阅读说明：本技术 一种集成差速器的两档变速箱 (Two-gear gearbox integrated with differential mechanism ) 是由 不公告发明人 于 2020-05-04 设计创作，主要内容包括：本发明提供一种集成差速器的两档变速箱,包括：差动耦合模块,动力输入齿轮轴(8),动力转换齿轮轴(9),离合器(12),制动器(13),下箱体(10),上箱体(11),行星架轴承(31),动力输入齿轮轴轴承(32),动力转换齿轮轴轴承(33)；本发明的有益效果为：通过巧妙的设计,将变速装置和差速输出装置集成为一体,结构紧凑,重量轻,成本低,既能够对电动机输入的运动实现变速,又能够将变速后的运动差速输出至传动轴并最终驱动车辆高效行驶,尤其适合作为纯电动汽车或混合动力汽车的变速箱,也适用于内燃机或其它任何动力形式的车辆。(The invention provides a two-gear gearbox integrated with a differential, which comprises: the device comprises a differential coupling module, a power input gear shaft (8), a power conversion gear shaft (9), a clutch (12), a brake (13), a lower box body (10), an upper box body (11), a planet carrier bearing (31), a power input gear shaft bearing (32) and a power conversion gear shaft bearing (33); the invention has the beneficial effects that: the speed change device and the differential output device are integrated into a whole through ingenious design, the structure is compact, the weight is light, the cost is low, the speed change can be realized on the motion input by the motor, the motion after speed change can be output to the transmission shaft in a differential mode, and finally the vehicle is driven to run efficiently.)

1. A differential-integrated two-speed transmission comprising: the device comprises a differential coupling module, a power input gear shaft (8), a power conversion gear shaft (9), a lower box body (10), an upper box body (11), a clutch (12), a brake (13), a planet carrier bearing (31), a power input gear shaft bearing (32) and a power conversion gear shaft bearing (33); the method is characterized in that:

the differential coupling module includes: the planetary gear set comprises a planetary carrier main body (1), a planetary carrier end cover (2), at least three identical planetary gear pairs (34), a planetary gear pair bearing (30), a first power input gear ring (5), a second power input gear ring (6) and a differential (7);

the planet carrier main body (1) is of a cylindrical structure and comprises a bottom plate (101) and a cylindrical wall (105), a differential installation hole I (102) and a differential installation spline sleeve I (103) are arranged at the center of the bottom plate (101), an internal spline I (103a) is arranged inside the differential installation spline sleeve I (103), planetary gear pair installation grooves I (104) are coaxially arranged on the outer side of the differential installation spline sleeve I (103) on the bottom plate (101), the number of the planetary gear pair installation grooves I (104) is equal to that of planetary gear pairs (34), partitions with the same number as that of the planetary gear pairs (34) are arranged on the cylindrical wall (105), the partition positions correspond to those of the planetary gear pair installation grooves I (104) on the bottom plate (101), and after the planetary gear pairs (34) are installed in the planet carrier, a part of teeth of the planetary gear pairs (34) are always positioned on the outer side of the cylindrical wall (105) of the planet carrier, the end face of the cylinder wall (105) is provided with at least 3 bolt connecting holes I (105 a);

a differential mounting hole II (201) and a differential mounting spline housing II (202) are arranged at the center of the planet carrier end cover (2), an internal spline II (202a) is arranged inside the differential mounting spline housing II (202), a planetary gear pair mounting groove II (203) is coaxially arranged on the planet carrier end cover (2) and positioned on the outer side of the differential mounting spline housing II (202), the shape, size, position and number of the planetary gear pair mounting groove II (203) are the same as those of the planetary gear pair mounting groove I (104), and a bolt connecting hole II (204) is also arranged on the planet carrier end cover (2) and has the size, position and number of the bolt connecting hole II (105 a);

the planet carrier main body (1) and the planet carrier end cover (2) are connected into a whole through a bolt connecting hole I (105a) and a bolt connecting hole II (204) by a bolt I (20), so that a planet carrier is formed;

each pair of planetary gear pairs (34) comprises a planetary gear I (3) and a planetary gear II (4), wherein the planetary gear I (3) comprises a first tooth section (301), a second tooth section (302) and a shaft neck I (303) which are integrated; the planetary gear II (4) comprises a third tooth section (401), a fourth tooth section (402) and a shaft neck II (403) which are integrated; parameters and sizes of the planetary gear I (3) and the planetary gear II (4) are the same;

