Duplex planetary differential gear train

Abstract

The utility model relates to a duplex planet differential gear train which comprises a duplex planet carrier, an inner gear ring, a first-stage planet differential gear train and a second-stage planet differential gear train, the duplex planet carrier is provided with a first mounting part and a second mounting part which are coaxial, the outer side of the duplex planet carrier is sleeved with the inner gear ring, the inner gear ring and the duplex planet carrier are coaxial, and the first-stage planet differential gear train and the second-stage planet differential gear train are coaxial. Each of the first-stage planetary differential gear train and the second-stage planetary differential gear train comprises a sun gear and at least two planetary gears which correspond to each other; the two sun gears are respectively connected with different input ends; the first-stage planet gear is installed on the first installation part, and the second-stage planet gear is installed on the second installation part and meshed with the inner gear ring and the corresponding sun gear. According to the duplex planet differential gear train provided by the invention, the primary planet differential gear train and the secondary planet differential gear train are connected in parallel through the duplex planet carrier, and when the two input ends input the speed at the same time, the differential gear train has different reduction ratios, so that the range of the reduction ratios is enlarged, and the output torque is improved.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to the technical field of gear transmission, more specifically, the present disclosure relates to a double planetary differential gear train. BACKGROUND

[0002] The planetary gear transmission has the advantages of light weight, small size, large transmission ratio range, unlimited load capacity, same axis of input and output shafts, and high transmission efficiency, and is widely used in transmission devices in various mobile systems.

[0003] However, in the prior art, a single differential gear train has only a small reduction ratio range, and under the same conditions, it generates a smaller torque than other types of reduction machines, limiting its application range to some extent, so the present disclosure provides a new differential connection method to solve the defects in the prior art. CONTENT OF THE INVENTION

[0004] Therefore, the present disclosure provides a double planetary differential gear train to solve the technical defects in the prior art.

[0005] To achieve the above-mentioned purpose, the present disclosure adopts the following technical solutions:

[0006] The present disclosure provides a double planetary differential gear train, comprising:

[0007] A double planetary carrier having two coaxial mounting portions, denoted as a first mounting portion and a second mounting portion;

[0008] An inner ring configured to be fitted outside the double planetary carrier and coaxial with the double planetary carrier;

[0009] A primary planetary differential gear train comprising a primary sun gear and at least two primary planetary gears; the primary sun gear is configured to be connected to a first input end; wherein the primary planetary gears are configured to be mounted on the first mounting portion and are configured to mesh with the inner ring and the primary sun gear, respectively;

[0010] A secondary planetary differential gear train comprising a secondary sun gear and at least two secondary planetary gears; the secondary sun gear is configured to be connected to a second input end; wherein the secondary planetary gears are configured to be mounted on the second mounting portion and are configured to mesh with the inner ring and the secondary sun gear, respectively.

[0011] In one embodiment of the present disclosure, the first mounting portion is provided with at least two primary planetary columns, and the primary planetary gears are configured to be rotatably connected to the primary planetary columns.

[0012] In one embodiment of the present disclosure, the second mounting portion is provided with at least two secondary planetary columns, and the secondary planetary gears are configured to be rotationally connected to the secondary planetary columns.

[0013] In one embodiment of the present disclosure, the double planetary carrier further comprises a fixing member matched with the primary planetary columns and the secondary planetary columns, and the fixing member is configured to prevent the primary planetary gears and the secondary planetary gears from falling off the corresponding planetary columns.

[0014] In one embodiment of the present disclosure, the primary planetary columns are configured to be uniformly distributed on the first mounting portion along the circumference of the double planetary carrier, and the secondary planetary columns are configured to be uniformly distributed on the second mounting portion along the circumference of the double planetary carrier, wherein the primary planetary columns and the secondary planetary columns are located on opposite sides of the double planetary carrier.

[0015] In one embodiment of the present disclosure, the primary planetary gears are configured to have a smaller diameter than the secondary planetary gears, and the primary sun gears are configured to have a larger diameter than the secondary sun gears.

[0016] In one embodiment of the present disclosure, the primary sun gears and the secondary sun gears rotate in opposite directions.

[0017] In one embodiment of the present disclosure, the double planetary differential gear train has at least a first working mode, and in the first working mode, only the first input end inputs the rotation speed to the double planetary differential gear train.

