High-rigidity two-stage ngw planetary structure wheel-side driving device

Abstract

The utility model discloses a high rigidity two -stage NGW planetary structure wheel edge drive arrangement, including the rack of coaxial establishment in the wheel hub, still include the motor of establishment in the inside of rack, the power output shaft of motor is coaxial and connects the first planetary transmission unit, and the first planetary transmission unit is located the outside of rack, and the coaxial establishment of first planetary transmission unit and the rack has the second planetary transmission unit, and the mutual meshing transmission of first planetary transmission unit and second planetary transmission unit and the wheel hub, through the reasonable setting of component structure, and the first planetary carrier outer end is supported with the first inner tooth ring through the fourth bearing and relatively rotates, and the first planetary carrier outer end is limited through the support bearing and the second planetary carrier, and relatively rotates and supports each other, under the heavy load working condition, improve the support rigidity of first planetary carrier, avoid the transmission precision decline caused by the deformation of first planetary carrier, improve transmission precision and carrying capacity, improve the stability of device whole simultaneously.

Description

Technical Field

[0001] This utility model belongs to the field of wheel stopper technology, specifically relating to a high-rigidity two-stage NGW planetary structure wheel-side drive device. Background Technology

[0002] With the trend towards larger-scale mining operations, the depth of mining is increasing year by year, and steep slopes and numerous curves are constantly increasing the difficulty of mining operations. As a key power transmission component of mining dump trucks, the performance of the wheel-side drive system directly affects the vehicle's load-bearing capacity, climbing ability, and energy efficiency. In harsh working conditions such as open-pit mines, the drive system needs to withstand instantaneous impact loads, continuous high torque, and combined loads caused by complex road conditions, which places stringent requirements on the compactness, load-bearing capacity, and reliability of the wheel-side drive system.

[0003] Existing wheel-side drive boxes have the following shortcomings: Insufficient planetary carrier support stiffness leads to uneven load distribution on the planetary gears, reduced system stability, and significantly reduced gear and bearing life. Mismatched load-sharing mechanism settings under high torque reduce system stiffness and reliability. Under heavy load conditions, external loads are directly applied to the secondary internal gear ring, and deformation of the secondary internal gear ring results in decreased transmission accuracy and reduced load-bearing capacity of the planetary gear train. Utility Model Content

[0004] To address the aforementioned problems, the purpose of this invention is to provide a high-rigidity two-stage NGW planetary structure wheel-side drive device, solving the problem of insufficient rigidity of existing planetary carrier supports and easy deformation under heavy load conditions.

[0005] To achieve the above objectives, the technical solution adopted by this utility model includes:

[0006] A high-rigidity two-stage NGW planetary structure wheel-side drive device includes a frame coaxially mounted within a wheel hub, and a motor located inside the frame. The motor's power output shaft is coaxially connected to a primary planetary transmission unit, which is located outside the frame. A secondary planetary transmission unit is coaxially mounted between the primary and secondary planetary transmission units and the frame. The primary and secondary planetary transmission units engage with each other, as do the secondary planetary transmission unit and the wheel hub. The primary planetary transmission unit includes a primary planetary carrier, a primary sun gear shaft, a primary planetary assembly, and a primary internal gear ring. The primary sun gear shaft is coaxially connected to the power output shaft, and its free end extends to the outside of the frame. A primary sun gear is located on the outer periphery of the free end of the primary sun gear shaft. The primary planetary carrier is coaxially fitted around the outer periphery of the primary sun gear, and the primary planetary assembly is located inside the primary planetary carrier and meshes with the primary sun gear. The primary internal gear ring is coaxially fitted around the outer periphery of the primary planetary carrier and meshes with the primary planetary assembly. The primary internal gear ring remains fixed. The second-stage planetary transmission unit includes a second-stage planetary carrier, a second-stage sun gear shaft, a second-stage planetary assembly, and a second-stage internal gear ring. The second-stage sun gear shaft is coaxially fitted around the outer circumference of the first-stage sun gear shaft located inside the first-stage sun gear, and the second-stage sun gear shaft and the first-stage sun gear shaft do not contact each other. The second-stage sun gear shaft meshes with the inner spline of the inner end of the first-stage planetary carrier. The second-stage planetary carrier is coaxially fitted around the outer circumference of the second-stage sun gear shaft. The second-stage planetary assembly is located inside the second-stage planetary carrier and meshes with the second-stage sun gear shaft. The second-stage internal gear ring is coaxially fitted around the outer circumference of the second-stage planetary carrier and meshes with the second-stage planetary assembly. The second-stage internal gear ring is connected to the hub, and both sides of the second-stage planetary carrier are fixedly connected to the frame and the first-stage internal gear ring, respectively. A support bearing is coaxially provided between the outer circumference of the inner end of the first-stage planetary carrier and the inner circumference of the outer end of the second-stage planetary carrier. It also includes a bearing mounting ring seat coaxially fixed to the outer end of the first-stage internal gear ring. A fourth bearing is coaxially provided between the inner circumference of the bearing mounting ring seat and the outer circumference of the outer end of the first-stage planetary carrier.

