Gear lubrication oil injection pipe and sector-like oil injection port optimization method based on orthogonal test

Abstract

The invention discloses a gear lubrication oil injection pipe and a fan-like nozzle optimization method based on an orthogonal test, the oil injection pipe comprises a fan-like nozzle, the cross section of the fan-like nozzle comprises a first fan-shaped edge and a second fan-shaped edge, an oil inlet is formed at one end between the two fan-shaped edges, and two or more oil injection ports are arranged at the other end between the two fan-shaped edges. The oil outlet end faces of the oil spraying openings are located on the same arc-shaped edge. The design of the fan-shaped nozzle structure enables the nozzle to be closer to the tooth surface of the gear, so that the lubricating effect is improved. The invention further discloses an optimization method of the fan-like nozzle, the orthogonal experiment method is adopted in the method, all structural parameters of the fan-like nozzle can be optimized, and the industrial production requirement is met.

Description

Technical Field

[0001] The present invention relates to the technical field of gear lubrication, and particularly to a gear lubrication spray oil pipe and an optimization method for fan-shaped oil injection nozzles based on orthogonal experiments. Background Art

[0002] High-speed gears generally refer to gears with a rotational speed of 3000 r / min and a linear velocity of more than 22 m / s. At present, high-speed gear drive systems are widely used in high-speed electric drive reducers and the aviation field. When the gears rotate at high speed, a large amount of heat will be generated due to friction in the gear meshing area. Therefore, it is necessary to lubricate the gears. When the gear lubrication conditions are poor, it will increase the risks of gear pitting corrosion, scuffing, etc., further affecting the operating life of the gears, and thus affecting the stability and safety of mechanical equipment. Therefore, it is necessary to design a reasonable lubrication method and structure to ensure the stability, safety and economy of high-speed gear operation.

[0003] Gear lubrication is divided into passive lubrication and active lubrication. The lubrication of gears by oil agitation is passive lubrication. Although passive lubrication has a simple structure and low cost, it will generate a large oil agitation torque and the lubrication effect on high-speed gears is not ideal. The oil injection for gears is active lubrication. Because the lubricating oil is always in a flowing state during high-speed rotation of the gears, the lubrication effect of oil injection lubrication is more advantageous than that of oil agitation lubrication.

[0004] The volume fraction of lubricating oil on the tooth surface is the most intuitive evaluation index for gear lubrication. Through simulation experiments, the inventor of this case analyzed the volume fraction of lubricating oil on the tooth surface and found that different oil injection speeds and distances affect the gear lubrication characteristics; moreover, a single nozzle will be compressed by the air domain generated by high-speed gears. Therefore, the inventor of this case concluded that the average volume fraction in the gear meshing area can be improved by increasing the number of nozzles to change the oil injection angle and oil volume; by changing the direction and length of the nozzle, the oil injection distance can be reduced, making the nozzle closer to the tooth surface to adapt to the gear size, and thus optimizing the oil injection lubrication.

[0005] After reaching the above conclusion, the inventor of this case searched the prior art, and the results are as follows:

[0006] The invention patent "A Method for Allocating Oil Supply Quantity of Multiple Injection Points in an Engine Transmission System" (CN201710084352.3) proposed by AECC Shenyang Engine Research Institute seems to have multiple injection points designed, but it is the design of the injection points for the overall engine transmission system, not the design of the spray oil pipe for a single gear pair.

[0007] The invention patent "An Intelligent Oil Injection Lubrication System for a High-Speed Gear Transmission Device and Its Control Method" (CN201910976376.9) proposed by Jilin University has nozzles that can be fan-shaped nozzles, but it is still a single nozzle and does not elaborate on the structure of the fan-shaped nozzle.

[0008] CN201320721133.9 is a utility model patent for "An improved oil spray lubrication device for a dryer" proposed by Wengfu (Group) Co., Ltd. The inner cavity of its nozzle is fan-shaped, but it is still a single-structure nozzle and the structure of the fan-shaped nozzle is not described in detail. Summary of the invention

[0009] The technical problem to be solved by the present invention is to provide a gear lubrication oil injection pipe which can change the oil injection angle and oil volume by increasing the nozzles and thus improve the average volume fraction of the gear meshing area.