[0018] In one embodiment of the present disclosure, the double planetary differential gear train has at least a second working mode, and in the second working mode, only the second input end inputs the rotation speed to the double planetary differential gear train.

[0019] In one embodiment of the present disclosure, the double planetary differential gear train has at least a third working mode, and in the third working mode, the first input end and the second input end are configured to jointly input the rotation speed to the double planetary differential gear train.

[0020] The double planetary differential gear train provided by the present disclosure connects a primary planetary differential gear train and a secondary planetary differential gear train in parallel through a double planetary carrier, a primary sun gear and a secondary sun gear are connected to different input ends respectively, and an inner ring is used as an output end of the double planetary differential gear train. When two input ends simultaneously receive different speed inputs, the double planetary differential gear train can exhibit different speed reduction ratios, and then output different rotation speeds through the inner ring. This design not only expands the speed reduction ratio range of the system, but also effectively improves the output torque, providing more flexible and efficient options for power transmission under complex working conditions.

[0021] Other features of the present disclosure, and their advantages, will become apparent in the non-limiting detailed description of exemplary embodiments of the present disclosure, which is presented in connection with the following drawings. BRIEF DESCRIPTION OF DRAWINGS

[0022] Figure 1 is a structural schematic diagram of a double planetary differential gear train provided by an embodiment of the present disclosure;

[0023] Figure 2 is a structural schematic diagram of a double planetary carrier provided by an embodiment of the present disclosure.

[0024] 1 - first planetary differential gear train; 11 - first sun gear; 12 - first planetary gear; 2 - second planetary differential gear train; 21 - second sun gear; 22 - second planetary gear; 3 - inner ring gear; 4 - double planetary carrier; 41 - first mounting portion; 42 - second mounting portion; 5 - first input end; 6 - second input end; 7 - first planetary column; 8 - second planetary column; 9 - process hole. DETAILED DESCRIPTION

[0025] Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. It should be noted that the relative arrangement, numerical expressions, and values of the components and steps set forth in these embodiments are not limiting to the scope of the present disclosure unless otherwise specifically stated.

[0026] The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way limiting to the scope of the disclosure and its applications or uses.

[0027] Techniques, methods, and devices known to those of ordinary skill in the relevant art can not be discussed in detail herein, but should be considered as part of the description if appropriate.

[0028] It should be noted that like reference numerals and letters refer to like items in the drawings, and thus once an item is defined in one drawing, it need not be discussed further in subsequent drawings.

[0029] The specific embodiments of the present disclosure will be described below with reference to the accompanying drawings.

[0030] In this document, "upper", "lower", "front", "back", "left", "right", and the like are used to describe relative positions between the relevant parts, and do not limit the absolute positions of the relevant parts.

[0031] In this document, "first", "second", and the like are used only to distinguish between each other, and do not indicate importance and order, and are not a prerequisite for each other.

[0032] In the present text, "equal", "identical" and the like are not to be understood in the strict mathematical and / or geometrical sense, but also include tolerances which can be understood by the person skilled in the art and which are permitted in manufacture or use.

[0033] The present disclosure relates to a double planetary differential gear train, which comprises a double planetary carrier, an inner ring, a first planetary differential gear train and a second planetary differential gear train, the double planetary carrier has coaxial first and second mounting portions, the inner ring is sleeved outside the double planetary carrier and coaxial with the double planetary carrier, the first and second planetary differential gear trains each comprises a corresponding sun gear and at least two planetary gears; the two sun gears are connected with different input ends respectively; the first planetary gears are mounted on the first mounting portion, and the second planetary gears are mounted on the second mounting portion and meshed with the inner ring and the corresponding sun gears respectively.

[0034] The double planetary differential gear train provided by the present disclosure connects the first and second planetary differential gear trains in parallel by using the double planetary carrier, the first and second sun gears are connected with different input ends respectively, and the inner ring serves as the output end of the double planetary differential gear train, so that the double planetary differential gear train can exhibit different reduction ratios when the two input ends simultaneously receive different speed inputs, and then output different rotational speeds through the inner ring. This design not only expands the reduction ratio range of the system, but also effectively improves the output torque, providing more flexible and efficient options for power transmission under complex working conditions.