each pair of planetary gear pairs (34) is arranged in a planetary gear pair mounting groove I (104) and a planetary gear pair mounting groove II (203) of the planet carrier through a planetary gear pair bearing (30) arranged on a journal I (303) of the planetary gear I (3) and a journal II (403) of the planetary gear II (4), the planetary gear I (3) and the planetary gear II (4) can rotate together with the planet carrier and can rotate around the axis of the planetary gear I and the planetary gear II, and a second tooth section (302) of the planetary gear I (3) and a fourth tooth section (402) of the planetary gear II (4) are always meshed in the operation;

a first power coupling tooth part (501) is arranged inside the first power input gear ring (5), a first power input tooth part (502) is arranged outside the first power input gear ring, a second power coupling tooth part (601) is arranged inside the second power input gear ring (6), and a second power input tooth part (602) is arranged outside the second power input gear ring;

the first power input gear ring (5) is sleeved outside the cylinder wall (105) of the planet carrier, a first power coupling tooth part (501) in the first power input gear ring is meshed with a first tooth section (301) of a planetary gear I (3) of each pair of planetary gears (34), the second power input gear ring (6) is sleeved outside the cylinder wall (105) of the planet carrier, and a second power coupling tooth part (601) in the second power input gear ring is meshed with a third tooth section (401) of a planetary gear II (4) of each pair of planetary gears (34);

the differential (7) comprises: the differential mechanism comprises a first half shaft (701), a second half shaft (703) and a differential shell (702), wherein a planet carrier connecting external spline (702a) is arranged on the differential shell (702), and the parameters of the planet carrier connecting external spline (702a) are matched with the parameters of an internal spline I (103a) and an internal spline II (202a) on the planet carrier;

the differential (7) is arranged in the planet carrier through a planet carrier connecting external spline (702a) on the differential carrier (702), the differential carrier (702) and the planet carrier are connected into a whole to move together with the planet carrier, and a first half shaft (701) and a second half shaft (703) of the differential (7) respectively penetrate through a differential mounting hole I (102) and a differential mounting hole II (201) and extend out of the planet carrier;

the lower box body (10) is in a double-cavity semi-cylindrical shape and comprises a power coupling cavity (10d) taking an axis I (10a) as an axis, a power input cavity (10e) taking an axis II (10b) as an axis, the axis I (10a) and the axis II (10b) are both positioned in an upper surface (10c) and are parallel to each other, both ends of the power coupling cavity (10d) are provided with a planet carrier mounting hole (1001) and a planet carrier bearing mounting groove (1002) which are coaxial with the axis I (10a), the left end of the power input cavity (10e) is provided with a power input gear shaft mounting hole (1003) and a power input gear shaft bearing mounting groove (1004) which are coaxial with the axis II (10b), the right end of the power input cavity (10e) is provided with a power conversion gear shaft (1005) and a power conversion gear shaft bearing mounting groove (1006) which are coaxial with the axis II (10b), a brake shell connecting hole (1007) is coaxially arranged on the right end surface of the lower box body (10) and the power conversion gear shaft mounting hole (1005);

the shapes and the sizes of the upper box body (11) and the lower box body (10) are symmetrical about the upper surface (10c), and the upper box body (11) and the lower box body (10) are connected into a complete gearbox body through a bolt II (21);

the power input gear shaft (8) comprises an integrated power input gear (801), a power input journal (802), a power input spline (803) and a power transmission spline (804), and the power conversion gear shaft (9) comprises an integrated power conversion gear (901), a power conversion journal (902), a braking force input spline (903) and a power conversion internal spline (904), wherein: the module and the tooth number of the power input gear (801) and the power conversion gear (901) are respectively the same;

the power input gear shaft (8) is mounted in a power input cavity (10e) of a gearbox box body through a power input gear shaft bearing (32), the power conversion gear shaft (9) is mounted in the power input cavity (10e) of the gearbox box body through a power conversion gear shaft bearing (33), the input end of a clutch (12) is connected with a power transmission spline (804) of the power input gear shaft (8) through an internal spline of a spline hub, the output end of the clutch (12) is connected with a power conversion internal spline (904) of the power conversion gear shaft (9) through a spline, the input end of a brake (13) is connected with a braking force input spline (903) of the power conversion gear shaft (9) through an internal spline of a spline hub, and the shell of the brake (13) is connected with the gearbox box body through a brake shell connecting hole (1007) through a bolt III (22);

the differential coupling module is arranged in a power coupling cavity (10d) of a gearbox casing through a planet carrier bearing (31) and is in rotary connection with the gearbox casing, a first power input tooth part (502) of a first power input gear ring (5) of the differential coupling module is meshed with a power input gear (801) of a power input gear shaft (8), and a second power input tooth part (602) of a second power input gear ring (6) is meshed with a power conversion gear (901) of a power conversion gear shaft (9).

