Electric push rod for driving solar support

Abstract

The utility model discloses an electric push rod used for driving a solar support. The electric push rod comprises a motor, a gear box, a bearing seat, a carrying bearing, an upper connecting piece, a lead screw, a telescopic pipe and an outer pipe. A limiting shaft shoulder, a first thread and a second thread are sequentially arranged on the lead screw and located on the two sides of the bearing ring. The first bearing nut and the second bearing nut are screwed to the first thread and the second thread respectively so as to be connected to the lead screw. Pushing and pulling force borne by the lead screw is transmitted to the bearing through the first bearing nut and the second bearing nut, and the situation that a narrow shaft shoulder bears the main load is avoided. The bearing bearing is arranged in the bearing seat and axially limited by the bearing seat and the upper connecting piece, the bearing bearing transmits the axial load to the bearing seat and the upper connecting piece, and the situation that the gear box wall bears the axial main load is avoided.

Description

Technical Field

[0001] This utility model relates to the field of electric linear actuator technology, and in particular to an electric linear actuator used to drive solar panels as a motion actuator in a solar photovoltaic power generation system to track sunlight. Background Technology

[0002] An electric linear actuator is an electric drive device that converts the rotary motion of an electric motor into the linear reciprocating motion of a lead screw. It can be widely used in industries such as automotive, furniture, medical, solar power, industrial control, and drive systems, and features reliable performance, sensitive operation, smooth running, and good environmental adaptability.

[0003] In photovoltaic (PV) power generation systems, to improve power generation efficiency, actuators are used to drive PV panels to rotate in response to sunlight, adjusting the angle of illumination to maximize sunlight exposure. Specifically, the PV panels are mounted on a support structure, and the actuators drive the support structure to rotate, adjusting the angle at which the PV panels receive sunlight. Electric actuators are one important type of actuator. In this application, the electric actuator must output the dynamic load driving the rotation of the PV panels and the support structure itself, while also withstanding additional static loads generated under extreme weather conditions, such as wind pressure from strong winds and the weight of accumulated snow. Therefore, the ultimate static load value is typically 6 to 10 times the dynamic load value. For example, in a typical application, the dynamic load force is 15 kN, and the static load force is 110 kN. This necessitates a rational design of the load-bearing structure of the solar panel support electric actuator to ensure reliability while reducing costs and improving economic efficiency.

[0004] Currently, electric linear actuators used in solar power systems mainly consist of a motor, a gearbox, and a telescopic rod. The motor drives the lead screw to rotate via the gearbox, and the lead screw nut converts the rotational motion into linear motion, driving the telescopic rod to perform linear reciprocating motion. The lead screw has a shoulder, forming an annular stepped surface perpendicular to the lead screw axis. This annular stepped surface directly or indirectly supports the load-bearing bearing. After the thrust or tension force on the telescopic rod is transmitted to the lead screw, at least one direction of force needs to be transmitted directly or indirectly to the load-bearing bearing through this annular stepped surface. Due to cost and structural space constraints, the lead screw diameter cannot be too large. Moreover, due to the influence of the lead screw thread root diameter, the area of ​​the annular stepped surface on the lead screw that can be used to transmit loads is usually relatively small, resulting in high unit pressure at the contact point. This places high demands on the strength of the lead screw material and the structural design. Since the lead screw is a slender component, its helical section and the load-bearing shoulder section are usually manufactured as a single piece. The length of the helical section is generally 8-15 times or more than that of the load-bearing shoulder section. High-performance materials mean higher overall lead screw material costs, which is detrimental to the product's cost-effectiveness.

