Design method of inlaid self-lubricating bearing for miter gate

Abstract

The application provides a design method of an inlaid self-lubricating bearing for a miter gate. The inlaid self-lubricating bearing is designed according to the stress condition of the bearing, a solid lubricant is selected, the coverage percentage of the solid lubricant is calculated, the coverage percentage of the filling holes is distributed, the positions of the filling holes are determined and the filling holes are punched, and finally the solid lubricant rod is filled into the filling holes to obtain the inlaid self-lubricating bearing.

Description

Technical Field

[0001] This invention belongs to the field of self-lubricating bearing technology, specifically relating to the design method of inlaid self-lubricating bearings for herringbone gates. Background Technology

[0002] With the development of inland shipping in China, miter locks, as a reliable type of lock, are widely used in navigation. In recent years, the traffic volume of locks has been increasing, and the number of times miter locks are opened has also been increasing, often exceeding the design capacity of the locks. The bottom and top pivots of the gate pillars used to connect the gates operate under heavy load conditions for a long time, making it difficult for fluid lubrication to form an oil film, resulting in poor lubrication. Regular maintenance can easily lead to huge economic losses due to downtime.

[0003] This places higher demands on the performance of its top and bottom pivots. The miter gate operates under low-speed, heavy-load conditions for extended periods, leading to high contact pressure in the bottom pivot friction pair. Combined with its constant underwater location and heavy sediment contamination, once the oil film between the mushroom head and the bearing shell (ball bearing) is damaged, the bottom pivot mushroom head and bearing shell seize up, accelerating wear and causing the gate to tilt at a certain angle due to wear on the bottom pivot mushroom head, resulting in a series of problems such as the gate failing to close tightly.

[0004] The gate top pivot is generally exposed to the outside, and the working environment is harsh. Ordinary oil lubrication is costly and troublesome to maintain. Therefore, solid lubrication is generally used for the top pivot of miter gates. Solid lubricant is embedded in the inner wall of the circular metal bearing to achieve the lubrication effect.

[0005] The lubrication performance of the ball bearings at the bottom is critical. Commonly used friction pairs in the bottom pivot of miter gates typically employ ball bearings with a hard-soft combination: the mushroom head is made of harder carbon steel, while the mushroom head cap is made of softer copper alloy. The bottom pivot of the gate operates under low-speed, heavy-load conditions for extended periods, making ordinary oil lubrication ineffective and hindering the formation of a continuous, effective lubricating film. Under heavy loads, this leads to severe wear and can easily cause the bearings to seize, affecting gate operation. Furthermore, lubricating oil leakage can easily pollute the environment. Solid lubricants offer advantages such as good low-speed anti-creep performance and high load-bearing capacity, effectively compensating for the limitations of oil lubrication in low-speed, heavy-load environments.

[0006] Currently, there are two main methods for combining solid lubricants with copper alloys: powder metallurgy and inlay. Powder metallurgy involves mixing solid lubricant powder with metal powder, forming a shape, and then sintering it. However, this method often results in poor bonding between the lubricant and metal powders, and the lubricant powder is not evenly distributed within the metal, leading to differences in strength properties across different parts. Inlay, on the other hand, involves embedding filling holes in a metal substrate and then filling them with solid lubricant. This method allows for the regular creation of filling holes, with the graphite filling holes designed according to the specific properties of the lubricant. This invention utilizes the inlay method for the design of bottom pivot bearings. Summary of the Invention

[0007] The purpose of this invention is to provide a design method for inlaid self-lubricating bearings for herringbone gates. The method involves designing the bearing based on its stress conditions, selecting a solid lubricant and calculating its coverage percentage, then designing the distribution of the coverage percentage of the filling holes, determining the position of each filling hole and drilling holes, and finally filling the solid lubricant rod into it to obtain a copper-based inlaid self-lubricating composite.