2. The differential-integrated two-speed transmission of claim 1, wherein: the differential (7) is a prior art product that is capable of splitting the motion of the differential case (702) into the motion of the first half-shaft (701) and the second half-shaft (703).

3. The differential-integrated two-speed transmission of claim 1, wherein: the clutch (12) is a product in the prior art and is a multi-plate clutch or a single-plate clutch, and the brake (13) is a product in the prior art and is a multi-plate brake or a single-plate brake or a drum brake.

Technical Field

The invention relates to an automobile speed changing device, in particular to a two-gear gearbox integrated with a differential mechanism.

Background

With the development of technology and the enhancement of environmental awareness of people, electric vehicles are more and more popularized in the world, but the electric vehicles in the current market basically adopt a speed reducing mechanism with a single speed ratio due to the limitation of cost and technology, and are not provided with a multi-gear gearbox in the traditional sense, so that the power performance of the current electric vehicle at medium and low speeds is very outstanding, the energy is saved, the power output is obviously reduced due to the limitation of the electromagnetic property of the motor after the electric vehicle reaches a high speed, the energy conversion efficiency is greatly reduced compared with the low speed, and the extreme speed of the electric vehicle is often low due to the limitation of the limit rotating speed of the motor, so that the practicability of the electric vehicle is greatly influenced.

Disclosure of Invention

Aiming at the problems in the prior art, the invention provides a two-gear transmission integrated with a differential mechanism, so as to achieve the effects of reducing the energy consumption of a vehicle, improving the power performance of the vehicle and improving the top speed of the vehicle.

In order to achieve the technical purpose, the technical scheme of the invention is realized as follows:

a differential-integrated two-speed transmission comprising: differential coupling module, power input gear shaft 8, power conversion gear shaft 9, clutch 12, brake 13, lower box 10, upper box 11, planet carrier bearing 31, power input gear shaft bearing 32 and power conversion gear shaft bearing 33.

The differential coupling module includes: the planetary gear set comprises a planetary carrier main body 1, a planetary carrier end cover 2, at least three identical planetary gear pairs 34, a planetary gear pair bearing 30, a first power input gear ring 5, a second power input gear ring 6 and a differential mechanism 7.

The planet carrier main body 1 is of a cylindrical structure and comprises a bottom plate 101 and a cylindrical wall 105, a differential installation hole I102 and a differential installation spline housing I103 are arranged at the center of the bottom plate 101, an internal spline I103 a is arranged inside the differential installation spline housing I103, a planetary gear pair installation groove I104 is coaxially arranged on the bottom plate 101 and positioned outside the differential installation spline housing I103, the number of the planetary gear pair installation grooves I104 is equal to that of the planetary gear pairs 34, partitions with the same number as that of the planetary gear pairs 34 are arranged on the cylindrical wall 105, and the partition positions correspond to the positions of the planetary gear pair installation grooves I104 on the bottom plate 101, after the planetary gear pair 34 is installed in the planet carrier, a part of teeth of the planetary gear pair 34 are always positioned outside the cylinder wall 105 of the planet carrier, and at least 3 bolt connecting holes I105 a are arranged on the end surface of the cylinder wall 105.

The center department of planet carrier end cover 2 is provided with differential installation hole II 201 and differential installation spline housing II 202, the inside of differential installation spline housing II 202 is provided with internal spline II 202a, lie in the outside of differential installation spline housing II 202 on planet carrier end cover 2 rather than coaxial being provided with planetary gear to mounting groove II 203, the shape of planetary gear to mounting groove II 203, the size, the position, quantity is the same with planetary gear to mounting groove I104, still be provided with bolted connection hole II 204 on planet carrier end cover 2, its size, the position, quantity is the same with bolted connection hole I105 a.

The planet carrier main body 1 and the planet carrier end cover 2 are integrally connected through a bolt connecting hole I105 a and a bolt connecting hole II 204 by a bolt I20, thereby forming a planet carrier.

Each pair of planetary gears 34 comprises a planetary gear I3 and a planetary gear II 4, wherein the planetary gear I3 comprises a first tooth section 301, a second tooth section 302 and a shaft neck I303 which are integrated; the planet gear II 4 comprises a third tooth section 401, a fourth tooth section 402 and a journal II 403 which are integrated; parameters and sizes of all parts of the planet gear I3 and the planet gear II 4 are the same.