[0005] Gearbox housings are generally made of cast aluminum alloy. To support the load on the bearings, common methods include increasing wall thickness and / or reinforcing ribs. Inserts or load-bearing screws can also be incorporated, or the gearbox can be made entirely of steel. However, these solutions all introduce structural complexity, manufacturing difficulties, or increased costs. In the prior art, Chinese patent CN210111913U discloses a solar-powered electric actuator. External load and impact forces are transmitted sequentially to the load-bearing plate, gear housing, gear cover, and load-bearing seat via a thrust bearing on a lead screw. These sequentially contacting parts require a certain wall thickness to ensure load-bearing strength, which obviously increases material usage and costs. Furthermore, Chinese patent CN210921839U discloses a solar-powered moving actuator. External thrust and pull forces act on a reinforcing plate through a thrust bearing and are ultimately transmitted to the load-bearing seat. Since the load-bearing seat and reinforcing plate do not directly contact each other, multiple screws (first screw, second screw, second nut, and second nut) passing through the gearbox and load-bearing seat are installed between the load-bearing seat and reinforcing plate to improve the overall structural stability and load-bearing strength. However, this design is structurally complex due to the use of multiple screws and nuts. The first and second screws need to pass through the gearbox and load-bearing seat sandwiched between the load-bearing seat and the reinforcing plate. The screws are long, affecting their strength and rigidity, and improving the screw performance also has a certain impact on cost. Under large external loads, sudden changes, or extreme weather conditions, the slender screws are also prone to deformation, thus affecting the load-bearing capacity. Furthermore, the gearbox wall and load-bearing seat sandwiched between the load-bearing seat and the reinforcing plate are still subject to significant external push and pull forces, requiring a certain wall thickness and strength, which also increases material costs. Utility Model Content

[0006] This invention proposes an electric push rod for driving solar panel brackets, which has a superior load-bearing structure, improves the ability of the lead screw to transmit axial load, avoids the external main load acting on the gearbox wall, helps save material costs, and meets the needs of more installation scenarios.

[0007] The technical solution of this utility model is:

[0008] An electric actuator for driving a solar panel mounting bracket includes a gearbox, a rod assembly at one end of the gearbox, a motor, a bearing housing at the other end of the gearbox, and an upper connector mounted on the bearing housing. The gearbox includes a housing and a cover, and its inner cavity accommodates a transmission gear set. The rod assembly includes an outer tube connected to the housing, and a lead screw, a lead screw nut, and a telescopic rod are coaxially arranged inside the tube. The lead screw nut is threaded onto the lead screw and moves along the length of the lead screw through the thread. The telescopic rod is connected to the lead screw nut. The output shaft end of the motor and the upper end of the lead screw both extend into the gearbox and are connected by the transmission gear set.

[0009] Furthermore, the upper end of the lead screw extends into the bearing housing, and the bearing housing and the lead screw are coaxially and fixedly connected to the gearbox cover; the bearing housing has an upper opening, a bearing chamber, a lower base plate and a base plate through hole, and the load bearing is installed into the inner cavity of the bearing chamber through the upper opening and abuts against the lower base plate; the upper end of the lead screw extends into the inner hole of the load bearing through the base plate through hole.

[0010] Preferably, the bearing housing is made of steel, and the gearbox housing and cover are made of aluminum. The bearing housing and cover are fixedly connected by screws.

[0011] Furthermore, the upper connector is fixedly connected to the upper end of the bearing housing, and the lower end face of the upper connector abuts against the upper end face of the bearing, thereby axially confining the bearing within the inner hole of the bearing housing.

[0012] Preferably, the load-bearing bearing is a double-direction thrust bearing, and the upper connecting piece is fixedly connected to the bearing housing by screws.

[0013] Furthermore, the upper end of the lead screw has a shoulder, and a first thread is provided above the shoulder. The diameter of the shoulder is larger than the diameter of the first thread. The first nut is screwed onto the first thread and directly or indirectly abuts against the shoulder, and is axially limited in one direction.

[0014] Furthermore, a cylindrical section is provided above the first thread of the lead screw, the diameter of which is smaller than the diameter of the first thread; a bearing ring is fitted on the cylindrical section, and the inner hole of the bearing ring is fitted with the outer circle of the cylindrical section.

[0015] The bearing ring also has a stepped surface and a smaller stepped outer circle, which extends into the inner hole of the moving ring of the bearing and fits in, so that the bearing, the cylindrical section of the lead screw, and the bearing ring are installed basically concentrically; the lower end of the bearing ring abuts against the first nut, and the upper stepped surface abuts against the bearing, thereby achieving axial positioning.