[0008] To achieve the above-mentioned technical features, the present invention provides a design method for a herringbone gate using an embedded self-lubricating bearing, characterized by comprising the following steps:

[0009] Step 1: By confirming the working conditions, operating conditions and external environmental factors, determine the basic dimensions of the bottom pivot ball bearing, design the basic parts of the bottom pivot ball bearing in advance, and perform preliminary modeling;

[0010] Step 2: Perform a mechanical analysis based on the weight and dimensions of the gate, and calculate the maximum contact stress;

[0011] Step 3: Analyze the performance of the solid lubricant and manufacture it into a solid lubricating rod. Design it based on the maximum contact stress calculated in Step 2, determine its coverage percentage, and design the drilling based on this.

[0012] Step 4: Design the drilling of the bottom pivot spherical bearing, starting from the outermost ring. Each filling hole has two directional angles: one is the angle of the ring line, and the other is the circumferential angle of the ring line.

[0013] An initial loop angle is set according to the specific dimensions, and the design is carried out with the front view section line as the initial point of the loop circumference angle.

[0014] Step 5: Calculate the ring diameter based on the initial ring angle, then select a suitable filling hole diameter, and then determine the number of holes on the ring based on the coverage area percentage. In order to ensure the overall coverage area percentage, determine the coverage area percentage of the inlaid holes on the ring band where each ring is located.

[0015] Step Six: The angle of the next loop is determined based on the angle of the previous loop and the diameter of the filling hole;

[0016] Step 7: Conduct inspection and adjustment, calculate whether the overall filling hole area coverage percentage is within the qualified range, and make some hole position adjustments to finally obtain the bottom pivot bearing.

[0017] The basic components of the bottom pivot ball bearing in step one include the bottom pivot bearing shell, and the preliminary design of the bottom pivot bearing shell includes the design of the sealing structure and basic dimensions.

[0018] The specific process of mechanical analysis in step two is as follows:

[0019] When the gate opens and closes at a constant speed in still water, the gate body is subjected to the coupling effect of multiple forces, including: hydrodynamic pressure P. h Wind pressure P v Gravity G, opening and closing force F t Top pivot support reaction force F1 and bottom pivot support reaction force F2;

[0020] The top pivot support reaction force is:

[0021]

[0022] The bottom pivot support reaction force is:

[0023]

[0024] The angle between the resultant force at the bottom pivot and the xoy plane is:

[0025]

[0026] Total dynamic water pressure P h for:

[0027]

[0028] In the formula: m is the horizontal distance from the gate's center of gravity to the axis of rotation; n is the horizontal distance from the point of application of the opening and closing force to the top pivot; γ is the angle between the opening and closing force and the gate; j and k are respectively the angles between P and the gate. h P v The vertical distance from the point of application to the lower end of the gate; B is the gate width; h1 is the submerged water depth of the obstructed surface; F 1x F is the horizontal supporting force along the direction of the door body that is applied to the top pivot; 1y F is the horizontal and vertical support force on the top pivot in the direction of the door body; 2x F is the horizontal supporting force along the direction of the door body on the bottom pivot; 2y F is the horizontal and vertical support force on the top pivot in the direction of the door body; 2z For the vertical support force of the bottom pivot; ρ 水 ρ is the density constant of water; Δh is the backwater height; g is the gravitational acceleration constant.

[0029] The wind pressure on the gate is:

[0030] P v =u t u h p b cosαh2B (5)

[0031] In the formula: P b Base wind pressure value; u tThe wind pressure shape coefficient; u h h2 is the wind pressure height coefficient; h2 is the height of the gate body above the water surface; α is the gate opening degree.

[0032]

[0033] In the formula: H is the gate height; M x M represents the sum of the torques acting horizontally along the door body, with the bottom pivot as the reference point; y M represents the sum of the torques acting on the door in the direction perpendicular to the bottom pivot; z The sum of the torques acting on the base pivot in the vertical direction;

[0034] Bottom-pivot contact is a type of spherical common contact, and the formula for the contact stress at any point on it is:

[0035]

[0036] In the formula: θ is the angle between the directed line segment and the positive direction of the Z-axis; φ is the angle through which the point projection rotates on the xoy plane; R is the radius of the base pivot.