[0007] Preferably, a third bearing is coaxially provided between the outer circumference of the second-stage sun gear shaft near the inner end and the inner circumference of the second-stage planetary carrier near the inner end.

[0008] Preferably, a torque sleeve is coaxially fixed at the outer end of the wheel hub, and the outer circumference of the secondary internal gear ring and the inner circumference of the torque sleeve are connected by spline meshing.

[0009] Preferably, the primary planetary assembly includes multiple primary planetary gear shafts that are circumferentially and uniformly fixed within the primary planetary carrier, with the axis of the primary planetary gear shaft parallel to the axis of the power output shaft; a primary planetary gear is coaxially sleeved on the outer circumference of each primary planetary gear shaft, and a first bearing is provided between each primary planetary gear shaft and the primary planetary gear, with each primary planetary gear meshing with a primary sun gear.

[0010] Preferably, the secondary planetary assembly includes multiple secondary planetary gear shafts evenly arranged circumferentially within the secondary planetary carrier, with the axis of the secondary planetary gear shaft parallel to the axis of the power output shaft; a secondary planetary gear is coaxially sleeved on the outer circumference of each secondary planetary gear shaft, a second bearing is provided between each secondary planetary gear shaft and the secondary planetary gear, and each secondary planetary gear meshes with the secondary sun gear shaft.

[0011] Preferably, the outer side of the secondary planetary carrier is provided with an oil collection groove, the secondary planetary gear shafts are open at both ends and hollow inside, the inner cavity of the secondary planetary gear shafts is connected to the oil collection groove, and the side wall of the secondary planetary gear shafts is provided with a lubrication through hole connected to its inner cavity.

[0012] Preferably, the secondary planetary gear shaft is fixedly connected to the frame.

[0013] Preferably, at least one fifth bearing is provided coaxially between the frame and the hub.

[0014] Preferably, a spacer ring is provided on the contact surface between the outer end of the wheel hub and the secondary internal gear ring.

[0015] Preferably, the first-stage sun gear shaft is open at both ends and hollow inside, and an oil collection cover is coaxially provided on the outer side of the first-stage sun gear shaft. The oil collection cover is provided with an oil collection groove, and the extension end of the oil collection groove extends into the outer port of the first-stage sun gear shaft.

[0016] Compared with the prior art, the advantages of this utility model are: (1) The present invention provides a high rigidity two-stage NGW planetary structure wheel-side drive device. Through the reasonable arrangement of the component structure, the outer end of the first-stage planetary carrier is supported and rotated relative to the first-stage internal gear ring through the fourth bearing. At the same time, the outer end of the first-stage planetary carrier is limited and supported relative to the second-stage planetary carrier through the support bearing. Under heavy load conditions, the support rigidity of the first-stage planetary carrier is improved, the transmission accuracy is avoided due to the deformation of the first-stage planetary carrier, the transmission accuracy and load-bearing capacity are improved, and the overall stability of the device is improved.