[0010] Another technical problem to be solved by the present invention is to provide a fan-shaped fuel injection nozzle optimization method based on orthogonal experiments.

[0011] To solve the above technical problems, the technical solution of the present invention is:

[0012] A gear lubrication oil spray pipe includes a fan-shaped nozzle, the cross-section of which includes a first fan-shaped edge and a second fan-shaped edge, an oil inlet is formed at one end between the two fan-shaped edges, and two or more oil spray ports are provided at the other end, and the oil outlet end faces of the oil spray ports are on the same arc edge.

[0013] Preferably, it further comprises an oil inlet pipe, which is connected to one end of the oil inlet of the fan-shaped nozzle and is a straight pipe.

[0014] Preferably, the length of the first sector edge and the second sector edge, where the length of the side located on the small gear side is greater than the length of the side located on the large gear side.

[0015] Preferably, among the first sector-shaped edge and the second sector-shaped edge, the angle of the sector-shaped edge located on the small gear side relative to the axis of the oil inlet is greater than the angle of the sector-shaped edge located on the large gear side relative to the axis of the oil inlet.

[0016] Preferably, the central angle of the arcuate edge is α, and the included angle between the first sector edge and the second sector edge is β, wherein the angles of angle α and angle β are the same or different, and the vertices of angle α and angle β coincide or do not coincide.

[0017] Preferably, when the gear pair has a gear module m=2.5-4, a gear number range of z=15-40, and a gear ratio of 1:1-8:3, the side length l of the sector edge and the angle γ relative to the oil inlet axis are determined by the number of teeth z of the gear on the same side, and the following formula is obtained:

[0018] l≤-z+55 (1)

[0019] γ≤135+(40-z) (2).

[0020] Preferably, the distance from the end face of the oil inlet to the center of the gear set is d. When the central angle of the arc edge, i.e., the radian of the oil injection port α, is less than 135°, the following formula holds:

[0021] d ≥ 90 - 10×(4 - m) (3).

[0022] The optimization method of the quasi-sector oil injection structure includes the following steps:

[0023] S05. Design an orthogonal experiment scheme; select the quasi-sector nozzle structure parameters to be optimized as the orthogonal experiment factors, and determine the number of levels to design the orthogonal experiment scheme;

[0024] S10. Select evaluation indicators to obtain the orthogonal experiment results;

[0025] S15. Conduct a range analysis on the evaluation indicators to obtain the optimal model, thereby completing the structure optimization of the quasi-sector nozzle.

[0026] Preferably, in the second step, a four-factor and four-level orthogonal experiment scheme is established by selecting the side length l of the sector edge on the small gear side, the number of nozzles n, the radian of the oil injection port α, and the sector angle β as the four structure parameters.

[0027] Preferably, in the third step, the average volume fraction F of the lubricating oil or the relative optimization ratio K is used as the evaluation indicator, where the definition of the relative optimization ratio K is as follows:

[0028]

[0029] After adopting the above scheme, since the quasi-sector nozzle structure of the present invention is provided with a plurality of oil injection ports with end faces on the same arc, such a structural design can make the nozzle closer to the tooth surface of the gear, thereby improving the lubrication effect. In addition, the present invention can also change the oil injection angle and the amount of oil by adjusting the number of nozzles to improve the average volume fraction in the gear meshing area, and reduce the oil injection distance by changing the sector side length, so that the nozzle is closer to the tooth surface to adapt to the size of the gear.