Each pair of planet gears 34 is mounted in the planet gear pair mounting groove i 104 and the planet gear pair mounting groove ii 203 of the planet carrier through the planet gear pair bearings 30 arranged on the journal i 303 of the planet gear i 3 and the journal ii 403 of the planet gear ii 4, the planet gears i 3 and the planet gears ii 4 can rotate along with the planet carrier and rotate around the axes thereof, and the second tooth section 302 of the planet gear i 3 and the fourth tooth section 402 of the planet gear ii 4 are meshed all the time in operation.

The first power input ring gear 5 is internally provided with a first power coupling tooth portion 501, the outside thereof is provided with a first power input tooth portion 502, the second power input ring gear 6 is internally provided with a second power coupling tooth portion 601, and the outside thereof is provided with a second power input tooth portion 602.

The first power input gear ring 5 is sleeved outside the cylinder wall 105 of the planet carrier, the first power coupling tooth part 501 in the first power input gear ring is meshed with the first tooth section 301 of the planetary gear I3 of each pair of planetary gear pairs 34, the second power input gear ring 6 is sleeved outside the cylinder wall 105 of the planet carrier, and the second power coupling tooth part 601 in the second power input gear ring is meshed with the third tooth section 401 of the planetary gear II 4 of each pair of planetary gear pairs 34.

The differential 7 includes: the first half shaft 701, the second half shaft 703 and the differential shell 702 are provided with a planet carrier connecting external spline 702a, and the parameters of the planet carrier connecting external spline 702a are matched with the parameters of an internal spline I103 a and an internal spline II 202a on the planet carrier.

The differential 7 is installed inside a planet carrier through a planet carrier connecting external spline 702a on a differential carrier 702, the differential carrier 702 and the planet carrier are connected into a whole to move together with the planet carrier, and a first half shaft 701 and a second half shaft 703 of the differential 7 respectively penetrate through a differential mounting hole I102 and a differential mounting hole II 201 to extend out of the planet carrier.

The differential 7 is a prior art product that is capable of decomposing the motion of the differential case 702 into the motion of the first axle shaft 701 and the second axle shaft 703.

The lower box body 10 is in a double-cavity semi-cylindrical shape and comprises a power coupling cavity 10d taking an axis I10 a as an axis, and a power input cavity 10e taking an axis II 10b as an axis, wherein the axis I10 a and the axis II 10b are both positioned in an upper surface 10c and are parallel to each other, both ends of the power coupling cavity 10d are provided with a planet carrier mounting hole 1001 and a planet carrier bearing mounting groove 1002 which are coaxial with the axis I10 a, the left end of the power input cavity 10e is provided with a power input gear shaft mounting hole 1003 and a power input gear shaft bearing mounting groove 1004 which are coaxial with the axis II 10b, the right end of the power input cavity 10e is provided with a power conversion gear shaft mounting hole 1005 and a power conversion gear shaft bearing mounting groove 1006 which are coaxial with the axis II 10b, and the right end face of the lower box body 10 is provided with a brake shell connecting hole 1005.

The shape and the size of the upper box body 11 and the lower box body 10 are symmetrical about the upper surface 10c, and the upper box body 11 and the lower box body 10 are connected through a bolt II 21 to form a complete gearbox box body.

The power input gear shaft 8 comprises an integrated power input gear 801, a power input journal 802, a power input spline 803 and a power transmission spline 804, and the power conversion gear shaft 9 comprises an integrated power conversion gear 901, a power conversion journal 902, a braking force input spline 903 and a power conversion internal spline 904, wherein: the module and the number of teeth of the power input gear 801 and the power conversion gear 901 are respectively the same.

The power input gear shaft 8 is arranged in a power input cavity 10e of the gearbox casing through a power input gear shaft bearing 32, the power conversion gear shaft 9 is arranged in the power input cavity 10e of the gearbox casing through a power conversion gear shaft bearing 33, the input end of the clutch 12 is connected with a power transmission spline 804 of the power input gear shaft 8 through an internal spline of a spline hub, the output end of the clutch 12 is connected with a power conversion internal spline 904 of the power conversion gear shaft 9 through a spline, the input end of the brake 13 is connected with a braking force input spline 903 of the power conversion gear shaft 9 through an internal spline of a spline hub, and the shell of the brake 13 is connected with the gearbox casing through a brake shell connecting hole 1007 by using a bolt III 22;

the differential coupling module is installed in the power coupling cavity 10d of the gearbox casing through the planet carrier bearing 31 and forms a rotary connection with the gearbox casing, the first power input tooth part 502 of the first power input gear ring 5 of the differential coupling module is meshed with the power input gear 801 of the power input gear shaft 8, and the second power input tooth part 602 of the second power input gear ring 6 is meshed with the power conversion gear 901 of the power conversion gear shaft 9.