[0037] The contact stress calculated in step two is taken as the maximum value for analysis, and a sufficient safety factor is given.

[0038] In step three, the diameter of the solid lubricating rod is fitted with the aperture of the hole, and it is fixedly connected to the bottom pivot bearing by an adhesive. The length of the solid lubricating rod is equal to the depth of the hole.

[0039] In step five, the annular area is determined using formula (8):

[0040]

[0041] In the formula: D is the diameter of the bottom pivot bearing; d is the diameter of the inlaid hole on the ring line; α is the angle between the ring line and the horizontal plane;

[0042] The number of holes embedded in the ring can be determined:

[0043]

[0044] The calculation result is rounded to obtain the number of holes embedded on the ring, and the holes are evenly distributed on the ring.

[0045] The number of inlay holes calculated on the ring line in step five is a reference value, and adjustments are made accordingly to ensure that the number of inlay holes on adjacent ring lines is the same as much as possible.

[0046] The specific method for determining the angle of the next loop in step six, based on the angle of the previous loop and the diameter of the filling hole, is as follows:

[0047] Let the overlap be m, and the diameter of the filling hole of the previous loop be d.n The angle of the loop is α n The current ring-shaped filling aperture is d. n+1 If the inner diameter of the bottom pivot bearing is D, then the current loop angle is:

[0048]

[0049] Based on this, the design of the hole angle position on the ring line is carried out, and the layers are stacked until the bearing inlay hole is filled.

[0050] The inspection and adjustment in step seven includes interference adjustment between the hole position and the oil groove, and interference adjustment between holes. For adjacent rings with different numbers of embedded holes, the ring angle can be increased.

[0051] The present invention has the following beneficial effects:

[0052] 1. By adopting the present invention, the bottom pivot bearing can be designed according to the type of solid lubricant to achieve the best performance of the lubricant.

[0053] 2. The inlay holes on the adjacent rings of the bottom pivot bearing overlap to ensure that solid lubricant is distributed in all parts of the bottom pivot bearing during rotation.

[0054] 3. The percentage of the area covered by the inlaid holes on each ring is consistent with the overall area and is relatively uniform. Attached Figure Description

[0055] The present invention will be further described below with reference to the accompanying drawings and embodiments.

[0056] Figure 1 This is a schematic diagram of the overlapping part of the inlaid holes on the ring line of the bearing bush.

[0057] Figure 2 This is a force diagram of the door body.

[0058] Figure 3 A simplified diagram for calculating the maximum contact stress of the mushroom head at the bottom pivot of the gate.

[0059] Figure 4 Force diagram of the bottom pivot.

[0060] Figure 5 Diagram showing the contact and force analysis of the bottom pivot spherical surface.

[0061] Figure 6 Diagram of the loop angle.

[0062] Figure 7 A schematic diagram of the circumferential angles on the ring.

[0063] Figure 8 Top pivot diagram.

[0064] Figure 9 Engineering drawing of bottom pivot bearing.

[0065] Figure 10 Design flowchart. Detailed Implementation

[0066] The embodiments of the present invention will be further described below with reference to the accompanying drawings.

[0067] Example 1:

[0068] See Figure 1-10 This embodiment addresses the design method of a copper-based inlaid self-lubricating bearing. The design is based on the bearing's stress conditions. A solid lubricant is selected, and its coverage percentage is calculated. The coverage percentage of the filling holes is then distributed and designed. The positions of each filling hole are determined and drilled. Finally, solid lubricant rods are filled in to obtain a copper-based inlaid self-lubricating composite.

[0069] To solve the above-mentioned technical problems, the following technical measures are adopted to achieve the purpose of the invention:

[0070] (1) The percentage of the filling hole coverage area is determined based on the type of solid lubricant and the maximum contact stress on the bearing, with the aim of achieving the best lubrication effect of the solid lubricant while ensuring safety.

