A pressure-bearing deceleration device for a flexible tracking support

Abstract

The utility model belongs to the technical field of speed reducer, disclose a kind of pressure reduction device for flexible tracking support, including shell, worm body, worm and end cover, shell is provided with worm cavity and worm cavity in, bearing seat is provided in worm cavity, worm body is provided with pressure bearing bin, gear section and output shaft, the pressure bearing bin of worm body is inlayed with pressure bearing, pressure bearing is simultaneously set on bearing seat, worm rotation is installed in worm cavity, and is engaged with gear section, end cover is set on output shaft, and fixedly installed on shell;The utility model whole simple structure can disperse axial load, reduce the abrasion of main force component, simplify whole structure, improve use effect.

Description

Technical Field

[0001] This utility model belongs to the field of speed reducer technology, specifically, it relates to a pressure-bearing speed reduction device for a flexible tracking bracket. Background Technology

[0002] In the photovoltaic industry, tracking brackets are key equipment for improving the efficiency of solar power generation. As the core transmission component of the tracking bracket, the rotary reducer is widely used in the photovoltaic industry because it can withstand large axial and radial loads. Its performance directly affects the operational stability, load-bearing capacity and service life of the bracket.

[0003] However, since the raceway base of the rotary reducer is made of ductile iron, the wear resistance of the raceway is generally not high due to the upper limit of the material's heat treatment, which affects the overall service life of the reducer.

[0004] In addition, most existing speed reducers typically have raceway grooves machined at the rotating positions of the worm gear and worm to enable rotation. If they are damaged by stress, the entire reducer needs to be replaced, which is costly.

[0005] Chinese patent application CN2021213967780 discloses a novel solar-powered sun-tracking reducer, comprising a flat washer, an external hexagonal bolt, a top plate, a first skeleton oil seal, and a base. The external hexagonal bolt is installed inside the flat washer, with its front end connected to the top plate. The base is located at the front end of the top plate, and the top plate is connected to the base via the flat washer and the external hexagonal bolt. The first skeleton oil seal is located on the inner side of the top plate. A plug is threaded onto the upper surface of the base, and a grease nipple is fixedly installed below the base, with a grease nipple cap movably connected to its front end. A worm gear is installed below the interior of the base, with a pressure bearing fixedly installed on the outer side of the worm gear, and a sliding bearing fixedly installed in the middle of the base. This novel solar-powered sun-tracking reducer features a central shaft manufactured using the ADI process. The central shaft, produced from isothermally hardened ductile iron, not only reduces the overall manufacturing cost of the reducer but also ensures the overall corrosion resistance and strength of the device.

[0006] However, this patent mainly relies on the cooperation between the worm gear and the central shaft to achieve force transmission and support, and does not design a special pressure-bearing structure for high load scenarios, resulting in limited overall load-bearing capacity. Especially in working conditions such as flexible tracking brackets that need to withstand large axial and radial combined loads, the concentrated force can easily lead to accelerated wear of key components, thereby affecting the overall service life of the deceleration device. Utility Model Content

[0007] The main technical problem to be solved by this utility model is to provide a pressure-bearing deceleration device for flexible tracking brackets with a simple overall structure. It can decompose and transmit axial loads to achieve stable bearing of axial loads, while also dispersing radial loads, reducing wear of main load-bearing components, simplifying the overall structure, effectively solving the problem of insufficient wear resistance of traditional ductile iron raceways, and significantly extending the overall service life of the deceleration device. It is suitable for the long-term outdoor heavy-load operation requirements of photovoltaic flexible tracking brackets.

[0008] To solve the above-mentioned technical problems, this utility model provides the following technical solution:

[0009] A pressure-bearing deceleration device for a flexible tracking bracket includes a housing, a worm gear body, a worm, and an end cap. The housing has a worm gear cavity and a worm cavity. A bearing seat is provided in the worm gear cavity. The worm gear body has a pressure-bearing bearing compartment, a gear segment, and an output shaft. A pressure-bearing bearing is embedded in the pressure-bearing bearing compartment of the worm gear body and is also sleeved on the bearing seat. The worm is rotatably installed in the worm cavity and meshes with the gear segment. The end cap is sleeved on the output shaft and fixedly installed on the housing.