[0035] For the sake of understanding, the specific structure and working principle of the double planetary differential gear train of the present disclosure will be described in detail below with reference to Figures 1 to 2 an embodiment.

[0036] As shown in Figure 1 and Figure 2 , the present disclosure provides a double planetary differential gear train, which comprises a double planetary carrier 4, an inner ring 3, a first planetary differential gear train 1 and a second planetary differential gear train 2, the double planetary carrier 4 has two coaxial mounting portions, which are referred to as a first mounting portion 41 and a second mounting portion 42; the inner ring 3 is sleeved outside the double planetary carrier 4 and coaxial with the double planetary carrier 4.

[0037] The first planetary differential gear train 1 comprises a first sun gear 11 and at least two first planetary gears 12; the first sun gear 11 is connected with a first input end 5; wherein the first planetary gears 12 are mounted on the first mounting portion 41 and meshed with the inner ring 3 and the first sun gear 11 respectively. The second planetary differential gear train 2 comprises a second sun gear 21 and at least two second planetary gears 22; the second sun gear 21 is connected with a second input end 6; wherein the second planetary gears 22 are mounted on the second mounting portion 42 and meshed with the inner ring 3 and the second sun gear 21 respectively.

[0038] Specifically, the double planetary carrier 4 provided by the present disclosure is designed with two coaxial mounting portions, referred to as a first mounting portion 41 and a second mounting portion 42, respectively. Since the two mounting portions are coaxial, the two mounting portions not only ensure that the primary planetary differential gear train 1 and the secondary planetary differential gear train 2 stably operate on the same central axis, but also provide accurate mounting positions for the respective planetary gears, preventing the primary planetary gears 12 and the secondary planetary gears 22 from disengaging from the double planetary differential gear train when rotating at high speed, thereby ensuring the stability of the double planetary differential gear train during movement.

[0039] Further, the inner ring gear 3 is sleeved on the outside of the double planetary carrier 4 and coaxial with the double planetary carrier 4, which reduces eccentricity errors between the gears, improves the accuracy and stability of transmission, and effectively reduces vibration and impact of the gears during operation, thereby reducing system noise. The primary planetary differential gear train 1 and the secondary planetary differential gear train 2 are connected in parallel through the double planetary carrier 4. The primary planetary differential gear train 1 is composed of a primary sun gear 11 and at least two primary planetary gears 12. The primary sun gear 11 is connected to the first input end 5 as a power input component. The primary planetary gears 12 are mounted on the first mounting portion 41 of the double planetary carrier 4. Each primary planetary gear 12 is simultaneously engaged with the inner ring gear 3 and the primary sun gear 11. At this time, the primary sun gear 11 is uniformly supported by the plurality of primary planetary gears 12 at the center of the first mounting portion 41. The secondary planetary differential gear train 2 has a similar structure to the primary planetary differential gear train 1 and is composed of a secondary sun gear 21 and at least two secondary planetary gears 22. The secondary sun gear 21 is connected to the second input end 6 as another power input component. The secondary planetary gears 22 are mounted on the second mounting portion 42 of the double planetary carrier 4. Each secondary planetary gear 22 is simultaneously engaged with the inner ring gear 3 and the secondary sun gear 21. At this time, the secondary sun gear 21 is uniformly supported by the plurality of secondary planetary gears 22 at the center of the second mounting portion 42. This connection ensures that each primary planetary gear 12 is subjected to the same force from the primary sun gear 11 and each secondary planetary gear 22 is subjected to the same force from the secondary sun gear 21, thereby enabling the primary planetary differential gear train 1 and the secondary planetary differential gear train 2 to stably transmit power. This design enables the primary planetary gears 12 and the secondary planetary gears 22 to revolve around the corresponding sun gears and rotate themselves, thereby achieving effective power transmission.