The working principle of the two-gear gearbox integrated with the differential is as follows:

the output shaft of the motor 100 transmits power to the power input gear shaft 8 through the power input spline 803 of the power input gear shaft 8, and is provided with: the rotational speed of the output shaft of the motor 100 is ω₀The rotational speed of the power input gear shaft 8 is omega₁The rotation speed of the power conversion gear shaft 9 is omega₂The rotational speed of the first power input ring gear 5 is ω₃The rotational speed of the second power input ring gear 6 is ω₄The rotational speed of the planet carrier is omega₅The gear ratio of the power input gear 801 to the first power input tooth portion 502 is 1/n, and the power conversion gear 901 and the second power areThe input tooth 602 has a tooth ratio of 1/n.

A differential gear train pi is formed by the planet carrier, the first power input gear ring 5, the second power input gear ring 6 and at least three planetary gear pairs 34, the motions of the first power input gear ring 5 and the second power input gear ring 6 are combined into the motion of the planet carrier, and the relationship of the motion synthesis is as follows: omega₃+ω₄＝2ω₅。

The planet carrier transmits its motion to the differential case 702, and the motion of the differential case 702 is split by the differential 7 into the motion of the first axle shaft 701 and the second axle shaft 703, which are then transmitted to the wheels 400 via the propeller shaft 300.

In the first gear: the clutch 12 is disengaged, the brake 13 is engaged, and the power conversion gear shaft 9 is locked with the transmission case by the brake 14, so that the rotation speed ω of the power input gear 1101₁＝ω₀Rotational speed ω of power conversion gear 1301₂0, and further: omega₃＝ω₁/n＝ω₀/n，ω₄＝ω₂/n＝0；

So the rotational speed omega of the planet carrier₅＝(ω₃+ω₄)/2＝(ω₀/n+0)/2＝ω₀/(2n)

Further, the motion of the carrier is split by the differential 7 to the first half shaft 701 and the second half shaft 703, and further transmitted to the wheels 400 through the propeller shaft 300.

In the second gear: the clutch 12 is engaged and the brake 13 is disengaged, and at this time, the power conversion gear shaft 9 and the power input gear shaft 8 are integrally connected, so that the rotation speed of the power conversion gear 901 is the same as that of the power input gear 801 and is equal to the rotation speed ω of the output shaft of the motor 100₀Namely: omega₁＝ω₂＝ω₀,ω₄＝ω₃＝ω₀/n；

So the rotational speed omega of the planet carrier₅＝(ω₃+ω₄)/2＝(ω₀/n+ω₀/n)/2＝ω₀/n

Further, the motion of the carrier is split by the differential 7 to the first half shaft 701 and the second half shaft 703, and further transmitted to the wheels 400 through the propeller shaft 300.

The invention has the beneficial effects that: the speed change device and the differential are integrated into a whole through ingenious design, the structure is compact, the weight is light, the cost is low, the speed change can be realized on the motion input by the motor, the motion differential after speed change can be output to the transmission shaft, and finally the vehicle is driven to run efficiently, so that the speed change device is particularly suitable for serving as a gearbox of a pure electric vehicle or a hybrid electric vehicle, and is also suitable for an internal combustion engine or other vehicles in any power form.

Drawings

In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.

FIG. 1 is a schematic structural diagram of a planet carrier of a two-speed transmission integrated with a differential according to an embodiment of the present invention;

FIG. 2 is a schematic structural diagram of a planet carrier end cover of a two-speed transmission case integrated with a differential according to an embodiment of the present invention;

FIG. 3 is a schematic diagram of an overall structure of a planet carrier of a differential-integrated two-speed transmission according to an embodiment of the present invention;

FIG. 4 is a schematic illustration of a differential configuration for a differential-integrated two-speed transmission according to an embodiment of the present invention;

FIG. 5 is a schematic illustration of a differential and carrier combination for a differential-integrated two speed transmission according to an embodiment of the present invention;

FIG. 6 is a schematic structural diagram of a planetary gear pair and a power input ring gear of a two-speed transmission integrated with a differential according to an embodiment of the present invention;

FIG. 7 is a schematic view of a planetary carrier and planetary gear pair combination of a two-speed transmission with an integrated differential according to an embodiment of the present invention;

fig. 8 is a schematic structural diagram of a differential gear train Π of a two-speed transmission integrated with a differential according to an embodiment of the invention;