[0030] In addition, the oil injection port optimization method of the present invention adopts the orthogonal experiment method, which can optimize the structural parameters of the quasi-sector nozzle to meet the requirements of industrial production. Description of the Drawings

[0031] Figure 1 is the structural schematic diagram of the fuel injection pipe of the present invention;

[0032] Figure 2 is the size parameter schematic diagram of the fuel injection pipe of the present invention;

[0033] Figure 3 is the three-dimensional structural schematic diagram of the fuel injection pipe of the present invention applied to the reducer drive system;

[0034] Figure 4 is a schematic structural view of the fuel injection pipe described in the present invention applied to a reducer drive system;

[0035] Figure 5 is Figure 4 a partially enlarged view;

[0036] Figure 6 is a schematic view of the manufacturing process of the oil outlet described in the present invention;

[0037] Figure 7 (a) is a curve graph showing the variation of the test index K with the factor level in the embodiment of the optimization method described in the present invention;

[0038] Figure 7 (b) is a curve graph showing the variation of the test index F with the factor level in the embodiment of the optimization method described in the present invention. Detailed implementation manners

[0039] The present invention will be further described in detail below in conjunction with the accompanying drawings and specific embodiments.

[0040] What the present invention discloses is a gear lubrication fuel injection pipe. As Figure 1 shown, it is a preferred embodiment of the fuel injection pipe. The fuel injection pipe 1 includes a quasi-sector-shaped nozzle 11 and an oil inlet pipe 12. Among them:

[0041] The cross-section of the quasi-sector-shaped nozzle 11 includes a first sector side 111 and a second sector side 112. An oil inlet 115 is formed at one end between the two sector sides, and two or more fuel injection nozzles 113 are provided at the other end. The oil outlet end faces of the fuel injection nozzles 113 are on the same arc edge 114. And the thickness of the quasi-sector-shaped nozzle 11 can be equivalent to the gear thickness of the reducer gear pair.

[0042] The setting of the quasi-sector-shaped nozzle 11 can make the oil outlet end faces of the fuel injection nozzles 113 closer to the gear pair, thereby increasing the lubrication effect. However, the quasi-sector-shaped nozzle 11 cannot interfere with the gear pair. Therefore, further restrictions need to be imposed on the parameters of the quasi-sector-shaped nozzle 11. For further explanation, the structural parameters of the quasi-sector-shaped nozzle 11 are defined as follows: Refer to Figure 2 shown, the length of the sector side (including the first sector side 111 and the second sector side 112) is l; the angle of the sector side (including the first sector side 111 and the second sector side 112) relative to the axis of the oil inlet 115 is γ; the central angle of the arc edge 114 is α (referred to as the fuel injection nozzle radian α in this article); the included angle between the first sector side 111 and the second sector side 112 is β (referred to as the sector angle β in this article); the distance from the end face of the oil inlet 115 to the center of the gear set (the center is not shown in the figure) is d.

[0043] Generally speaking, the arc degree α of the fuel injection port is the same as or different from the sector angle β; the centers of the central angle α and the included angle β may overlap or not. Similarly, the lengths l and the angles γ of the two sector sides can be the same or different. In order to make the fuel injection port closer to the gear set, obviously, the sector side on the side with fewer gear teeth is relatively longer and has a larger angle than the side with more gear teeth. As for the distance d, of course, it is better to be as small as possible on the premise of not interfering with the gears.

[0044] In order to make the fuel injection port as close as possible to the gear set without interfering with the gears, the structural parameters of the sector-like fuel injection port 11 are obviously related to the module and the number of teeth of the gear set. The simplest method is to determine by drawing, but obviously this does not conform to industrial production. For this reason, the present invention proposes the following formula to limit the above parameters:

[0045] Specifically, on the premise that the gears of the reducer gear set meet the following requirements: select gears with a module m = 2.5 - 4, the number of teeth range z = 15 - 40, and the gear transmission ratio between 1:1 - 8:3, the structural parameters of the sector-like fuel injection port 11 have the following formula:

[0046] The side length l of the sector can be determined according to the number of teeth z of the gears on the same side, and there is the following formula:

[0047] l ≤ -z + 55 (1)

[0048] The angle γ of the sector side relative to the axis of the oil inlet 115 is also determined by the number of teeth z of the gears on the same side, and there is the following formula:

[0049] γ ≤ 135 + (40 - z) (2)

[0050] In fact, after the angles of the two sector sides relative to the axis of the oil inlet 115 are determined, the included angle β between the two sector sides is determined.