[0016] Furthermore, the upper end of the lead screw is provided with a second thread, located above the cylindrical section, and the second nut is screwed onto the second thread and abuts against the moving ring of the bearing.

[0017] Furthermore, a non-circular shaft section is provided above the second threaded section of the lead screw, and a locking ring with a corresponding non-circular inner hole is sleeved on the non-circular shaft section to achieve circumferential fixation of the lead screw and the locking ring; the locking ring is fixedly connected to the second nut circumferentially, and the two cannot rotate relative to each other.

[0018] Preferably, the non-circular shaft section is a flat shaft section, and the non-circular inner hole is a flat inner hole.

[0019] Furthermore, the lower end face of the upper connector has a groove, and an elastic element is disposed in the groove to provide axial preload for the bearing.

[0020] By adopting the above technical solution, this utility model has the following beneficial effects:

[0021] (1) In this utility model, the first nut is screwed onto the first thread section and is limited by the shoulder, which avoids the transmission of the axial main load force through the narrow shoulder ring surface. Instead, the main load force is distributed through multiple turns of the first thread. The shoulder mainly bears the limiting function of the first nut, which improves the load capacity of the screw or makes it possible to reduce the screw diameter, which is beneficial to improving product performance or reducing material costs.

[0022] (2) In this utility model, the upper connecting part, bearing seat, and bearing bearing are located at the very end of the electric push rod, serving as the force-bearing support part of the electric push rod. The tension and pressure on the bearing screw are directly transmitted to this support part, without the need for the transmission of the main load through the gearbox body or cover. This avoids the need for a load-bearing structure design for the already relatively complex gearbox, thus simplifying the gearbox structure or reducing the thickness of the gearbox wall, which is beneficial for simplifying the design and reducing material costs. Secondly, when the load-bearing capacity of the electric push rod needs to be increased, only the parts of the aforementioned force-bearing support part need to be adjusted. For example, by adjusting the thickness or selecting a higher strength material to make the force-bearing support part, the load-bearing requirements can be met. The complex gearbox and rod parts can be directly interchangeable, which is beneficial for product standardization and mass production, and reduces design costs and mold investment costs. Attached Figure Description

[0023] To make the content of this utility model easier to understand, the present utility model will be further described in detail below with reference to specific embodiments and accompanying drawings, wherein:

[0024] Figure 1 This is an external view of Example 1;

[0025] Figure 2 This is an exploded perspective view of Example 1;

[0026] Figure 3 for Figure 2 Enlarged view of section A in the image;

[0027] Figure 4 This is a cross-sectional structural diagram of Example 1;

[0028] Figure 5 This is a schematic diagram of a partial cross-section of Example 1.

[0029] Figure 6 This is a schematic diagram of a partial cross-section of Example 2.

[0030] The labels in the attached diagram are:

[0031] 1. Gearbox; 2. Rod assembly; 3. Motor; 4. Bearing housing; 5. Upper connector; 6. Housing; 7. Cover; 8. Transmission gear set; 9. Outer tube; 10. Lead screw; 11. Lead screw nut; 12. Telescopic rod; 13. Upper opening; 14. Bearing chamber; 15. Lower base plate; 16. Base plate through hole; 17. Bearing bearing; 18. Upper connecting hole; 19. Lower connector; 20. Lower connecting hole; 21. Shoulder; 22. First thread; 23. First nut; 24. Cylindrical section; 25. Bearing ring; 26. Stepped annular surface; 27. Stepped outer circle; 28. Second thread; 29. ​​Second nut; 30. Non-circular shaft section; 31. Locking ring; 32. Non-circular inner hole; 33. Groove; 34. Elastic element.

[0032] Bearing housing 4′, bearing partition 15′, bearing bearing 17′, first nut 23′, second nut 29′. Detailed Implementation

[0033] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain this utility model and are not intended to limit this utility model.