[0010] The following are further optimizations of the above technical solution by this utility model:

[0011] The bearing seat on the housing is a protruding cylindrical structure. A first limiting body is provided on the inner wall of the housing. A bolting structure is provided on the outer end face of the housing. A threaded mounting hole is provided near the opening of the worm gear cavity.

[0012] Further optimization: The worm gear cavity is designed as a concave circular structure, the gear segment is fan-shaped and arranged at a specific angle, and a second limiting body is provided at both ends of the gear segment. Multiple flange fixing holes are provided at the output shaft position away from the worm gear cavity.

[0013] Further optimization: The worm is configured with a meshing part in the middle, which meshes with the worm wheel body. Both ends of the meshing part are provided with bearing positions, and rolling bearings are sleeved on the bearing positions. The two rolling bearings are fixedly installed in the worm cavity. The pressure cover is sleeved on the worm and threaded into the threaded mounting hole.

[0014] Further optimization: A sliding bearing mounting part is provided on the inner wall of the end cover, and the outer surface of the sliding bearing is embedded in the inner wall of the sliding bearing mounting part and slides in cooperation with the output shaft;

[0015] The sliding bearing is made of wear-resistant material.

[0016] Further optimization: A second oil seal groove is provided on the inner wall of the end cover near the sliding bearing mounting part, and a second sealing ring groove is provided on the outer surface of the end cover;

[0017] The end cap is also equipped with a first sealing part that serves a sealing function.

[0018] Further optimization: The first sealing part includes a first sealing ring placed in the second sealing ring groove, and the first sealing ring simultaneously abuts against the inner wall of the worm gear cavity near the edge;

[0019] The first oil seal is placed in the second oil seal groove, and the first oil seal is in contact with the outer surface of the output shaft near the edge.

[0020] Further optimization: The gland is also provided with a second sealing part that also serves a sealing function, and the outer surface of the gland is also provided with multiple mounting holes.

[0021] Further optimization: The pressure bearing is selected from tapered roller bearings that can withstand axial pressure.

[0022] The present invention adopts the above technical solution and has the following beneficial effects:

[0023] This utility model adopts the above-mentioned technical solution, which is ingenious in conception and reasonable in structure. It can optimize load bearing and distribution. By using tapered roller bearings as the bearing bearing, its tapered raceway and roller structure can decompose the axial load into radial and axial components. The axial component is transmitted to the housing through the outer ring of the bearing, while the radial component is borne by the inner ring of the bearing and the worm gear body, thus realizing the stable transmission and distribution of axial load. At the same time, the output shaft forms an auxiliary support through the cooperation of sliding bearings and end caps, which shares part of the radial load, reduces the load on the main load-bearing components, reduces the wear rate, and is suitable for flexible tracking brackets to bear large axial and radial combined loads.

[0024] The overall structure is simple in design, with each component fitting together tightly. Multiple sealing parts are provided (the first sealing part includes a first sealing ring and a first oil seal, and the second sealing part includes a second sealing ring and a second oil seal), which effectively prevents internal lubricating oil leakage and external dust and moisture intrusion, ensuring the reliability of the device in complex environments.

[0025] To reduce maintenance costs, compared to traditional speed reducers where the worm gear and worm shaft need to be replaced entirely after being damaged by stress, the bearings and other vulnerable parts in this device are standard parts, which are easy to purchase and replace, thus reducing maintenance costs.