[0071] (2) The percentage of the total area of ​​the filling hole should be close to the optimal lubrication coverage area of ​​the solid lubricant.

[0072] (3) The size of the filling holes is not the same. The hole diameter is determined according to the diameter of the bearing ring.

[0073] (4) The filling holes on adjacent rings have a certain degree of overlap (e.g., Figure 1 This ensures that the bottom pivot is covered with lubricant at all positions during operation.

[0074] (5) The solid lubricant rod is formed by molding, and the formed solid lubricant block is finally fixed in the filling hole by adhesive.

[0075] Taking a low-speed, heavy-duty copper-based PTFE-embedded self-lubricating bottom pivot as an example, and taking a large gate as the research object, the main technical parameters of the gate are shown in Table 1.

[0076] Table 1 Main Technical Parameters of a Large Gate

[0077]

[0078] The specific design method is as follows:

[0079] The copper alloy of the PTFE solid lubricant is composed of Cu, Sn, Al2O3, and Zn, all with a purity greater than 99.5%. Sn accounts for 1% of the mass fraction of the copper alloy, Al2O3 accounts for 0.3% of the mass fraction of the copper alloy, Zn accounts for 1% of the mass fraction of the copper alloy, and the remainder is Cu.

[0080] The initial design of the bottom pivot bearing is carried out, including its dimensions and sealing structure.

[0081] Step 1: By confirming the working conditions, operating conditions and external environmental factors, determine the basic dimensions of the bottom pivot ball bearing, preliminarily design the basic parts of the bottom pivot ball bearing, and perform preliminary modeling; the basic parts of the bottom pivot ball bearing include the bottom pivot bearing shell, and the preliminary design of the bottom pivot bearing shell includes the design of the sealing structure and basic dimensions.

[0082] Step 2: Perform a mechanical analysis based on the weight and dimensions of the gate, and calculate the maximum contact stress;

[0083] The weight of a single leaf of the miter gate is 2.8 × 10. 5 (kg), given wind pressure Pv=5.725cosα(kN), hydrodynamic pressure P h = 2.21 (kN); the gate height parameters are H = 12.5 (m), m = B / 2 = 3.35 (m), j = h1 / 2 = 2.9 (m), k = h1 + h2 / 2 = 9.15 (m) and n = 1.53 (m). Substituting the above known quantities, solving the system of equations yields the resultant force at the bottom pivot:

[0084]

[0085]

[0086] The maximum resultant force at the bottom pivot is F2 = 2841 kN when the gate opening is 0, corresponding to a resultant force angle β = 75°. When the gate opening is 67.5°, F2 = 2840.7 kN and β = 74.9°. The variation in the magnitude and angle of the resultant force is very small and can be considered a constant. Taking the average of the maximum and minimum values, the resultant force at the bottom pivot is: F2 = 2841 kN, β = 75°.

[0087] Substituting the calculated resultant force and resultant angle of the actual gate bottom pivot into (7) for calculation, we can obtain the contact stress σ = 23.4cosθ (MPa). When θ = 0°, that is, in the direction of the normal of the resultant angle, σ max =23.4MPa, therefore the maximum contact stress of the gate bottom pivot is also 23.4MPa.

[0088] Step 3: Analyze the performance of the solid lubricant and manufacture it into a solid lubricating rod. Design it based on the maximum contact stress calculated in Step 2, determine its coverage percentage, and design the drilling based on this.

[0089] Step 4: Design the drilling of the bottom pivot spherical bearing, starting from the outermost ring. Each filling hole has two directional angles: one is the angle of the ring line, and the other is the circumferential angle of the ring line.

[0090] An initial loop angle is set according to the specific dimensions, and the design is carried out with the front view section line as the initial point of the loop circumference angle.

[0091] Step 5: Calculate the ring diameter based on the initial ring angle, then select a suitable filling hole diameter, and then determine the number of holes on the ring based on the coverage area percentage. In order to ensure the overall coverage area percentage, determine the coverage area percentage of the inlaid holes on the ring band where each ring is located.