[0040] In practical applications, when the primary sun gear 11 inputs a rotational speed, the secondary sun gear 21 simultaneously inputs a rotational speed opposite to that of the primary sun gear 11, at this time, the inner ring gear 3 outputs a third rotational speed, because the rotational speed input by the secondary sun gear 21 is opposite to that of the primary sun gear 11, at this time, the primary planetary gear 12 and the secondary planetary gear 22 revolve around the primary sun gear 11 and the secondary sun gear 21 respectively, and at the same time, the rotational speed of the primary planetary gear 12 and the secondary planetary gear 22 is adjusted to ensure that the double planetary differential gear train does not dislocate, and through the meshing with the inner ring gear 3, the inner ring gear 3 generates the output third rotational speed, so under this configuration, the output rotational speed of the inner ring gear 3 is determined by the input rotational speeds of the primary sun gear 11 and the secondary sun gear 21, and different transmission ratios and output rotational speeds can be achieved according to different combinations of input rotational speeds, and the flexibility makes the double planetary differential gear train adapt to more complex working conditions.

[0041] As shown in Figure 1 and Figure 2 , in one embodiment of the present disclosure, at least two primary planetary columns 7 are arranged on the first mounting portion 41, and the primary planetary gear 12 is rotatably connected to the primary planetary column 7.

[0042] Specifically, as shown in Figure 2 , at least two primary planetary columns 7 are arranged on the first mounting portion 41, and these primary planetary columns 7 are used to mount and support the primary planetary gear 12, to ensure that the primary planetary gear 12 can freely rotate on the primary planetary column 7, and a process hole 9 is arranged on at least one primary planetary column 7, which is used to mount a lifting ring, to facilitate the movement of the double planetary differential gear train to a suitable position by external force through the lifting ring.

[0043] As shown in Figure 1 and Figure 2 , in one embodiment of the present disclosure, at least two secondary planetary columns 8 are arranged on the second mounting portion 42, and the secondary planetary gear 22 is rotatably connected to the secondary planetary column 8.

[0044] Specifically, at least two secondary planetary columns 8 are arranged on the second mounting portion 42, and these secondary planetary columns 8 are used to mount and support the secondary planetary gear 22, to ensure that the secondary planetary gear 22 can freely rotate on the secondary planetary column 8, and a process hole 9 is arranged on at least one secondary planetary column 8, which is used to mount a lifting ring, to facilitate the movement of the double planetary differential gear train to a suitable position by external force through the lifting ring, wherein, because the primary planetary column 7 and the secondary planetary column 8 are symmetrically distributed with the double planetary carrier 4 as the axis of symmetry, the process hole 9 on the secondary planetary column 8 is also arranged to be symmetrically distributed with the process hole 9 of the primary planetary column 7, so that the process hole 9 on the secondary planetary column 8 is also arranged to be symmetrically distributed with the process hole 9 of the primary planetary column 7, which can ensure that the double planetary differential gear train can move smoothly during the process of external force lifting, and avoid the primary sun gear 11 and the secondary sun gear 21 from disengaging from the system during transportation, which can cause damage to the equipment.

[0045] like Figure 2 As shown, in one embodiment of the present disclosure, the double planet carrier 4 also includes a fixing member adapted to the primary planet column 7 and the secondary planet column 8, and the fixing member is used to prevent the primary planet gear 12 and the secondary planet gear 22 from falling off from the corresponding planet column.

[0046] Specifically, the double planetary carrier 4 also includes fixings that are compatible with the primary planetary column 7 and the secondary planetary column 8. These fixings also play a key role in preventing them from falling off. The fixings can be retaining springs, retaining rings, nuts or other types of fasteners. The specific selection depends on the specific needs and working environment of the system. The fixings are installed at the ends of the primary planetary column 7 and the secondary planetary column 8, that is, at one end away from the double planetary carrier 4. The fixings reduce the vibration caused by the loosening of the primary planetary gear 12 and the secondary planetary gear 22, improve the stability of the system operation, and avoid failures or damage caused by the falling off of the primary planetary gear 12 and the secondary planetary gear 22 due to high-speed rotation.

[0047] like Figure 2 As shown, in one embodiment of the present disclosure, the first-level planetary column 7 is evenly distributed on the first mounting portion 41 along the circumference of the double-linked planetary carrier 4; the second-level planetary column 8 is evenly distributed on the second mounting portion 42 along the circumference of the double-linked planetary carrier 4; wherein the first-level planetary column 7 and the second-level planetary column 8 are located on opposite sides of the double-linked planetary carrier 4.