[0026] The present invention will be further described below with reference to the accompanying drawings and embodiments. Attached Figure Description

[0027] Figure 1 This is a schematic diagram of the overall structure in an embodiment of the present utility model;

[0028] Figure 2 This is an exploded view of the overall structure in an embodiment of this utility model;

[0029] Figure 3 This is a front view of the overall structure in an embodiment of this utility model;

[0030] Figure 4 This is an embodiment of the present utility model. Figure 3 Schematic diagram of the AA section;

[0031] Figure 5 This is a schematic diagram of the shell structure in an embodiment of the present utility model;

[0032] Figure 6 This is a schematic diagram of the shell structure from another perspective in an embodiment of this utility model;

[0033] Figure 7 This is a front view of the housing in an embodiment of the present utility model;

[0034] Figure 8 This is a schematic diagram of the worm gear body in an embodiment of the present invention;

[0035] Figure 9 This is a schematic diagram of the output shaft in an embodiment of the present invention;

[0036] Figure 10 This is a schematic diagram of the end cap structure in an embodiment of the present utility model;

[0037] Figure 11 This is a structural schematic diagram of the end cap from another perspective in an embodiment of this utility model;

[0038] Figure 12 This is a schematic diagram of the worm gear structure in an embodiment of this utility model;

[0039] Figure 13 This is a schematic diagram of the structure of the pressure cap in an embodiment of this utility model.

[0040] In the diagram: 1. Housing; 12. Worm gear cavity; 121. Bearing housing; 13. Worm cavity; 132. Threaded mounting hole; 14. Bolted connection structure; 140. First mounting post; 15. First limiting body; 2. Pressure bearing; 3. Worm gear body; 31. Pressure bearing housing; 32. Gear section; 321. Second limiting body; 33. Output shaft; 331. Flange fixing hole; 35. Rotation limiting part; 4. Worm; 41. Sealing position; 42. 5. Bearing seat; 6. End cover; 7. Second oil seal groove; 8. Second sealing ring groove; 9. Sliding bearing mounting part; 10. Pressure cover; 11. First oil seal groove; 12. First sealing ring groove; 13. Second sealing part; 14. Second oil seal; 15. Second sealing ring; 16. Mounting hole; 17. Rolling bearing; 18. First sealing part; 19. First oil seal; 20. First sealing ring; 10. Sliding bearing; 11. Locking bolt. Detailed Implementation

[0041] like Figure 1-13As shown: A pressure-bearing deceleration device for a flexible tracking bracket includes a housing 1, a worm gear body 3, a worm 4, and an end cap 5. The housing 1 is provided with a worm gear cavity 12 and a worm shaft cavity 13. The worm gear cavity 12 is provided with a bearing seat 121. The worm gear body 3 is provided with a pressure bearing chamber 31, a gear segment 32, and an output shaft 33. The pressure bearing chamber 31 of the worm gear body 3 is inlaid with a pressure bearing 2, which is also sleeved on the bearing seat 121. The worm 4 is rotatably installed in the worm shaft cavity 13 and meshes with the gear segment 32. The end cap 5 is sleeved on the output shaft 33 and fixedly installed on the housing 1.

[0042] like Figure 5-7 As shown, the bearing housing 121 is a cylindrical structure protruding from the worm gear cavity 12.

[0043] A bolted structure 14 is provided on the outer end face of the housing 1.

[0044] The bolted structure 14 includes a plurality of first mounting posts 140 vertically arranged on the outer end face of the housing 1.

[0045] In this embodiment, the number of the first mounting posts 140 is set to six, with three first mounting posts 140 forming a group, located on the upper and lower sides of the housing 1 near the edge.

[0046] The first mounting post 140 has a first threaded hole. With this design, the housing 1 can be fixedly connected to the external support through the first threaded holes of multiple first mounting posts 140, ensuring stability during use.

[0047] The structural design of the support base is well known in the application of speed reducers, and is not shown in the figure, so it will not be described in detail here.

[0048] The worm gear cavity 12 is configured as a concave circular structure.

[0049] The gear segment 32 is fan-shaped and arranged at a specific angle, and a second limiting body 321 is provided at both ends of the gear segment 32.