[0092] In step five, the annular area is determined using formula (8):

[0093]

[0094] In the formula: D is the diameter of the bottom pivot bearing; d is the diameter of the inlaid hole on the ring line; α is the angle between the ring line and the horizontal plane;

[0095] The number of holes embedded in the ring can be determined:

[0096]

[0097] The calculation result is rounded to obtain the number of holes embedded on the ring, and the holes are evenly distributed on the ring.

[0098] The number of inlay holes calculated on the ring line in step five is a reference value, and adjustments are made accordingly to ensure that the number of inlay holes on adjacent ring lines is the same as much as possible.

[0099] Table 2 Recommended Hole Diameters for Mounting Holes

[0100]

[0101] Step Six: The angle of the next loop is determined based on the angle of the previous loop and the diameter of the filling hole; the specific method for determining the angle of the next loop based on the angle of the previous loop and the diameter of the filling hole is as follows:

[0102] Let the overlap be m, and the diameter of the filling hole of the previous loop be d. n The angle of the loop is α n The current ring-shaped filling aperture is d. n+1 If the inner diameter of the bottom pivot bearing is D, then the current loop angle is:

[0103]

[0104] Table 3. Inlay Hole Design Table

[0105] loop Protrusion diameter Material initial angle radian Angle of deflection from the horizontal plane Vertical deflection angle radian value Axis radius Hole diameter and circumference Hole diameter Hole area Circular area Coverage ratio Calculate the number actual number Remark 1 400 PTFE 6 0.10472 6 84 1.466077 198.90 1249.7531 25 490.873852 31183 0.3 19 18 2 400 PTFE 0.223331 12.8 77.2 1.347466 195.03304 1225.4288 25 490.873852 30576.1 0.3 18 18 3 400 PTFE 0.341941 19.6 70.4 1.228855 188.4211 1183.8847 25 490.873852 29539.5 0.3 18 18 4 400 PTFE 0.460552 26.4 63.6 1.110244 179.16146 1125.7047 25 490.873852 28087.8 0.3 17 18 5 400 PTFE 0.567322 32.5 57.5 1.003475 168.66865 1059.7764 20 314.159265 21169.1 0.3 20 18 6 400 PTFE 0.66225 37.9 52.1 0.908546 157.7221 990.99719 20 314.159265 19795.2 0.3 18 18 7 400 PTFE 0.757179 43.4 46.6 0.813617 145.35532 913.29438 20 314.159265 18243.1 0.3 17 18 8 400 PTFE 0.847367 48.6 41.4 0.723429 132.39175 831.8419 18 254.469005 14958 0.3 17 18 9 400 PTFE 0.942478 54.0 36.0 0.628319 117.55705 738.63273 18 254.469005 13281.9 0.3 15 14 36 10 400 PTFE 1.027926 58.9 31.1 0.542871 103.31919 649.17365 18 254.469005 11673.3 0.3 13 14 11 400 PTFE 1.10626 63.4 26.6 0.464537 89.601717 562.98419 15 176.714587 8438.83 0.3 14 14 12 400 PTFE 1.17748 67.5 22.5 0.393317 76.650802 481.6112 15 176.714587 7219.09 0.3 12 14 13 400 PTFE 1.256637 72.0 18.0 0.314159 61.803399 388.32221 14 153.93804 5433.18 0.3 10 12 18 14 400 PTFE 1.323113 75.8 14.2 0.247684 49.031812 308.07596 14 153.93804 4310.42 0.3 8 12 15 400 PTFE 1.387537 79.5 10.5 0.18326 36.447105 229.00392 10 78.5398163 2289.32 0.3 8 8 10.5 16 400 PTFE 1.435028 82.2 7.8 0.135768 27.070356 170.08806 10 78.5398163 1700.35 0.3 6 8 17 400 PTFE 1.477771 84.7 5.3 0.093025 18.578228 116.73045 8 50.2654825 933.657 0.3 5 8 18 400 PTFE 1.518436 87.0 3.0 0.05236 10.467191 65.767302 6 28.2743339 394.559 0.3 4 6 3

[0106] Step 7: Conduct inspection and adjustment, calculate whether the overall filling hole area coverage percentage is within the qualified range, and make some hole position adjustments to finally obtain the bottom pivot bearing.