[0017] (2) The present invention provides a high rigidity two-stage NGW planetary structure wheel-side drive device. Through the reasonable setting of the component structure, the second-stage sun gear shaft is limited and rotates relative to the second-stage planetary carrier through the third bearing. At the same time, the outer circumference of the second-stage internal gear ring is connected to the torque sleeve through the spline. Under high torque conditions, the load-sharing mechanism eliminates or reduces the deformation of the second-stage internal gear ring, while increasing the system rigidity and reliability and reducing the assembly complexity.

[0018] (3) The high rigidity two-stage NGW planetary structure wheel-side drive device of this utility model, through the reasonable setting of the component structure, the lubricating oil in the oil collection cover flows through the inner hole of the first-stage sun gear shaft to the input connecting gear sleeve to supplement the lubrication of the connecting gear sleeve. Attached Figure Description

[0019] The accompanying drawings are provided to further illustrate the present invention and form part of the specification. They are used together with the following detailed description to explain the present invention, but do not constitute a limitation thereof. In the drawings: Figure 1 This is a schematic diagram of the high-rigidity two-stage NGW planetary structure wheel-side drive device of this utility model; Figure 2 for Figure 1 Schematic diagram of the structure of the first-stage planetary transmission unit; Figure 3 for Figure 1 Schematic diagram of the structure of the second-stage planetary transmission unit; Figure 4 for Figure 1 Schematic diagram of the intermediate-level planetary carrier; Figure 5 for Figure 1 A schematic diagram of the secondary planetary support structure.

[0020] The labels in the diagram represent: 0 Hub, 01 Spacer, 1 Motor, 1-1 Power Take-Off Shaft, 1-2 Connecting Gear Sleeve, 1-3 Sealing Cover, 2 Frame, 3 First-Stage Planetary Transmission Unit, 4 Second-Stage Planetary Transmission Unit, 5 Support Bearing, 6 Third Bearing, 7 Torque Sleeve, 8 Fifth Bearing, 8-1 Bearing Retaining Ring, 9 Floating Seal Mechanism, 10 Oil Collector Cover 3-0 First-stage planetary carrier, 3-01 First inner bore, 3-02 Second inner bore; 3-1 First-stage sun gear shaft, 3-10 First-stage sun gear; 3-2 First-stage planetary assembly, 3-21 First-stage planetary gear shaft, 3-22 First bearing, 3-23 First-stage planetary gear; 3-3 First-stage internal gear ring, 3-31 Gear ring retaining ring seat; 3-4 Bearing mounting ring seat, 3-41 Fourth bearing; 4-0 Second-stage planetary carrier; 4-01 Third inner bore; 4-1 Second-stage sun gear shaft; 4-2 Second-stage planetary assembly; 4-21 Second-stage planetary gear shaft; 4-210 Lubrication through hole; 4-22 Second bearing; 4-23 Second-stage planetary gear; 4-3 Second-stage internal gear ring. Detailed Implementation

[0021] The utility model is not limited to the following specific embodiments. All equivalent modifications made based on the technical solution of this application fall within the protection scope of this utility model.

[0022] It should be noted that the directional terms mentioned in this document, such as "inner cavity," "inner circumference," "inner wall," and "outer side," are consistent with the specific directions on the paper in the accompanying drawings or the corresponding directions of the space shown in the drawings; all components and devices in this utility model, unless otherwise specified, adopt components and devices known in the prior art.