[0051] The larger the angle of the arc degree α of the fuel injection port, the closer the fuel injection port is to the gear, but it is also easy to cause interference with the gear. Therefore, during actual installation, it can be adjusted by the distance d from the end face of the sector oil inlet 115 to the center of the gear set. Specifically, when the arc degree α of the fuel injection port is less than 135°, there is the following formula:

[0052] d ≥ 90 - 10×(4 - m) (3)

[0053] Obviously, as the module m decreases, d also decreases continuously.

[0054] The inlet oil pipe 12 is connected to one end of the oil inlet 115 of the fan-shaped nozzle 11. It is a straight pipe and can be a square pipe. Similar to the fan-shaped nozzle 11, the thickness of the inlet oil pipe 12 is equivalent to the gear thickness of the reducer gear pair. The width of the inlet oil pipe 12 is theoretically related to the initial velocity of the lubricating oil at the oil inlet, but the initial injection velocity can be adjusted by the oil pump pressure. Therefore, the width of the inlet oil pipe 12 can be unrestricted.

[0055] According to the structural parameter formula of the above-mentioned injection oil pipe 1, flexible manufacturing of the injection oil pipe can be carried out according to different gear transmission ratios. Specific examples are as Figures 3 - 5 shown. In this embodiment, the module m of the gear set is 2.5, and the tooth number ratio is 40:15. Labels in the figure: nozzle pipe 1, driving wheel 2, driven wheel 3, fuel tank 4. The structural parameters of the fan-shaped nozzle 11 are as follows: the side lengths of the two fan-shaped sides are 15 mm and 40 mm respectively, the angles of the two fan-shaped sides are 135° and 160° respectively, the distance d = 75 mm, and the injection port radian α is selected as 90°. As for the number of injection ports 113, it can be designed according to needs. Specifically, it can be seen in Figure 6 shown. First, divide the arc-shaped side 114 into several equal parts according to the number of injection ports 113. In the example in the figure, there are four injection ports 113, and the arc-shaped side is divided into 7 equal parts according to the arc angle, as in Figure 6 Figures (a) and (b); then connect the injection ports, as in Figure 6 Figure (c); then round the connection points, as in Figure 6 Figure (d) to complete the design of the injection port.

[0056] The essence of the present invention is to change the injection angle and the amount of oil by increasing the nozzle, so as to improve the average volume fraction in the gear meshing area, change the fan-shaped side length to reduce the injection distance, make the nozzle closer to the tooth surface, so as to adapt to the gear size, and form a fan-shaped multi-nozzle structure. How to optimize the important structural parameters of the fan-shaped multi-nozzle structure of the present invention is also the focus of the present invention. The above formulas for obtaining the size parameters of the fan-shaped nozzle 11 are designed from the perspective of preventing interference with the gear. They are obtained through drawing or experience and cannot obtain the optimal structure. The present invention further uses the orthogonal test method to optimize the fan-shaped injection structure. The optimization method steps are as follows:

[0057] S1. Setting the initial values of the structural parameters of the injection oil pipe. For structural parameters that are not important and do not need to be optimized, the initial values need to be set first.

[0058] The important structural parameters of the injection oil pipe include: the structural parameters of the fan-shaped nozzle 11 and the structural parameters of the inlet oil pipe 12.

[0059] The structural parameters of the fan-shaped nozzle 11 include the side length and angle of the first fan-shaped side, the side length and angle of the second fan-shaped side, the arc degree α of the fuel injection nozzle, the fan angle β, and the number n of fuel injection nozzles. The fan angle β is determined by the angles γ of the two fan-shaped sides.

[0060] In the present invention, the maximum value obtained by the foregoing formula (1) can be used as the initial side lengths of the two fan-shaped sides of the fan-shaped nozzle, or a selection can be made within the maximum value according to experimental requirements as the initial side lengths of the two fan-shaped sides. Similarly, the maximum value of formula (2) can be used as the initial angles of the two fan-shaped sides, or a selection can be made within the maximum value according to experimental requirements. The arc degree α of the fuel injection nozzle, the fan angle β, and the number n of fuel injection nozzles are the main optimization parameters, and generally there is no need to set the initial values.