[0034] The implementation of this utility model will be described in detail below with reference to specific embodiments.

[0035] In the accompanying drawings of this embodiment, the same or similar reference numerals correspond to the same or similar components. In the description of this utility model, it should be understood that if terms such as "upper," "lower," "left," and "right" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, they are only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the terms used to describe positional relationships in the drawings are only for illustrative purposes and should not be construed as limiting this patent. For those skilled in the art, the specific meaning of the above terms can be understood according to the specific circumstances.

[0036] In a preferred embodiment, such as Figures 1 to 5 The electric actuator in the solar photovoltaic power generation system shown, which tracks sunlight, includes a gearbox 1, a rod assembly 2 at one end of the gearbox 1, a motor 3, a bearing housing 4 at the other end of the gearbox 1, and an upper connector 5 mounted on the bearing housing 4. The bearing housing 4 and the upper connector 5 are fixedly connected by screws. The central axis of the rod assembly 2 is parallel to the central axis of the motor 3, and the central axes of the bearing housing 4 and the upper connector 5 coincide with the central axis of the rod assembly 2. This central axis coincidence can be achieved using common methods such as circumferential fitting or pin positioning.

[0037] The gearbox 1 comprises a housing 6 and a cover 7, which are fixedly connected by screws, forming an inner cavity that accommodates a transmission gear set 8. The rod assembly 2 includes an outer tube 9 connected to the housing 6, within which a bidirectional rotatable lead screw 10 is coaxially mounted. A lead screw nut 11 is screwed onto the lead screw 10 and is restricted from rotating relative to it; a telescopic rod 12 is fixedly connected to the lead screw nut 11. The output shaft end of the motor 3 and the upper end of the lead screw 10 both extend into the gearbox 1 and are respectively connected to the input and output ends of the transmission gear set 8 within the gearbox 1, forming a reduction transmission mechanism. The motor 3 drives the lead screw 10 to rotate bidirectionally and reversibly via the transmission gear set 8, thereby driving the lead screw nut 11 to move the telescopic rod 12 in a reciprocating linear motion along the lead screw axis.

[0038] The bottom end face of the bearing housing 4 abuts against the cover 7 and can be fixedly connected by welding, riveting, snap-fitting, screw connection, etc. In this embodiment, multiple screws are preferred for connection. The bearing housing 4 has an upper opening 13, a bearing chamber 14, a lower base plate 15, and a bottom plate through hole 16. A load-bearing bearing 17 is installed in the bearing chamber 14. During assembly, the load-bearing bearing 17 is installed into the bearing chamber 14 through the upper opening 13. The outer circle of the load-bearing bearing 17 fits with the inner circle wall of the bearing chamber 14 to form radial positioning. The lower end face of the load-bearing bearing 17 abuts against the lower base plate 15 of the bearing housing 4. The upper end of the lead screw 10 extends through the bottom plate through hole 16 into the inner hole of the load-bearing bearing 17 for rotatable connection with the load-bearing bearing 17.

[0039] The upper connecting piece 5 is fixedly connected to the upper end of the bearing housing 4, and the lower end face of the upper connecting piece 5 abuts against the upper end face of the bearing 17, thereby axially confining the bearing 17 within the bearing housing 4. The bearing 17 can be a deep groove ball bearing, a one-way thrust bearing, a two-way thrust bearing, a tapered roller bearing, etc., or a bearing assembly composed of different bearings. In this embodiment, a two-way thrust bearing is preferred. The upper connecting piece 5 has an upper connecting hole 18 for connecting to external equipment; a lower connecting piece 19 with a lower connecting hole 20 is installed at the lower end of the telescopic rod 12 for connecting to external equipment.

[0040] The upper end of the lead screw 10 has a shoulder 21, and a first thread 22 is provided above the shoulder 21. The diameter of the shoulder 21 is larger than the diameter of the first thread 22. A first nut 23 is screwed onto the first thread 22 and directly or indirectly abuts against the shoulder 21, and is axially limited in one direction. Both the shoulder 21 and the first thread 22 are concentrically arranged with the axis of the lead screw.