[0048] Specifically, the primary planetary columns 7 are evenly distributed on the first mounting portion 41 along the circumference of the duplex planetary carrier 4, ensuring that each primary planetary gear 12 is evenly distributed in space. This even distribution enables the primary planetary gears 12 to evenly withstand the force from the primary sun gear 11, improving the stability and transmission uniformity of the primary planetary differential gear system 1. The secondary planetary columns 8 are evenly distributed on the second mounting portion 42 along the circumference of the duplex planetary carrier 4, similarly ensuring that each secondary planetary gear 22 is evenly distributed in space. This even distribution enables the secondary planetary gears 22 to evenly withstand the force from the secondary sun gear 21, further improving the stability and transmission uniformity of the secondary planetary differential gear system 2. The primary planetary columns 7 and the secondary planetary columns 8 are located on opposite sides of the duplex planetary carrier 4. This symmetrical layout makes the center of gravity of the entire system more balanced, reduces vibration and imbalance caused by the asymmetric layout, and improves the system's operational smoothness.

[0049] like Figure 1 As shown, in one embodiment of the present disclosure, the diameter of the first-stage planetary gear 12 is smaller than that of the second-stage planetary gear 22 , and the diameter of the first-stage sun gear 11 is larger than that of the second-stage sun gear 21 .

[0050] Specifically, although the diameter of the primary planetary gear 12 is smaller than that of the secondary planetary gear 22, and the diameter of the primary sun gear 11 is larger than that of the secondary sun gear 21, the sum of the diameter of the primary planetary gear 12 and the diameter of the primary sun gear 11 is equal to the sum of the diameter of the secondary planetary gear 22 and the diameter of the secondary sun gear 21, so that the primary planetary gear 12 and the secondary planetary gear 22 are designed to be in close meshing with the inner ring gear 3 at the same time, so as to output the input of the primary sun gear 11 and the secondary sun gear 21 through the inner ring gear 3 through the primary planetary gear 12 and the secondary planetary gear 22.

[0051] As shown in the drawings, Figure 1 In one embodiment of the present disclosure, the rotation direction of the primary sun gear 11 is opposite to that of the secondary sun gear 21.

[0052] Specifically, in order to obtain different transmission ratios of the double planetary differential gear train, the primary sun gear 11 and the secondary sun gear 21 can input different rotation speeds and directions at the same time. In specific applications, since the primary sun gear 11 is connected to the first input end 5, the secondary sun gear 21 is connected to the second input end 6, and the first input end 5 and the second input end 6 are independent of each other and do not affect each other, the double planetary differential gear train has three working modes, that is, when the primary sun gear 11 inputs a rotation speed, the secondary sun gear 21 is fixed, at this time, the inner ring gear 3 outputs a first rotation speed; when the secondary sun gear 21 inputs a rotation speed, the primary sun gear 11 is fixed, at this time, the inner ring gear 3 outputs a second rotation speed; when the primary sun gear 11 inputs a rotation speed, the secondary sun gear 21 inputs a rotation speed opposite to the direction thereof, at this time, the inner ring gear 3 outputs a third rotation speed.

[0053] Further, since the rotation speed input by the secondary sun gear 21 is opposite to that of the primary sun gear 11, at this time, the primary planetary gear 12 and the secondary planetary gear 22 revolve around the primary sun gear 11 and the secondary sun gear 21 respectively, while also adjusting their own rotation speed to ensure that no dislocation occurs in the double planetary differential gear train, and through the meshing with the inner ring gear 3, the inner ring gear 3 outputs the third rotation speed, so that under this configuration, the output rotation speed of the inner ring gear 3 is determined by the input rotation speeds of the primary sun gear 11 and the secondary sun gear 21, and a plurality of different transmission ratios and output rotation speeds can be realized according to different combinations of input rotation speeds, and such flexibility enables the double planetary differential gear train to adapt to more complex working conditions.

[0054] As shown in the drawings, Figure 1 In one embodiment of the present disclosure, the double planetary differential gear train has at least a first working mode, and in the first working mode, only the first input end 5 inputs a rotation speed to the double planetary differential gear train.