[0050] A first limiting body 15 is provided inside the worm gear cavity 12 above the output shaft 33.

[0051] The first limiting body 15 is arc-shaped. When the worm gear body 3 rotates in the worm gear cavity 12, the rotation angle of the worm gear body 3 can be limited by the two ends of the first limiting body 15 contacting the second limiting body 321 respectively.

[0052] The worm chamber 13 is connected to the worm wheel chamber 12.

[0053] A flange is fixedly installed on the housing 1 near the opening of the worm gear cavity 13.

[0054] The worm cavity 13 of the housing 1 is connected to an external drive device through a first threaded hole. The power output end of the external drive device is connected to the worm 4 and can drive the worm 4 to rotate.

[0055] In this embodiment, the external drive device is usually driven by a motor. The specific structure is known in the prior art and can be obtained commercially, so it will not be described in detail here.

[0056] A threaded mounting hole 132 is provided on the inner wall of the worm gear cavity 13 near the opening.

[0057] The intermediate hole of the pressure bearing 2 is fixedly sleeved on the bearing housing 121. The pressure bearing 2 is a tapered roller bearing, which is a conventional standard part and can be obtained commercially.

[0058] In addition to this embodiment, the pressure bearing 2 can also be a self-aligning roller bearing, an angular contact bearing, or a thrust bearing, and the pressure bearing 2 is a bearing capable of withstanding axial pressure.

[0059] like Figure 8-9 As shown, the pressure bearing housing 31 is located at the position corresponding to the pressure bearing 2 on the worm gear body 3.

[0060] The inner surface of the pressure bearing housing 31 is fixedly mounted on the outer rotating surface of the pressure bearing 2.

[0061] With this design, the worm gear body 3 can rotate within the worm gear cavity 12 via the pressure bearing 2.

[0062] A rotation limiting part 35 is provided at a position other than the gear segment 32 on the outer surface of the worm gear body 3. The width of the rotation limiting part 35 matches the width of the first limiting body 15, and the length of the rotation limiting part 35 is longer than the length of the first limiting body 15.

[0063] This design allows the length of the first limiting body 15 to be set according to the rotation angle requirements of the flexible tracking bracket. Therefore, the worm gear 3 does not rotate a full circle within the worm gear cavity 12. When the second limiting body 321 at one end of the gear segment 32 contacts one end of the first limiting body 15, it rotates in the opposite direction, enabling the worm gear 3 to rotate left and right. This facilitates the adjustment of the rotation angle of the flexible tracking bracket and achieves better tracking.

[0064] In this embodiment, the worm gear body 3 rotates at an angle of 60° to both the left and right.

[0065] By using a pressure bearing 2 as the core load-bearing component to bear the main load generated when the support is rotating, its tapered raceway and tapered roller structure design can decompose the axial load from the rotating beam of the tracking support into radial and axial components along the roller cone surface. The axial component is transmitted to the housing 1 through the outer ring of the pressure bearing 2, while the radial component is borne by the mating structure of the inner ring of the pressure bearing 2 and the worm gear body 3, thus achieving efficient dispersion and transmission of axial load and avoiding load concentration at a single contact point.

[0066] In this embodiment, the output shaft 33 is configured as a circular sleeve, and a plurality of second mounting posts are vertically arranged inside the circular sleeve near the edge, and flange fixing holes 331 are provided on the second mounting posts.

[0067] In this embodiment, the number of the second mounting posts is also set to six, with three second mounting posts forming a group, symmetrically arranged inside the circular sleeve.

[0068] With this design, the rotating beam of the tracking bracket is fixedly connected to the flange fixing hole 331 of the output shaft 33 by bolts. When the output shaft 33 rotates, it drives the rotating beam to rotate, thus completing the power output.

[0069] A sliding bearing 8 is slidably mounted on the outer surface of the output shaft 33. The sliding bearing 8 is made of wear-resistant powder metallurgy.