[0061] Whether the fuel inlet pipe 12 is provided is related to the transmission system selected in the experiment, so as to ensure that the distance d between the fan-shaped nozzle 11 and the center of the gear set satisfies formula (3), or as long as the fan-shaped nozzle 11 does not interfere with the gear.

[0062] S05. Design an orthogonal experiment scheme. Select the structural parameters of the fan-shaped nozzle to be optimized as the orthogonal experiment factors, and determine the number of levels to design the orthogonal experiment scheme.

[0063] Theoretically, all the structural parameters of the above fan-shaped nozzle need to be optimized and can be used as the factors of the orthogonal experiment. However, considering the experimental complexity and the fact that the change of the longer fan-shaped side has a greater impact on the lubrication effect than the shorter fan-shaped side, the longer fan-shaped side is used as a variable for research, and it is the fan-shaped side with fewer teeth on the longer fan-shaped side. Therefore, the present invention can select four structural parameters, namely, the side length l of the fan-shaped side on the small gear side, the number n of nozzles, the arc degree α of the fuel injection nozzle, and the fan angle β, to establish a four-factor and four-level orthogonal experiment scheme.

[0064] S10. Select evaluation indicators to obtain the orthogonal experiment results.

[0065] The present invention can use the average volume fraction F of the lubricating oil or the relative optimization ratio K as the evaluation indicator. Among them, K is used to eliminate the influence of the nozzle area on the lubrication effect, and the definition of the relative optimization ratio is as follows:

[0066]

[0067] Where S f is the area of the fan-shaped nozzle; S o is the area of the original nozzle; V f is the average volume fraction in the gear meshing area under the fuel injection lubrication of the fan-shaped nozzle; V o is the average volume fraction in the gear meshing area under the fuel injection lubrication of the original nozzle. The original nozzle is a nozzle with a straight pipe structure in the prior art for optimization comparison.

[0068] S15. Perform a range analysis on the evaluation indexes to obtain the optimal model, thus completing the structural optimization of the fan-shaped nozzle. By performing a range analysis on the evaluation indexes, the influence degree of each factor on the lubrication effect can be obtained, and thus the optimal model can be obtained.

[0069] The following uses a specific embodiment to illustrate the above fan-shaped oil injection structure optimization method based on orthogonal experiments.

[0070] The parameters of the experimental reduction gearbox are as shown in Table 1 below:

[0071] Table 1 Parameters of gears and gearboxes

[0072]

[0073] For the above reduction gear transmission system, optimize the structural parameters of the fuel injection pipe. The specific steps are as follows:

[0074] I. Establish a three-dimensional simulation model including the gear pair and the fuel injection pipe. The structure of this simulation model is shown in Figures 3 - 5 (Note that the structures are the same, but the sizes are different, and they are all within the parameter ranges obtained from Equations 1, 2, and 3).

[0075] II. Design the structure of the fuel injection pipe.

[0076] The fuel injection pipe 1 includes a fan-shaped nozzle 11 and an inlet pipe 12. Its important dimensions are the fan-shaped side length l on the side close to the driving wheel (pinion), the fuel injection port radian α, the fan-shaped angle β, and the number of fuel injection ports n. The initial values of other structural parameters are as follows: the length and width of the inlet pipe nozzle are 8 mm each, and the length is 20 mm; the fan-shaped side length on the side of the driven wheel (big gear) of the fan-shaped nozzle is 15 mm, and the angle is 135°.

[0077] III. Design the working conditions of the reduction gearbox.

[0078] The comparison of the average volume fractions of the fan-shaped nozzle and the original nozzle at different fuel injection speeds is shown in Table 2. For the 9600 r / min working condition, when the fuel injection speed is greater than 40 m / s, the average volume fraction of the fan-shaped nozzle no longer increases with the increase of the fuel injection speed. For the 25000 r / min working condition, the increase of the fuel injection speed does cause the average volume fraction to increase, but the highest optimization multiple is also the case of the fuel injection speed of 40 m / s. Therefore, when performing orthogonal experiments on the fan-shaped structure parameters later, select the working condition of the fuel injection speed of 40 m / s and the rotational speed of 25000 r / min, and obtain a higher optimization multiple through orthogonal experiments.