[0023] Example This embodiment discloses a high-rigidity two-stage NGW planetary structure wheel-side drive device, including a frame 2 coaxially disposed within a wheel hub 0, and a motor 1 disposed inside the frame 2. The power output shaft 1-1 of the motor 1 is coaxially connected to a first-stage planetary transmission unit 3, which is located outside the frame 2. A second-stage planetary transmission unit 4 is coaxially disposed between the first-stage planetary transmission unit 3 and the frame 2. The first-stage planetary transmission unit 3 and the second-stage planetary transmission unit 4 are meshed and transmitted, as are the second-stage planetary transmission unit 4 and the wheel hub 0. The motor 1 outputs power, which sequentially drives the wheel hub 0 to rotate relative to the frame 2 through the first-stage planetary unit 3 and the second-stage planetary unit 4. The overall high torque output eliminates or reduces the deformation of the internal gear ring, eliminates the torque tube, reduces the risk of failure, and improves transmission stability and load sharing. At the same time, it reduces unnecessary connecting parts, has a compact structure, improves system rigidity, and improves the load sharing effect of the planetary units. The primary planetary transmission unit 3 includes a primary planetary carrier 3-0, a primary sun gear shaft 3-1, a primary planetary assembly 3-2, and a primary internal gear ring 3-3. The primary sun gear shaft 3-1 is coaxially connected to the power output shaft 1-1, and the free end of the primary sun gear shaft 3-1 extends to the outside of the frame 2. A primary sun gear 3-10 is provided on the outer periphery of the free end of the primary sun gear shaft 3-1. The primary planetary carrier 3-0 is coaxially sleeved on the outer periphery of the primary sun gear 3-10. The primary planetary assembly 3-2 is located inside the primary planetary carrier 3-0, and the primary planetary assembly 3-2 meshes with the primary sun gear 3-10. The primary internal gear ring 3-3 is coaxially sleeved on the outer periphery of the primary planetary carrier 3-0, and the primary internal gear ring 3-3 meshes with the primary planetary assembly 3-2. The primary internal gear ring 3-3 is always fixed. The secondary planetary transmission unit 4 includes a secondary planetary carrier 4-0, a secondary sun gear shaft 4-1, a secondary planetary assembly 4-2, and a secondary internal gear ring 4-3. The secondary sun gear shaft 4-1 is coaxially sleeved on the outer circumference of the primary sun gear shaft 3-1 located inside the primary sun gear 3-10, and the secondary sun gear shaft 4-1 and the primary sun gear shaft 3-1 do not contact each other. The secondary sun gear shaft 4-1 meshes with the inner spline of the inner end of the primary planetary carrier 3-0. The secondary planetary carrier 4-0 is coaxially sleeved on the outer circumference of the secondary sun gear shaft 4-1. The secondary planetary assembly 4-2 is located inside the secondary planetary carrier 4-0 and meshes with the secondary sun gear shaft 4-1. The secondary internal gear ring 4-3 is coaxially sleeved on the outer circumference of the secondary planetary carrier 4-0 and meshes with the secondary planetary assembly 4-2. The secondary internal gear ring 4-3 is connected to the hub 0. The two sides of the secondary planetary carrier 4-0 are fixedly connected to the frame 2 and the primary internal gear ring 3-3, respectively. A support bearing 5 is coaxially provided between the outer circumference of the inner end of the first-stage planetary carrier 3-0 and the inner circumference of the outer end of the second-stage planetary carrier 4-0. It also includes a bearing mounting ring seat 3-4 coaxially fixed to the outer end of the first-stage internal gear ring 3-3. A fourth bearing 3-41 is coaxially provided between the inner circumference of the bearing mounting ring seat 3-4 and the outer circumference of the outer end of the first-stage planetary carrier 3-0. Its function is as follows: the outer end of the first-stage planetary carrier 3-0 is supported and rotates relative to the first-stage internal gear ring 3-3 through the fourth bearing 3-41. At the same time, the outer end of the first-stage planetary carrier 3-0 is limited and supported relative to the second-stage planetary carrier 4-0 through the support bearing 5. Under heavy load conditions, it improves the support rigidity of the first-stage planetary carrier 3-0, avoids the reduction in transmission accuracy caused by the deformation of the first-stage planetary carrier 3-0, improves the transmission accuracy and load-bearing capacity, and improves the overall stability of the device.