[0070] In addition to this embodiment, the sliding bearing 8 may also be made of copper-based alloy, Babbitt alloy, or high-molecular wear-resistant material.

[0071] like Figure 10-11 As shown, a sliding bearing mounting part 53 is provided on the inner wall of the end cover 5 at a position corresponding to the sliding bearing 8, and the outer surface of the sliding bearing 8 is embedded in the inner wall of the sliding bearing mounting part 53.

[0072] A second oil seal groove 51 is provided on the inner wall of the end cover 5 near the sliding bearing mounting part 53.

[0073] A second sealing ring groove 52 is provided on the outer surface of the end cap 5.

[0074] The end cap 5 is fixedly connected to the housing 1 by bolts. In this embodiment, multiple third threaded holes are opened at the edge of the housing 1, and through holes are opened at the corresponding positions of the third threaded holes at the edge of the end cap 5. The locking bolt 9 is then threaded through the through holes and connected to the corresponding third threaded holes to complete the fixed connection between the end cap 5 and the housing 1.

[0075] The end cap 5 is also provided with a first sealing part 7, which serves a sealing function.

[0076] like Figure 4As shown, the first sealing part 7 includes a first sealing ring 72 placed in the second sealing ring groove 52, and the first sealing ring 72 simultaneously abuts against the inner wall of the worm gear cavity 12 near the edge.

[0077] The second oil seal groove 51 contains a first oil seal 71, which is in contact with the outer surface of the output shaft 33 near the edge.

[0078] Both the first sealing ring 72 and the first oil seal 71 are standard parts and can be obtained commercially. Furthermore, the sealing principle of the first sealing ring 72 and the first oil seal 71 is well known in the prior art and will not be described in detail here.

[0079] like Figure 2 , Figure 12-13 As shown, the worm 4 has a meshing part in the middle, which meshes with the gear segment 32 of the worm wheel body 3. The specific meshing method and structure are known in the prior art.

[0080] Both ends of the meshing part are provided with bearing seats 42, and rolling bearings 65 are sleeved on the bearing seats 42.

[0081] Two rolling bearings 65 are simultaneously fixedly installed in the worm cavity 13. With this design, the worm 4 rotates in the worm cavity 13 through the rolling bearings 65.

[0082] A sealing position 41 is fixedly connected to one end of the bearing position 42 near the flange.

[0083] A pressure cap 6 is threaded onto the threaded mounting hole 132, and the pressure cap 6 is also fitted onto the worm gear 4.

[0084] The pressure cap 6 is provided with a screw that matches the threaded mounting hole 132 at the corresponding position, so that the pressure cap 6 can be threaded into the worm cavity 13 of the housing 1.

[0085] The outer surface of the pressure cover 6 is also provided with mounting holes 64 to facilitate the installation of the pressure cover 6.

[0086] The outer surface of the pressure cap 6 is provided with a first sealing ring groove 62 near the screw.

[0087] A first oil seal groove 61 is provided on the inner wall of the pressure cap 6 near the screw position.

[0088] The pressure cap 6 is also provided with a second sealing part 63 that also serves a sealing function.

[0089] The second sealing part 63 includes a second sealing ring 631 placed in the first sealing ring groove 62. The second sealing ring 631 is in contact with the inner wall of the worm gear cavity 13 of the housing 1 to achieve a seal.

[0090] A second oil seal 630 is placed in the first oil seal groove 61. The second oil seal 630 is in contact with the sealing position 41 of the worm gear 4 to achieve a seal.

[0091] The second sealing ring 631 and the second oil seal 630 are both standard parts and can be obtained commercially. The sealing principle will not be described in detail here.

[0092] In use, the worm gear body 3 is supported by the sliding bearing 8 and the end cover 5, which can bear part of the radial load, further disperse the radial force borne by the tapered roller bearing, reduce the load on the main load-bearing components, realize the reasonable distribution of the overall load, reduce the wear rate of individual components, and extend the overall service life.