[0041] Above the first thread 22 of the lead screw, a cylindrical section 24 is provided, which is concentric with the axis of the lead screw and has a diameter smaller than that of the first thread 22. A bearing ring 25 is fitted onto the cylindrical section 24, with its inner hole fitting into the outer circle of the cylindrical section 24. The bearing ring 25 also has a stepped annular surface 26 and a smaller stepped outer circle 27, which extends into and fits into the inner hole of the moving ring of the bearing 17, ensuring that the bearing 17, the cylindrical section 24 of the lead screw 10, and the bearing ring 25 are installed substantially concentrically. The lower end of the bearing ring 25 abuts against the first nut 23, and the upper stepped annular surface 26 abuts against the end face of the moving ring of the bearing 17, achieving axial positioning. By appropriately selecting a double-acting thrust bearing as the bearing 17 and appropriately configuring the diameter of the bearing ring 25, the area of ​​the stepped annular surface 26 can be effectively increased, thereby reducing the load-bearing capacity per unit area.

[0042] When the electric actuator receives an upward thrust along the screw axis, the lower connector 19, after receiving the external transmission screw 10, will sequentially transmit the force to the first thread 22, the first nut 23, the bearing ring 25, the stepped annular surface 26, and the moving ring of the bearing bearing 17. The advantage of this is that, since the first thread 22 has multiple turns, the thrust can be effectively distributed along each turn, and then transmitted through the upper end face of the first nut 23. This avoids the need for a narrow radial shoulder on the screw 10 to bear the thrust; or the need to use a thicker screw diameter to increase the radial width of the shoulder, which would increase material and processing costs. According to the solution described in this invention, the shoulder 21 only needs to bear the tightening force of tightening the first nut 23, which is far lower than the maximum upward thrust that the external mechanism can actually apply.

[0043] In this embodiment, another function of the bearing ring 25 is to better maintain the concentricity of the lead screw 10 and the bearing 17. In the above solution, the bearing ring 25 can also be omitted; an alternative is to have the first nut 23 directly abut against the lower end face of the bearing 17, achieving the same effect of transmitting axial thrust. Other structural solutions can be adopted to ensure the concentricity of the lead screw 10 and the bearing 17, such as providing a ring-shaped part with a mating relationship between the lead screw and the bearing, or providing a cylindrical section on the lead screw whose outer circle directly mates with the bearing.

[0044] In this embodiment, a second thread 28 is provided above the cylindrical section 24 of the lead screw, and a second nut 29 is screwed onto the second thread and abuts against the upper end of the moving ring of the bearing 17 for limiting. When an external mechanism applies a downward pulling force to the electric push rod, the pulling force is transmitted through the lead screw 10 to the second thread 28, the second nut 29, and the moving ring of the bearing 17.

[0045] When the electric actuator is subjected to an upward thrust, the upper end face of the bearing 17 abuts against the lower end face of the upper connector 5, and the upward thrust is ultimately transmitted to the external mechanism through the upper connecting hole 18. When the electric actuator is subjected to an upward thrust, the lower end face of the bearing 17 abuts against the lower end plate 15 of the bearing seat 4, and the downward pull is transmitted to the upper connector 5 through the bearing seat, and then to the external mechanism through the upper connecting hole 18.

[0046] In summary, regardless of whether the lower connector 19 of the electric actuator is subjected to external thrust or tension, the load-bearing bearing 17 will transmit the force to the bearing seat 4 and the upper connector 5. During the force transmission process, the gearbox 1's housing 6 and cover 7 do not participate in the transmission of the main external forces. Therefore, it is not necessary to set up relatively complex load-bearing structures within them, or to appropriately reduce the wall thickness and size, which is beneficial for simplifying the design and reducing material costs. Secondly, when it is necessary to increase the load-bearing capacity of the electric actuator, it is only necessary to adjust the main load-bearing parts such as the bearing seat 4, the upper connector 5, and the load-bearing bearing 17. For example, by adjusting the thickness or selecting a higher-strength material to make the load-bearing support, the load-bearing requirements can be met. Complex gearbox and rod parts can be directly interchangeable, which is beneficial for product standardization and mass production, and reduces design costs and mold investment costs.