[0079] Table 2 Average volume fraction of lubricating oil in the meshing area of the fan-shaped nozzle at each flow rate

[0080]

[0081] IV. Design an orthogonal experiment scheme

[0082] For the sector - like structure, select four structural parameters: the side length l of the driving wheel sector, the number of nozzles n, the radian α of the fuel injection port, and the sector angle β to conduct a four - factor and four - level orthogonal experiment. The factor - level table is shown in Table 3 as follows:

[0083] Table 3 Orthogonal experiment level table

[0084]

[0085] The orthogonal experiment uses the L16(4 4 ) orthogonal table, and finally obtains 16 groups of data as shown in Table 4.

[0086] Table 4 Orthogonal experiment results

[0087]

[0088]

[0089] IV. Select evaluation indicators to obtain the orthogonal experiment results.

[0090] Take the average volume fraction F of lubricating oil and the relative optimization multiple K as evaluation indicators. Among them, the average volume fraction F of lubricating oil can be obtained by simulating through existing conventional methods, and the relative optimization multiple K is calculated by formula (4).

[0091] V. Conduct range analysis on the evaluation indicators to obtain the optimal model.

[0092] For the four factors, use range analysis to determine the influence of these four parameters on the test indicators and analyze the variation law of these four parameters on the test indicators. The range formula is prior art and will not be elaborated here.

[0093] Conduct range analysis on the average volume fraction F and the relative optimization multiple K, and the results are shown in Tables 5 and 6. In the tables: is the value of the test indicator when the i - factor is at the j - th level; R i is the range of the i - factor; i = l, n, α, β; j = 1, 2, 3, 4.

[0094] Table 5 Range analysis of F

[0095]

[0096]

[0097] Table 6 Range analysis of K

[0098]

[0099] For F, the curve of its test index varying with the factor level is as Figure 7 (a) shown. The parameter influence weights are Rl > Rn > Rα > Rβ. The influence of the sector angle on the average volume fraction is relatively small, while the larger the l, the greater the increase in the volume fraction. This is because the larger the l, the closer the nozzle on the side of the driving wheel is to the gear, so it can significantly increase the average volume fraction of the lubricating oil. For K, the curve of its test index varying with the factor level is as Figure 7 (b) shown. The parameter influence weights are Rn > Rβ > Rl > Rα. The influence of the sector angle on it can be almost ignored, and the influence of l on it is the same as that on the average volume fraction.

[0100] According to the influence results of F, select the optimal combination of each factor (i.e., Figure 7 (a) the highest point of the average volume fraction of each factor). The obtained optimal model is l = 30, n = 4, α = 135°, β = 100°. The obtained simulation results are F = 0.13645 and K = 0.97361. According to the influence results of K, select the optimal combination of each factor (i.e., Figure 7 (b) the highest point of the relative optimization magnification of each factor). The obtained optimal model is l = 30, n = 4, α = 120°, β = 80°, which is the 14th group of orthogonal experiments. Its F and K are 0.11741 and 0.994722 respectively. Therefore, if a higher average volume fraction is required to achieve a better lubrication effect, the first optimal model can be selected. If the economy of lubrication is considered, the second optimal model can be selected.

[0101] VI. Comparative experiments on the effects of the embodiments.

[0102] It can be seen from the K value that the increase in the average volume fraction of the lubricating oil in the first optimal model is caused by the increase in the nozzle area. Therefore, the second optimal model is selected for subsequent comparison.