[0024] Specifically, a third bearing 6 is coaxially provided between the outer circumference of the second-stage sun gear shaft 4-1 near the inner end and the inner circumference of the second-stage planetary carrier 4-0 near the inner end. A torque sleeve 7 is coaxially fixed at the outer end of the hub 0. The outer circumference of the second-stage internal gear ring 4-3 and the inner circumference of the torque sleeve 7 are connected by spline meshing. Its function is as follows: the secondary sun gear shaft 4-1 is limited and rotates relative to the secondary planetary carrier 4-0 through the third bearing 6, while the outer circumference of the secondary internal gear ring 4-3 is connected to the torque sleeve 7 through splines. The torque sleeve 7 is connected to the hub 0 through bolts. Under high torque conditions, this load-sharing mechanism eliminates or reduces the deformation of the secondary internal gear ring 4-3, while increasing the rigidity and reliability of the system and reducing the assembly complexity.

[0025] In this embodiment, the secondary planetary carrier 4-0 and the primary internal gear ring 3-3 are fixedly connected by a gear ring fixing ring seat 3-31. The gear ring fixing ring seat 3-31 and the secondary planetary carrier 4-0 are fixedly connected by bolts. The gear ring fixing ring seat 3-31 and the primary internal gear ring 3-3 are limited by a fixing plate and fixedly connected by bolts. This ensures that the primary internal gear ring 3-3 is always fixed, while improving the support rigidity between the secondary planetary carrier 4-0 and the primary internal gear ring 3-3, avoiding deformation of the primary internal gear ring 3-3 that would lead to a decrease in transmission accuracy, and improving the overall stability of the device.

[0026] Specifically, the first-stage planetary assembly 3-2 includes multiple first-stage planetary gear shafts 3-21 that are circumferentially and uniformly fixed within the first-stage planetary carrier 3-0. The axis of the first-stage planetary gear shaft 3-21 is parallel to the axis of the power output shaft 1-1. A first-stage planetary gear 3-23 is coaxially sleeved on the outer circumference of any first-stage planetary gear shaft 3-21. A first bearing 3-22 is provided between any first-stage planetary gear shaft 3-21 and the first-stage planetary gear 3-23. Each first-stage planetary gear 3-23 meshes with the first-stage sun gear 3-10.

[0027] In this embodiment, the first-stage planetary carrier 3-0 is provided with a plurality of first inner holes 3-01, and a second inner hole 3-02 is provided from the inner wall of any first inner hole 3-01 to the outer wall of the first-stage planetary carrier 3-0. Each first-stage planetary gear shaft 3-21 is coaxially inserted into each first inner hole 3-01, and is limited and fixed by bolts inserted into the second inner hole 3-02. Specifically, the secondary planetary assembly 4-2 includes multiple secondary planetary gear shafts 4-21 circumferentially evenly arranged within the secondary planetary carrier 4-0, with the axis of the secondary planetary gear shaft 4-21 parallel to the axis of the power output shaft 1-1; a secondary planetary gear 4-23 is coaxially sleeved on the outer circumference of any secondary planetary gear shaft 4-21, and a second bearing 4-22 is provided between any secondary planetary gear shaft 4-21 and the secondary planetary gear 4-23; each secondary planetary gear 4-23 meshes with the secondary sun gear shaft 4-1.

[0028] In this embodiment, the secondary planetary gear shaft 4-21 is fixedly connected to the frame 2 by screws. The outer side of the secondary planetary carrier 4-0 is provided with an oil collection groove. The secondary planetary gear shaft 4-21 is open at both ends and hollow inside. The inner cavity of the secondary planetary gear shaft 4-21 is connected to the oil collection groove, and the side wall of the secondary planetary gear shaft 4-21 is provided with a lubrication through hole 4-210 that is connected to its inner cavity.

[0029] Specifically, at least one fifth bearing 8 is coaxially provided between the frame 2 and the hub 0. In this embodiment, the hub 0 rotates relative to the frame 2 through a pair of double fifth bearings 8.

[0030] In this embodiment, a spacer 01 is provided on the contact surface between the outer end of the hub 0 and the secondary internal gear ring 4-3, that is, the inner side of the secondary internal gear ring 4-3 is axially limited by the spacer 01.