[0047] In this embodiment, the bearing housing 4 is made of steel, and the gearbox 1 housing 6 and cover 7 are made of aluminum. The bearing housing 4 and cover 7 are fixedly connected by screws.

[0048] Above the second thread 28 of the lead screw 10, there is a non-circular shaft section 30. A locking ring 31 with a corresponding non-circular inner hole 32 is fitted onto the non-circular shaft section 30, preventing the lead screw 10 and the locking ring 31 from rotating relative to each other. The locking ring 31 has multiple through holes, and the second nut 29 has at least one corresponding threaded hole. The locking ring 31 is fixedly connected to the second nut 29 by screws, preventing them from rotating relative to each other and effectively preventing the second nut 29 from loosening.

[0049] In this embodiment, the non-circular shaft segment 30 is a flat shaft segment, and the non-circular inner hole 32 is a flat inner hole.

[0050] The lower end face of the upper connector 5 has a groove 33, and an elastic element 34 is disposed in the groove 33 to provide axial preload for the bearing 17.

[0051] (Example 2)

[0052] like Figure 6As shown, the overall structure is similar to that of Embodiment 1, except that two unidirectional thrust bearings are used instead of the bidirectional thrust bearings as the load bearings 17′, and the structure of the bearing housing 4′ is also adjusted accordingly. The bearing housing 4′ has a load-bearing partition 15′ inside. The two load bearings 17′ are located on both sides of the load-bearing partition 15′. The fixed rings of the two unidirectional thrust bearings serving as load bearings 17′ abut against both sides of the load-bearing partition 15′, the upper end of the first nut 23′ abuts against the moving ring of the lower load bearing 17′, and the lower end of the second nut 29′ abuts against the moving ring of the upper load bearing 17′. Alternatively, a single load ring can be placed between the first nut 23′ or the second nut 29′ and the moving ring of the load bearing, or two load rings can be placed between the first nut 23′, the second nut 29′, and the moving ring of the load bearing, respectively. The scheme for achieving concentricity between the lead screw 10 and the load bearings is similar to that of the first embodiment. Similarly, in this embodiment, deep groove ball bearings and tapered roller bearings can be used instead of the unidirectional thrust bearings, or combinations of different types of bearings can be used. The thrust or pull force on the electric actuator is transmitted to the bearing 17' via the lead screw 10, and then to the bearing seat 4' via the bearing partition 15', and further to the upper connecting member 5. In this embodiment, a pre-tightening structure similar to that in Embodiment 1 can be provided between the upper connecting member 5 and the bearing 17', or the second nut 29' can directly apply axial pre-tightening force to the bearing 17', without providing other pre-tightening parts or structures.

[0053] The specific embodiments described above further illustrate the purpose, technical solution, and beneficial effects of this utility model. It should be understood that the above descriptions are merely specific embodiments of this utility model and are not intended to limit this utility model. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of this utility model should be included within the protection scope of this utility model.

Claims

1. An electric actuator for driving a solar panel mounting bracket, comprising: A gearbox (1) is provided with a rod assembly (2) and a motor (3) at one end and a bearing seat (4) at the other end. The gearbox (1) includes a housing (6), a cover (7), and a transmission gear set (8). The central axes of the rod assembly (2) and the motor (3) are parallel. The bearing seat (4) is provided with an upper connecting member (5) and a load-bearing bearing (17) inside. The bearing seat (4), the upper connecting member (5), and the central axis of the rod assembly (2) coincide. The rod assembly (2) includes a lead screw (10), the upper end of which passes through the gearbox (1) and extends to the load-bearing bearing (17). The inner hole is characterized in that: the upper end of the lead screw (10) includes a shoulder (21) with a diameter decreasing sequentially, a first thread (22) and a cylindrical section (24), a first nut (23) is screwed onto the first thread (22), the first nut (23) abuts against the shoulder (21), the bearing (17) is disposed above the first nut (23), and the cylindrical section (24) ensures that the lead screw (10) and the bearing (17) are concentric. When there is a thrust upward along the axial direction of the lead screw, the first thread (22) distributes the thrust to each turn of the helix, and then transmits it directly or indirectly to the bearing (17) through the upper end face of the first nut (23).