[0055] Specifically, the first working mode is that the first sun gear 11 inputs a rotating speed, the second sun gear 21 is fixed, and the inner ring gear 3 outputs a first rotating speed. At this time, the working principle is that the first input end 5 drives the first sun gear 11 to input the rotating speed, and the second sun gear 21 is fixed. In this configuration, the output rotating speed of the inner ring gear 3 is mainly determined by the input rotating speed of the first sun gear 11, and the reduction ratio is determined at this time. Since the first sun gear 11 inputs the rotating speed, and the second sun gear 21 is fixed, at this time, the first sun gear 11 drives the first planetary gear 12 to start rotating. Since the inner ring gear 3 and the double planetary carrier 4 are completely free, at this time, the double planetary carrier 4 and the inner ring gear 3 also start rotating, and the second planetary gear 22 moves around the second sun gear 21 with the movement of the double planetary carrier 4. When the double planetary differential gear train reaches a balanced state, the first rotating speed is output. This mode is suitable for occasions where single-stage reduction and fixed output rotating speed are required.

[0056] As shown in FIG. 1, Figure 1 In one embodiment of the present disclosure, the double planetary differential gear train has at least a second working mode. In the second working mode, only the second input end 6 inputs a rotating speed to the double planetary differential gear train.

[0057] Specifically, the second working mode is that the second sun gear 21 inputs a rotating speed, the first sun gear 11 is fixed, and the inner ring gear 3 outputs a second rotating speed. At this time, the working principle is that the second input end 6 drives the second sun gear 21 to input the rotating speed, and the first sun gear 11 is fixed. In this configuration, the output rotating speed of the inner ring gear 3 is mainly determined by the input rotating speed of the second sun gear 21, and the reduction ratio is determined at this time. Since the second sun gear 21 inputs the rotating speed, and the first sun gear 11 is fixed, at this time, the second sun gear 21 drives the second planetary gear 22 to start rotating. Since the inner ring gear 3 and the double planetary carrier 4 are completely free, at this time, the double planetary carrier 4 and the inner ring gear 3 also start rotating, and the first planetary gear 12 moves around the first sun gear 11 with the movement of the double planetary carrier 4. When the double planetary differential gear train reaches a balanced state, the second rotating speed is output. This mode is suitable for occasions where single-stage reduction and fixed output rotating speed are required.

[0058] As shown in FIG. 1, Figure 1 In one embodiment of the present disclosure, the double planetary differential gear train has at least a third working mode. In the third working mode, the first input end 5 and the second input end 6 jointly input a rotating speed to the double planetary differential gear train.

[0059] Specifically, in the third working mode, when the primary sun gear 11 inputs a rotational speed, the secondary sun gear 21 inputs a rotational speed opposite to it, and at this time, the inner ring gear 3 outputs a third rotational speed. Since the rotational speed input by the secondary sun gear 21 is opposite to that of the primary sun gear 11, at this time, the primary planetary gear 12 and the secondary planetary gear 22 revolve around the primary sun gear 11 and the secondary sun gear 21 respectively, and at the same time, the rotational speed of the primary planetary gear 12 and the secondary planetary gear 22 is adjusted to ensure that the double planetary differential gear train does not dislocate, and through the meshing with the inner ring gear 3, the inner ring gear 3 generates the third rotational speed. Therefore, under this configuration, the output rotational speed of the inner ring gear 3 is determined by the input rotational speeds of the primary sun gear 11 and the secondary sun gear 21, and different transmission ratios and output rotational speeds can be achieved according to different combinations of input rotational speeds. The flexibility makes the double planetary differential gear train adapt to more complex working conditions.

[0060] The double planetary differential gear train provided by the present disclosure connects the primary planetary differential gear train 1 and the secondary planetary differential gear train 2 in parallel through the use of the double planetary carrier 4, the primary sun gear 11 and the secondary sun gear 21 are connected to different input ends respectively, and the inner ring gear 3 serves as the output end of the double planetary differential gear train. When the two input ends simultaneously receive different speed inputs, the double planetary differential gear train can exhibit different transmission ratio characteristics, and then output different rotational speeds from the inner ring gear 3. This design not only expands the transmission ratio range of the system, but also effectively improves the output torque, providing more flexible and efficient options for power transmission under complex working conditions.

[0061] It should be noted that, for the foregoing method embodiments, in order to facilitate description, they are all described as a series of action combinations, but those skilled in the art should know that the present disclosure is not limited by the action sequence described, because according to the present disclosure, certain steps can be performed in other sequences or simultaneously. Secondly, those skilled in the art should know that the embodiments described in the specification all belong to preferred embodiments, and the actions and modules involved are not necessarily essential to the present disclosure.