[0103] Select the oil injection outlet area of the optimal model, set the oil injection port area of the original nozzle model to be the same as that of the optimal model, and also set the oil injection speed to 40 m / s. Finally, the results of the average volume fraction of the lubricating oil in the meshing area are shown in Table 7. It can be seen that without changing the original structure, only increasing the nozzle area can increase the lubrication effect in the meshing area. However, the lubrication effect of the sector-shaped nozzle with the same nozzle area is better than the former, and its lubrication effect is improved by 15.94%. Therefore, the sector-shaped structure of the optimal model has better oil injection economy than the prototype nozzle of the same level.

[0104] Table 7 Model efficiency comparison

[0105]

[0106] The above are only the preferred embodiments of the present invention, and do not impose any limitation on the technical scope of the present invention. Therefore, any changes or modifications made in accordance with the claims and the description of the present invention shall fall within the scope covered by the patent of the present invention.

Claims

1. A gear lubrication spray oil pipe, characterized in that: It includes a fan-shaped nozzle (11). The cross-section of the fan-shaped nozzle includes a first fan-shaped side (111) and a second fan-shaped side (112). An oil inlet (115) is formed at one end between the two fan-shaped sides, and two or more oil injection nozzles (113) are provided at the other end. The oil outlet end faces of the oil injection nozzles are on the same arc-shaped side (114).

2. The gear lubrication spray oil pipe according to claim 1, characterized in that: It further includes an oil inlet pipe (12). The oil inlet pipe is connected to one end of the oil inlet (115) of the fan-shaped nozzle (11), and it is a straight pipe.

3. The gear lubrication spray oil pipe according to claim 1 or 2, characterized in that: The side lengths of the first fan-shaped side (111) and the second fan-shaped side (112), where the side length on the side of the pinion is greater than the side length on the side of the big gear.

4. The gear lubrication spray oil pipe according to claim 1 or 2, characterized in that: The first fan-shaped side (111) and the second fan-shaped side (112), where the angle of the fan-shaped side on the side of the pinion relative to the axis of the oil inlet is greater than the angle of the fan-shaped side on the side of the big gear relative to the axis of the oil inlet.

5. The gear lubrication spray oil pipe according to claim 1 or 2, characterized in that: The central angle of the arc-shaped side (114) is α, and the included angle between the first fan-shaped side (111) and the second fan-shaped side (112) is β. Among them, the angles of α and β are the same or different, and the vertices of α and β coincide or do not coincide.

6. The gear lubrication spray oil pipe according to claim 1 or 2, characterized in that: When the gear pair has gears with a module m = 2.5 - 4, a tooth number range of z = 15 - 40, and a gear transmission ratio of 1:1 - 8:3, the side length l of the fan-shaped side and the angle γ relative to the axis of the oil inlet are determined by the tooth number z of the same-side gear, and there is the following formula: l≤-z+55 (1) γ ≤ 135 + (40 - z) (2).

7. The gear lubrication spray oil pipe according to claim 6, characterized in that: The distance from the end face of the oil inlet (115) to the center of the gear set is d. When the central angle of the arc-shaped side (114), that is, the radian of the oil injection nozzle α, is less than 135°, there is the following formula: d ≥ 90 - 10×(4 - m) (3).

8. The optimized method for the fan-shaped oil injection structure according to any one of claims 1-5, characterized in that It includes the following steps: S05. Design an orthogonal experiment plan; select the structural parameters of the fan-shaped nozzle to be optimized as the orthogonal experiment factors, and determine the number of levels to design the orthogonal experiment plan; S10. Select evaluation indicators to obtain the orthogonal experiment results; S15. Conduct a range analysis on the evaluation indicators to obtain the optimal model, thereby completing the structural optimization of the fan-shaped nozzle.

9. The optimized method for the fan-shaped fuel injection structure according to claim 8, characterized in that: In the second step, select four structural parameters, namely the side length l of the fan-shaped side on the side of the pinion, the number of nozzles n, the radian α of the oil injection nozzle, and the fan-shaped angle β, to establish a four-factor and four-level orthogonal experiment plan.

10. The optimized method for the fan-shaped oil injection structure according to claim 8, characterized in that: In the third step, use the average volume fraction F of the lubricating oil or the relative optimization ratio K as the evaluation indicator, where the definition of the relative optimization ratio K is as follows:

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