2. The electric actuator for driving a solar panel mounting bracket according to claim 1, characterized in that: The bearing housing (4) has an upper opening (13), a bearing chamber (14), a lower base plate (15), and a base plate through hole (16). The bearing (17) is installed into the bearing chamber (14) through the upper opening (13). The outer circle of the bearing (17) is engaged with the inner wall of the bearing chamber (14) to form a radial positioning. The lower end face of the bearing (17) abuts against the lower base plate (15) of the bearing housing (4).

3. An electric actuator for driving a solar panel mounting bracket according to claim 1, characterized in that: The upper connector (5) is fixedly connected to the upper end of the bearing seat (4), and the lower end face of the upper connector (5) abuts against the upper end face of the bearing (17), thereby axially confining the bearing (17) in the bearing seat (4).

4. An electric actuator for driving a solar panel mounting bracket according to claim 1, characterized in that: The cylindrical segment (24) is fitted with a bearing ring (25) whose inner hole mates with the outer wall of the cylindrical segment (24). The bearing ring (25) has a stepped annular surface (26) and a stepped outer circle (27). The stepped outer circle (27) extends into and mates with the inner hole of the moving ring of the bearing bearing (17). The stepped annular surface (26) abuts against the lower end of the bearing bearing (17). The first nut (23) abuts against the lower end of the bearing ring (25). The bearing bearing (17), the bearing ring (25), and the cylindrical segment (24) are installed concentrically.

5. An electric actuator for driving a solar panel mounting bracket according to claim 1, characterized in that: A second thread (28) is provided above the cylindrical section (24), and a second nut (29) is screwed onto the second thread (28). The second nut (29) is positioned and abuts against the upper end of the moving ring of the bearing (17).

6. An electric actuator for driving a solar panel mounting bracket according to claim 5, characterized in that: Above the second thread (28), there is a non-circular shaft section (30), on which a locking ring (31) is fitted. The locking ring (31) has a non-circular inner hole (32) corresponding to the non-circular shaft section (30). The lead screw (10) is adapted to cooperate with the non-circular shaft section (30) through the non-circular inner hole (32) and maintain circumferential fixation with the locking ring (31).

7. An electric actuator for driving a solar panel mounting bracket according to claim 6, characterized in that: The locking ring (31) has multiple through holes, and the second nut (29) has at least one corresponding threaded hole. The locking ring (31) is fixedly connected to the second nut (29) by screws.

8. An electric actuator for driving a solar panel mounting bracket according to claim 6, characterized in that: The non-circular shaft section (30) is a flat shaft section, and the non-circular inner hole (32) is a flat inner hole.

9. An electric actuator for driving a solar panel mounting bracket according to claim 3, characterized in that: The lower end face of the upper connector (5) has a groove (33), in which an elastic element (34) is provided to provide axial preload for the bearing (17).

10. An electric actuator for driving a solar panel mounting bracket according to claim 1, characterized in that: The load-bearing bearing (17) is a deep groove ball bearing, a one-way thrust bearing, a two-way thrust bearing, a tapered roller bearing, or a bearing assembly composed of different bearings.

11. An electric actuator for driving a solar panel mounting bracket according to claim 10, characterized in that: The bearing (17) consists of two unidirectional thrust bearings. The bearing housing is provided with a bearing partition (15'). The two unidirectional thrust bearings are located on both sides of the bearing partition (15'), and the fixed rings of the two unidirectional thrust bearings abut against both sides of the bearing partition (15'). The upper end of the first nut abuts directly or indirectly against the moving ring of the lower unidirectional thrust bearing.

Images