[0062] In the above embodiments, the description of each embodiment has its own focus, and the parts not described in detail in a certain embodiment can be referred to the related description of other embodiments.

[0063] The preferred embodiments of the present disclosure disclosed above are only used to help explain the present disclosure. The alternative embodiments do not describe all the details and do not limit the present disclosure to the specific embodiments described. Obviously, many modifications and changes can be made according to the content of the present disclosure. The present disclosure selects and describes these embodiments in order to better explain the principles and practical applications of the present disclosure, so that those skilled in the art can well understand and utilize the present disclosure. The present disclosure is limited only by the claims and their full scope and equivalents.

Claims

1. A double planetary differential gear train, characterized in that: include: A double planet carrier (4), the double planet carrier (4) having two coaxial mounting portions, denoted as a first mounting portion (41) and a second mounting portion (42); An inner gear ring (3), the inner gear ring (3) being configured to be sleeved on the outside of the double-linked planet carrier (4) and being configured to be coaxial with the double-linked planet carrier (4); A first-stage planetary differential gear train (1), the first-stage planetary differential gear train (1) comprising a first-stage sun gear (11) and at least two first-stage planetary gears (12); the first-stage sun gear (11) is configured to be connected to a first input end (5); wherein the first-stage planetary gear (12) is configured to be mounted on the first mounting portion (41) and to be meshed with the inner gear ring (3) and the first-stage sun gear (11), respectively; A secondary planetary differential gear train (2), the secondary planetary differential gear train (2) comprising a secondary sun gear (21) and at least two secondary planetary gears (22); the secondary sun gear (21) is configured to be connected to a second input end (6); wherein the secondary planetary gears (22) are configured to be mounted on the second mounting portion (42) and to be meshed with the inner ring gear (3) and the secondary sun gear (21), respectively.

2. The double planetary differential gear train according to claim 1, characterized in that: At least two first-level planetary columns (7) are provided on the first mounting portion (41), and the first-level planetary gear (12) is configured to be rotatably connected to the first-level planetary columns (7).

3. The double planetary differential gear train according to claim 2, characterized in that: At least two secondary planetary columns (8) are provided on the second mounting portion (42), and the secondary planetary gear (22) is configured to be rotatably connected to the secondary planetary columns (8).

4. The double planetary differential gear train according to claim 3, characterized in that: The double planet carrier (4) further comprises a fixing member adapted to the primary planet column (7) and the secondary planet column (8), wherein the fixing member is configured to prevent the primary planet wheel (12) and the secondary planet wheel (22) from falling off the corresponding planet column.

5. The double planetary differential gear train according to claim 4, characterized in that: The first-level planetary column (7) is configured to be evenly distributed on the first mounting portion (41) along the circumference of the double-linked planetary carrier (4); the second-level planetary column (8) is configured to be evenly distributed on the second mounting portion (42) along the circumference of the double-linked planetary carrier (4); wherein the first-level planetary column (7) and the second-level planetary column (8) are configured to be located on opposite sides of the double-linked planetary carrier (4).

6. The double planetary differential gear train according to claim 1, characterized in that: The first-stage planetary gear (12) is configured to have a smaller diameter than the second-stage planetary gear (22), and the first-stage sun gear (11) is configured to have a larger diameter than the second-stage sun gear (21).

7. The double planetary differential gear train according to claim 6, characterized in that: The primary sun gear (11) and the secondary sun gear (21) rotate in opposite directions.

8. The double planetary differential gear train according to claim 7, characterized in that: The double planetary differential gear train has at least a first working mode. In the first working mode, only the first input end (5) inputs a rotational speed to the double planetary differential gear train.

9. The double planetary differential gear train according to claim 7, characterized in that: The double planetary differential gear train has at least a second working mode. In the second working mode, only the second input end (6) inputs a rotational speed to the double planetary differential gear train.

10. The double planetary differential gear train according to claim 7, characterized in that: The double planetary differential gear train has at least a third working mode. In the third working mode, the first input end (5) and the second input end (6) are configured to jointly input a rotational speed to the double planetary differential gear train.

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