[0107] Table 4 Calculation of Distributed Load for Inlay Holes

[0108]

[0109] Analysis of Tables 3 and 4 reveals that the mounting hole diameters used in the bottom pivot bearing are 6, 8, 10, 14, 15, 18, 20, and 25 mm. The inner diameter of the bottom pivot bearing is 400 mm, from which the area of ​​the bearing hemisphere can be calculated. There are 72 mounting holes with a diameter of 25 mm, evenly distributed in each ring from the outermost ring (1-4). The mounting holes with a diameter of 20 mm are also evenly distributed in each ring from rings 5-7. There are 46 mounting holes with a diameter of 18 mm, distributed in ring 8 (18 holes) and rings 9-10 (14 holes each). Furthermore, the angle of ring 9 is adjusted to 36°; there are 28 inlay holes with a diameter of 15mm, 14 on each of rings 11 and 12; there are 24 inlay holes with a diameter of 14mm, distributed on rings 13 and 14, with the angle of ring 13 adjusted to 18°; there are 16 inlay holes with a diameter of 10mm, 8 on each of rings 15 and 16, with the angle of ring 15 adjusted to 10.5°; there are 8 inlay holes with a diameter of 8mm distributed on ring 17; and 6 inlay holes with a diameter of 6mm are evenly distributed on ring 18, with the ring angle adjusted to 3°. Finally, the total area percentage is calculated to be 29.64%, which meets the requirements.

Claims

1. A design method for using embedded self-lubricating bearings in a herringbone gate, characterized in that, It includes the following steps: Step 1: By confirming the working conditions, operating conditions and external environmental factors, determine the basic dimensions of the bottom pivot ball bearing, design the basic parts of the bottom pivot ball bearing in advance, and perform preliminary modeling; Step 2: Perform a mechanical analysis based on the weight and dimensions of the gate, and calculate the maximum contact stress; Step 3: Analyze the performance of the solid lubricant and manufacture it into a solid lubricating rod. Design it based on the maximum contact stress calculated in Step 2, determine its coverage percentage, and design the drilling based on this. Step 4: Design the drilling of the bottom pivot spherical bearing, starting from the outermost ring. Each filling hole has two directional angles: one is the angle of the ring line, and the other is the circumferential angle of the ring line. An initial loop angle is set according to the specific dimensions, and the design is carried out with the front view section line as the initial point of the loop circumference angle. Step 5: Calculate the ring diameter based on the initial ring angle, then select a suitable filling hole diameter, and then determine the number of holes on the ring based on the coverage area percentage. In order to ensure the overall coverage area percentage, determine the coverage area percentage of the inlaid holes on the ring band where each ring is located. Step Six: The angle of the next loop is determined based on the angle of the previous loop and the diameter of the filling hole; Step 7: Conduct inspection and adjustment, calculate whether the overall filling hole area coverage percentage is within the qualified range, and make some hole position adjustments to finally obtain the bottom pivot bearing.

2. The design method for the inlaid self-lubricating bearing of the herringbone gate according to claim 1, characterized in that: The basic components of the bottom pivot ball bearing in step one include the bottom pivot bearing shell, and the preliminary design of the bottom pivot bearing shell includes the design of the sealing structure and basic dimensions.

