input sun gears is provided with a brake.

4. The transmission module of claim 1,

the torque input comprises a torque input shaft, each clutch comprising a clutchably connected inner hub and outer drum;

at least some of the torque input shaft and the m input sun gears are connected to one and the other of the inner hub and the outer drum of the corresponding clutch, respectively.

5. The transmission module of claim 1,

at least part of the m input sun gears are connected with a first transfer gear, and the first transfer gear is in meshing transmission with a second transfer gear;

the torque input end comprises a torque input shaft, the torque input shaft is provided with an input switching gear, and the input switching gear is in meshing transmission with a third switching gear;

a clutch is arranged between the second switching gear and the third switching gear, and at least part of the input sun gear is connected to the torque input shaft in a clutchable manner through the first switching gear, the second switching gear, the clutch, the third switching gear and the input switching gear in sequence.

6. The transmission module of claim 1,

the speed change module comprises more than two planet wheel assemblies, and the more than two planet wheel assemblies are uniformly distributed along the circumferential direction of the sun wheel set.

7. The transmission module of claim 1,

at least some of the sun gears of the sun gear set are held coaxially and rotatably relative to each other by pairs of tubes that are nested within each other.

8. The transmission module of claim 1,

the transmission rack comprises a front shaft hole and a rear shaft hole which are coaxial and arranged side by side;

the planet carrier rotatably supports in preceding shaft hole with between the rear axle hole, the moment of torsion input is located the front side in preceding shaft hole, the moment of torsion output is located the rear side in rear axle hole.

9. The transmission module of claim 8,

the brake of at least part of the m input sun gears is arranged at the rear side of the rear shaft hole.

10. A transmission comprising two or more transmission modules according to any one of claims 1 to 9, the torque output of a preceding transmission module of the two or more transmission modules being drivingly connected to the torque input of a subsequent transmission module.