[0093] Although embodiments of the present invention have been shown and described, it will be understood by those skilled in the art that various changes, modifications, substitutions and alterations can be made to these embodiments without departing from the principles and spirit of the present invention, the scope of which is defined by the appended claims and their equivalents.

Claims

1. A pressure-bearing deceleration device for a flexible tracking bracket, comprising a housing (1), a worm gear body (3), a worm (4), and an end cap (5), wherein the housing (1) is provided with a worm gear cavity (12) and a worm shaft cavity (13), a bearing seat (121) is provided in the worm gear cavity (12), and a pressure-bearing bearing chamber (31), a gear segment (32), and an output shaft (33) are provided on the worm gear body (3), characterized in that: The pressure bearing (2) is embedded in the pressure bearing chamber (31) of the worm gear body (3). The pressure bearing (2) is also sleeved on the bearing seat (121). The worm (4) is rotatably installed in the worm cavity (13) and meshes with the gear section (32). The end cover (5) is sleeved on the output shaft (33) and fixedly installed on the housing (1).

2. The pressure-bearing deceleration device for a flexible tracking bracket according to claim 1, characterized in that: The bearing seat (121) on the housing (1) is a protruding cylindrical structure. The inner wall of the housing (1) is provided with a first limiting body (15). The outer end face of the housing (1) is provided with a bolting structure (14). The worm cavity (13) is provided with a threaded mounting hole (132) near the opening.

3. The pressure-bearing deceleration device for a flexible tracking bracket according to claim 1, characterized in that: The worm gear cavity (12) is designed as a concave circular structure, the gear segment (32) is fan-shaped and arranged at a specific angle, and a second limiting body (321) is provided at both ends of the gear segment (32). Multiple flange fixing holes (331) are provided at the position of the output shaft (33) away from the worm gear cavity (12).

4. The pressure-bearing deceleration device for a flexible tracking bracket according to claim 1, characterized in that: The worm (4) is configured with a meshing part in the middle, which meshes with the worm wheel body (3). Both ends of the meshing part are provided with bearing seats (42), and rolling bearings (65) are fitted on the bearing seats (42). The two rolling bearings (65) are fixedly installed in the worm cavity (13). The pressure cap (6) is fitted on the worm (4) and threaded into the threaded mounting hole (132).

5. The pressure-bearing deceleration device for a flexible tracking bracket according to claim 1, characterized in that: The inner wall of the end cap (5) is provided with a sliding bearing mounting part (53), and the outer surface of the sliding bearing (8) is embedded in the inner wall of the sliding bearing mounting part (53) and slides in cooperation with the output shaft (33); The sliding bearing (8) is made of wear-resistant material.

6. The pressure-bearing deceleration device for a flexible tracking bracket according to claim 5, characterized in that: A second oil seal groove (51) is provided on the inner wall of the end cover (5) near the sliding bearing mounting part (53), and a second sealing ring groove (52) is provided on the outer surface of the end cover (5). The end cap (5) is simultaneously equipped with a first sealing part (7) that serves a sealing function.

7. A pressure-bearing deceleration device for a flexible tracking bracket according to claim 6, characterized in that: The first sealing part (7) includes a first sealing ring (72) placed in the second sealing ring groove (52), and the first sealing ring (72) simultaneously abuts against the inner wall of the worm gear cavity (12) near the edge; The first oil seal (71) is placed in the second oil seal groove (51), and the first oil seal (71) is in contact with the outer surface of the output shaft (33) near the edge.

8. The pressure-bearing deceleration device for a flexible tracking bracket according to claim 4, characterized in that: The pressure cap (6) is also provided with a second sealing part (63) that also serves a sealing function, and the outer surface of the pressure cap (6) is also provided with a plurality of mounting holes (64).

9. A pressure-bearing deceleration device for a flexible tracking bracket according to claim 1, characterized in that: The pressure bearing (2) is selected as a tapered roller bearing that can withstand axial pressure.

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