[0031] In this embodiment, the primary sun gear shaft 3-1 is open at both ends and hollow inside. An oil collection cover 10 is coaxially provided on the outer side of the primary sun gear shaft 3-1. An oil collection groove is provided on the oil collection cover 10. The extended end of the oil collection groove extends into the outer port of the primary sun gear shaft 3-1, so that the lubricating oil in the oil collection cover 10 flows through the inner hole of the primary sun gear shaft 3-1 to the input connecting gear sleeve 1-2 to supplement the lubrication of the connecting gear sleeve 1-2.

[0032] The preferred embodiments of this disclosure have been described in detail above with reference to the accompanying drawings. However, this disclosure is not limited to the specific details of the above embodiments. Within the scope of the technical concept of this disclosure, various simple modifications can be made to the technical solutions of this disclosure, and these simple modifications all fall within the protection scope of this disclosure.

[0033] It should also be noted that the various specific technical features described in the above specific embodiments can be combined in any suitable manner without contradiction. In order to avoid unnecessary repetition, this disclosure will not describe the various possible combinations separately.

[0034] Furthermore, the various implementation methods disclosed in this solution can be combined in any way, as long as they do not violate the spirit of this disclosure, they should also be regarded as the content invented by this disclosure.

Claims

1. A high-rigidity two-stage NGW planetary structure wheel-side drive device, comprising a frame (2) coaxially disposed within a wheel hub (0), and a motor (1) disposed inside the frame (2). The power output shaft (1-1) of the motor (1) is coaxially connected to a first-stage planetary transmission unit (3). The first-stage planetary transmission unit (3) is located outside the frame (2). A second-stage planetary transmission unit (4) is coaxially disposed between the first-stage planetary transmission unit (3) and the frame (2). The first-stage planetary transmission unit (3) and the second-stage planetary transmission unit (4) are meshed and driven, as are the second-stage planetary transmission unit (4) and the wheel hub (0). Its characteristics are: The first-stage planetary transmission unit (3) includes a first-stage planetary carrier (3-0), a first-stage sun gear shaft (3-1), a first-stage planetary assembly (3-2), and a first-stage internal gear ring (3-3). The first-stage sun gear shaft (3-1) is coaxially connected to the power output shaft (1-1), and the free end of the first-stage sun gear shaft (3-1) extends to the outside of the frame (2). A first-stage sun gear (3-10) is provided on the outer periphery of the free end of the first-stage sun gear shaft (3-1). The first-stage planetary carrier (3-0) is coaxially sleeved on the outer periphery of the first-stage sun gear (3-10). The first-stage planetary assembly (3-2) is located inside the first-stage planetary carrier (3-0), and the first-stage planetary assembly (3-2) meshes with the first-stage sun gear (3-10). The first-stage internal gear ring (3-3) is coaxially sleeved on the outer periphery of the first-stage planetary carrier (3-0), and the first-stage internal gear ring (3-3) meshes with the first-stage planetary assembly (3-2). The first-stage internal gear ring (3-3) is always fixed. The secondary planetary transmission unit (4) includes a secondary planetary carrier (4-0), a secondary sun gear shaft (4-1), a secondary planetary assembly (4-2), and a secondary internal gear ring (4-3). The secondary sun gear shaft (4-1) is coaxially sleeved on the outer circumference of the primary sun gear shaft (3-1) located inside the primary sun gear (3-10), and the secondary sun gear shaft (4-1) and the primary sun gear shaft (3-1) do not contact each other. The secondary sun gear shaft (4-1) meshes with the inner spline of the inner end of the primary planetary carrier (3-0). The secondary planetary carrier (4-0) is coaxial. The secondary planetary assembly (4-2) is sleeved on the outer circumference of the secondary sun gear shaft (4-1), and is located inside the secondary planetary carrier (4-0), with the secondary planetary assembly (4-2) meshing with the secondary sun gear shaft (4-1); the secondary internal gear ring (4-3) is coaxially sleeved on the outer circumference of the secondary planetary carrier (4-0), and the secondary internal gear ring (4-3) meshes with the secondary planetary assembly (4-2); the secondary internal gear ring (4-3) is connected to the hub (0), and the two sides of the secondary planetary carrier (4-0) are fixedly connected to the frame (2) and the primary internal gear ring (3-3) respectively; The outer circumference of the inner end of the first-stage planetary carrier (3-0) and the inner circumference of the outer end of the second-stage planetary carrier (4-0) are coaxially provided with a support bearing (5), and also include a bearing mounting ring seat (3-4) coaxially fixed to the outer end of the first-stage internal gear ring (3-3). The inner circumference of the bearing mounting ring seat (3-4) and the outer circumference of the outer end of the first-stage planetary carrier (3-0) are coaxially provided with a fourth bearing (3-41).