3. The design method for the inlaid self-lubricating bearing of the herringbone gate according to claim 1, characterized in that: The specific process of mechanical analysis in step two is as follows: When the gate opens and closes at a constant speed in still water, the gate body is subjected to the coupling effect of multiple forces, including: hydrodynamic pressure P. h Wind pressure P v Gravity G, opening and closing force F t Top pivot support reaction force F1 and bottom pivot support reaction force F2; The top pivot support reaction force is: The bottom pivot support reaction force is: The angle between the resultant force at the bottom pivot and the xoy plane is: Total dynamic water pressure P h for: In the formula: m is the horizontal distance from the gate's center of gravity to the axis of rotation; n is the horizontal distance from the point of application of the opening and closing force to the top pivot; γ is the angle between the opening and closing force and the gate; j and k are respectively the angles between P and the gate. h P v The vertical distance from the point of application to the lower end of the gate; B is the gate width; h1 is the submerged water depth of the obstructed surface; F 1x F is the horizontal supporting force along the direction of the door body that is applied to the top pivot; 1y F is the horizontal and vertical support force on the top pivot in the direction of the door body; 2x F is the horizontal supporting force along the direction of the door body on the bottom pivot; 2y F is the horizontal and vertical support force on the top pivot in the direction of the door body; 2z For the vertical support force of the bottom pivot; ρ 水 ρ is the density constant of water; Δh is the backwater height; g is the gravitational acceleration constant; The wind pressure on the gate is: P v =in t in h p b cosαh2B (5) In the formula: P b Base wind pressure value; u t The wind pressure shape coefficient; u h h2 is the wind pressure height coefficient; h2 is the height of the gate body above the water surface; α is the gate opening degree. In the formula: H is the gate height; M x M represents the sum of the torques acting horizontally along the door body, with the bottom pivot as the reference point; y M represents the sum of the torques acting on the door in the direction perpendicular to the bottom pivot; z The sum of the torques acting on the base pivot in the vertical direction; Bottom-pivot contact is a type of spherical common contact, and the formula for the contact stress at any point on it is: In the formula: θ is the angle between the directed line segment and the positive direction of the Z-axis; φ is the angle through which the point projection rotates on the xoy plane; R is the radius of the base pivot.

4. The design method for the inlaid self-lubricating bearing of the herringbone gate according to claim 3, characterized in that: The contact stress calculated in step two is taken as the maximum value for analysis, and a sufficient safety factor is given.

5. The design method for the inlaid self-lubricating bearing of the herringbone gate according to claim 3, characterized in that: In step three, the diameter of the solid lubricating rod is fitted with the aperture of the hole, and it is fixedly connected to the bottom pivot bearing by an adhesive. The length of the solid lubricating rod is equal to the depth of the hole.

6. The design method for the inlaid self-lubricating bearing of the herringbone gate according to claim 1, characterized in that: In step five, the annular area is determined using formula (8): In the formula: D is the diameter of the bottom pivot bearing; d is the diameter of the inlaid hole on the ring line; α is the angle between the ring line and the horizontal plane; The number of holes embedded in the ring can be determined: The calculation result is rounded to obtain the number of holes embedded on the ring, and the holes are evenly distributed on the ring.

7. The design method for the inlaid self-lubricating bearing of the herringbone gate according to claim 6, characterized in that: The number of inlay holes calculated on the ring line in step five is a reference value, and adjustments are made accordingly to ensure that the number of inlay holes on adjacent ring lines is the same as much as possible.

8. The design method for the inlaid self-lubricating bearing of the herringbone gate according to claim 1, characterized in that: The specific method for determining the angle of the next loop in step six, based on the angle of the previous loop and the diameter of the filling hole, is as follows: Let the overlap be m, and the diameter of the filling hole of the previous loop be d. n The angle of the loop is α n The current ring-shaped filling aperture is d. n+1 If the inner diameter of the bottom pivot bearing is D, then the current loop angle is: Based on this, the design of the hole angle position on the ring line is carried out, and the layers are stacked until the bearing inlay hole is filled.

9. The design method for the inlaid self-lubricating bearing of the herringbone gate according to claim 1, characterized in that: The inspection and adjustment in step seven includes interference adjustment between the hole position and the oil groove, and interference adjustment between holes. For adjacent rings with different numbers of embedded holes, the ring angle can be increased.

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