FIG. 9 is a schematic structural diagram of a differential coupling device of a differential-integrated two-speed transmission according to an embodiment of the present invention;

FIG. 10 is a schematic diagram of the power input gear shaft and the power conversion gear shaft of a differential-integrated two-speed transmission according to an embodiment of the present invention;

FIG. 11 is a schematic structural view of a lower case of a differential-integrated two-speed transmission according to an embodiment of the present invention;

FIG. 12 is a schematic structural diagram of an internal overall structure of a differential-integrated two-speed transmission according to an embodiment of the present invention;

FIG. 13 is a schematic external overall configuration of a differential-integrated two-speed transmission according to an embodiment of the present invention;

FIG. 14 is a schematic structural diagram of a powertrain incorporating a differential two-speed transmission according to an embodiment of the present invention;

in the figure:

1. a planet carrier body; 101. a base plate; 102. a differential mounting hole I; 103. a spline housing I is mounted on the differential; 103a and an inner spline I; 104. a planetary gear pair mounting groove I; 105. a cylinder wall; 105a and a bolt connecting hole I; 2. a planet carrier; 201. a differential mounting hole II; 202. mounting a spline sleeve II on the differential; 202a and an internal spline II; 203. a planetary gear pair mounting groove II; 34. a pair of planetary gears; 3. a planetary gear I; 301. a first tooth segment; 302. a second tooth segment; 303. a shaft neck I; 4. a planetary gear II; 401. a third tooth segment; 402. a fourth tooth segment; 403. a journal II; 5. a first power input ring gear; 501. a first power coupling tooth portion; 502. a first power input tooth portion; 6. a second power input ring gear; 601. a second power coupling tooth portion; 602. a second power input tooth portion; 7. a differential mechanism; 701, performing heat treatment on the mixture; a first half shaft; 702. a differential housing; 702a and the planet carrier are connected with an external spline; 703. a second half shaft; 8. a power input gear shaft; 801. a power input gear; 802. a power input journal; 803. a power input spline 804, a power transfer spline; 9. a power conversion gear shaft; 901. a power conversion gear; 902. a power conversion journal; 903. a braking force input spline; 904. power conversion internal splines; 10. a lower box body; 11. an upper box body; 12. a clutch; 13. a brake; 20. a bolt I; 22. a bolt II; 23. a bolt III; 30. a planetary gear pair bearing; 31. a planet carrier bearing; 32. a power input gear shaft bearing; 33. a power conversion gear shaft bearing; 100. a first power source; 300. a drive shaft; 400. and (7) wheels.

The specific implementation mode is as follows:

the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, rather than all embodiments, and all other embodiments obtained by those skilled in the art based on the embodiments of the present invention belong to the scope of protection of the present invention.

1-14, a differential-integrated two-speed transmission, comprising: differential coupling module, power input gear shaft 8, power conversion gear shaft 9, clutch 12, brake 13, lower box 10, upper box 11, planet carrier bearing 31, power input gear shaft bearing 32 and power conversion gear shaft bearing 33.

As shown in fig. 1-9, the differential coupling module includes: the planetary gear set comprises a planetary carrier main body 1, a planetary carrier end cover 2, three identical planetary gear pairs 34, a planetary gear pair bearing 30, a first power input gear ring 5, a second power input gear ring 6 and a differential mechanism 7.

As shown in fig. 1, the planet carrier main body 1 is a cylindrical structure, and includes a bottom plate 101 and a cylindrical wall 105, a differential installation hole i 102 and a differential installation spline housing i 103 are provided at the center of the bottom plate 101, an internal spline i 103a is provided inside the differential installation spline housing i 103, three sets of planetary gear pair installation grooves i 104 are provided on the bottom plate 101 coaxially with the differential installation spline housing i 103, three partitions are provided on the cylindrical wall 105, the partitions correspond to the planetary gear pair installation grooves i 104 on the bottom plate 101, so as to divide the cylindrical wall 105 into three parts uniformly, and after the planetary gear pair 34 is installed in the planet carrier, a part of teeth of the planetary gear pair 34 are always located on the outer side of the cylindrical wall 105 of the planet carrier, and 9 bolt connection holes i 105a are provided on the end surface of the cylindrical wall 105.