2. The high-rigidity two-stage NGW planetary structure wheel-side drive device as described in claim 1, characterized in that, A third bearing (6) is coaxially located between the outer circumference of the inner end of the secondary sun gear shaft (4-1) and the inner circumference of the inner end of the secondary planetary carrier (4-0).

3. The high-rigidity two-stage NGW planetary structure wheel-side drive device as described in claim 2, characterized in that, The outer end of the hub (0) is coaxially fixed with a torque sleeve (7), and the outer circumference of the secondary internal gear ring (4-3) and the inner circumference of the torque sleeve (7) are connected by spline meshing.

4. The high-rigidity two-stage NGW planetary structure wheel-side drive device as described in any one of claims 1-3, characterized in that, The primary planetary assembly (3-2) includes multiple primary planetary gear shafts (3-21) that are circumferentially and uniformly fixed within the primary planetary carrier (3-0). The axis of the primary planetary gear shaft (3-21) is parallel to the axis of the power output shaft (1-1). Each first-stage planetary gear shaft (3-21) is coaxially fitted with a first-stage planetary gear (3-23) on its outer circumference. Each first-stage planetary gear shaft (3-21) and the first-stage planetary gear (3-23) are provided with a first bearing (3-22). Each first-stage planetary gear (3-23) meshes with a first-stage sun gear (3-10).

5. The high-rigidity two-stage NGW planetary structure wheel-side drive device as described in claim 4, characterized in that, The secondary planetary assembly (4-2) includes a plurality of secondary planetary gear shafts (4-21) evenly arranged circumferentially within the secondary planetary carrier (4-0), and the axis of the secondary planetary gear shaft (4-21) is parallel to the axis of the power output shaft (1-1); Each secondary planetary gear shaft (4-21) is coaxially fitted with a secondary planetary gear (4-23) on its outer circumference. A second bearing (4-22) is provided between each secondary planetary gear shaft (4-21) and the secondary planetary gear (4-23). ​​Each secondary planetary gear (4-23) meshes with the secondary sun gear shaft (4-1).

6. The two-stage NGW planetary structure wheel-side drive device as described in claim 5, characterized in that, The outer side of the secondary planetary carrier (4-0) is provided with an oil collection groove. The secondary planetary gear shafts (4-21) are open at both ends and hollow inside. The inner cavity of the secondary planetary gear shaft (4-21) is connected to the oil collection groove, and the side wall of the secondary planetary gear shaft (4-21) is provided with a lubrication through hole (4-210) that is connected to its inner cavity.

7. The high-rigidity two-stage NGW planetary structure wheel-side drive device as described in claim 6, characterized in that, The secondary planetary gear shaft (4-21) is fixedly connected to the frame (2).

8. The high-rigidity two-stage NGW planetary structure wheel-side drive device as described in claim 7, characterized in that, At least one fifth bearing (8) is coaxially provided between the frame (2) and the hub (0).

9. The high-rigidity two-stage NGW planetary structure wheel-side drive device as described in claim 8, characterized in that, The outer end of the hub (0) is provided with a spacer (01) on the contact surface between it and the secondary internal gear ring (4-3).

10. The high-rigidity two-stage NGW planetary structure wheel-side drive device as described in claim 9, characterized in that, The first-stage sun gear shaft (3-1) is open at both ends and hollow inside. An oil collection cover (10) is coaxially provided on the outer side of the first-stage sun gear shaft (3-1). An oil collection groove is provided on the oil collection cover (10). The extended end of the oil collection groove extends into the outer port of the first-stage sun gear shaft (3-1).

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