As shown in fig. 2, a differential mounting hole ii 201 and a differential mounting spline housing ii 202 are provided at the center of the planet carrier end cover 2, an internal spline ii 202a is provided inside the differential mounting spline housing ii 202, a planetary gear pair mounting groove ii 203 is provided on the planet carrier end cover 2 on the outer side of the differential mounting spline housing ii 202 coaxially therewith, the shape, size, position and number of the planetary gear pair mounting groove ii 203 are the same as those of the planetary gear pair mounting groove i 104, and a bolt connecting hole ii 204 is further provided on the planet carrier end cover 2, and the size, position and number thereof are the same as those of the bolt connecting hole i 105 a.

As shown in fig. 3, the carrier body 1 and the carrier cover 2 are integrally connected by bolts i 20 through bolt connection holes i 105a and bolt connection holes ii 204, thereby constituting a carrier.

As shown in fig. 6, each planetary gear pair 34 comprises a planetary gear i 3 and a planetary gear ii 4, wherein the planetary gear i 3 comprises a first tooth section 301, a second tooth section 302 and a shaft journal i 303 which are integrated; the planet gear II 4 comprises a third tooth section 401, a fourth tooth section 402 and a journal II 403 which are integrated; parameters and sizes of all parts of the planet gear I3 and the planet gear II 4 are the same.

As shown in fig. 7, each pair of planetary gears 34 is mounted in the planetary gear pair mounting groove i 104 and the planetary gear pair mounting groove ii 203 of the planet carrier through the planetary gear pair bearings 30 arranged on the shaft journals i 303 and ii 403 of the planetary gears i 3 and ii 4, the planetary gears i 3 and ii 4 can rotate together with the planet carrier and rotate around the axis, and the second tooth sections 302 of the planetary gears i 3 and the fourth tooth sections 402 of the planetary gears ii 4 are always meshed in operation.

As shown in fig. 6, the first power input ring gear 5 is provided with a first power coupling tooth portion 501 inside, a first power input tooth portion 502 outside, a second power coupling tooth portion 601 inside, and a second power input tooth portion 602 outside.

As shown in fig. 8, the first power input ring gear 5 is sleeved outside the cylinder wall 105 of the planet carrier, the first power coupling tooth portion 501 inside the first power input ring gear is meshed with the first tooth section 301 of the planetary gear i 3 of each pair of planetary gears 34, the second power input ring gear 6 is sleeved outside the cylinder wall 105 of the planet carrier, and the second power coupling tooth portion 601 inside the second power input ring gear is meshed with the third tooth section 401 of the planetary gear ii 4 of each pair of planetary gears 34.

As shown in fig. 4, the differential 7 includes: the first half shaft 701, the second half shaft 703 and the differential shell 702 are provided with a planet carrier connecting external spline 702a, and the parameters of the planet carrier connecting external spline 702a are matched with the parameters of an internal spline I103 a and an internal spline II 202a on the planet carrier.

As shown in FIG. 5, the differential 7 is mounted inside a planet carrier through a planet carrier connecting external spline 702a on a differential case 702, the differential case 702 and the planet carrier are connected into a whole to move together with the planet carrier, and a first half shaft 701 and a second half shaft 703 of the differential 7 respectively pass through a differential mounting hole I102 and a differential mounting hole II 201 and extend out of the planet carrier.

The differential 7 is a prior art product that is capable of decomposing the motion of the differential case 702 into the motion of the first axle shaft 701 and the second axle shaft 703.

As shown in fig. 11, the lower casing 10, which is in the shape of a double-cavity semi-cylinder, includes a power coupling cavity 10d with an axis i 10a as an axis, the power input cavity 10e is characterized in that an axis II 10b is taken as a power input cavity 10e of the axis, the axis I10 a and the axis II 10b are both located in the upper surface 10c and are parallel to each other, a planet carrier mounting hole 1001 and a planet carrier bearing mounting groove 1002 which are coaxial with the axis I10 a are arranged at two ends of the power coupling cavity 10d, a power input gear shaft mounting hole 1003 and a power input gear shaft bearing mounting groove 1004 which are coaxial with the axis II 10b are arranged at the left end of the power input cavity 10e, a power conversion gear shaft mounting hole 1005 and a power conversion gear shaft bearing mounting groove 1006 which are coaxial with the axis II 10b are arranged at the right end of the power input cavity 10e, and a brake shell connecting hole 1007 is coaxially arranged with the power conversion gear shaft mounting hole 1005 on the right end surface of the lower box 10.

As shown in fig. 13, the shape and size of the upper casing 11 and the lower casing 10 are symmetrical about the upper surface 10c, and the upper casing 11 and the lower casing 10 are connected by a bolt ii 21 to form a complete transmission casing.

As shown in fig. 10, the power input gear shaft 8 includes an integrated power input gear 801, a power input journal 802, a power input spline 803, a power transmission spline 804, and the power conversion gear shaft 9 includes an integrated power conversion gear 901, a power conversion journal 902, a braking force input spline 903, and a power conversion internal spline 904, wherein: the module and the number of teeth of the power input gear 801 and the power conversion gear 901 are respectively the same.

As shown in fig. 12, the power input gear shaft 8 is mounted in the power input cavity 10e of the gearbox casing through the power input gear shaft bearing 32, the power conversion gear shaft 9 is mounted in the power input cavity 10e of the gearbox casing through the power conversion gear shaft bearing 33, the input end of the clutch 12 is connected with the power transmission spline 804 of the power input gear shaft 8 through the internal spline of the spline hub, the output end of the clutch 12 is connected with the power conversion internal spline 904 of the power conversion gear shaft 9 through the spline, the input end of the brake 13 is connected with the braking force input spline 903 of the power conversion gear shaft 9 through the internal spline of the spline hub, and the shell of the brake 13 is connected with the gearbox casing through the brake shell connecting hole 1007 by the bolt iii 22;

as shown in fig. 12, the differential coupling module is mounted in the power coupling cavity 10d of the transmission case through the planet carrier bearing 31 and forms a rotary connection with the transmission case, the first power input tooth portion 502 of the first power input ring gear 5 of the differential coupling module is meshed with the power input gear 801 of the power input gear shaft 8, and the second power input tooth portion 602 of the second power input ring gear 6 is meshed with the power conversion gear 901 of the power conversion gear shaft 9.

The working principle of the two-gear gearbox integrated with the differential is as follows:

as shown in fig. 14, the output shaft of the electric motor 100 transmits power to the power input gear shaft 8 through the power input spline 803 of the power input gear shaft 8, provided with: the rotational speed of the output shaft of the motor 100 is ω₀The rotational speed of the power input gear shaft 8 is omega₁The rotation speed of the power conversion gear shaft 9 is omega₂The rotational speed of the first power input ring gear 5 is ω₃The rotational speed of the second power input ring gear 6 is ω₄The rotational speed of the planet carrier is omega₅The gear ratio between the power input gear 801 and the first power input tooth portion 502 is 1/n, and the gear ratio between the power conversion gear 901 and the second power input tooth portion 602 is 1/n.

A differential gear train pi is formed by the planet carrier, the first power input gear ring 5, the second power input gear ring 6 and three groups of planetary gear pairs 34, the motion of the first power input gear ring 5 and the motion of the second power input gear ring 6 are combined into the motion of the planet carrier, and the relationship of the motion synthesis is as follows: omega₃+ω₄＝2ω₅。

The planet carrier transmits its motion to the differential case 702, and the motion of the differential case 702 is split by the differential 7 into the motion of the first axle shaft 701 and the second axle shaft 703, which are then transmitted to the wheels 400 via the propeller shaft 300.

In the first gear: the clutch 12 is disengaged, the brake 13 is engaged, and the power conversion gear shaft 9 is locked with the transmission case by the brake 14, so that the rotation speed ω of the power input gear 1101₁＝ω₀Rotational speed ω of power conversion gear 1301₂0, and further: omega₃＝ω₁/n＝ω₀/n，ω₄＝ω₂/n＝0；

So the rotational speed omega of the planet carrier₅＝(ω₃+ω₄)/2＝(ω₀/n+0)/2＝ω₀/(2n)

Further, the motion of the carrier is split by the differential 7 to the first half shaft 701 and the second half shaft 703, and further transmitted to the wheels 400 through the propeller shaft 300.

In the second gear: the clutch 12 is engaged and the brake 13 is disengaged, and at this time, the power conversion gear shaft 9 and the power input gear shaft 8 are integrally connected, so that the rotation speed of the power conversion gear 901 is the same as that of the power input gear 801 and is equal to the rotation speed ω of the output shaft of the motor 100₀Namely: omega₁＝ω₂＝ω₀,ω₄＝ω₃＝ω₀/n；

So the rotational speed omega of the planet carrier₅＝(ω₃+ω₄)/2＝(ω₀/n+ω₀/n)/2＝ω₀/n

Further, the motion of the carrier is split by the differential 7 to the first half shaft 701 and the second half shaft 703, and further transmitted to the wheels 400 through the propeller shaft 300.

The above description is only one of the preferred embodiments of the present invention, and should not be taken as limiting the invention, and any modifications, equivalents, improvements, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.