A design method for oil spray lubrication of bearings

Abstract

A bearing oil spray lubrication design method includes setting relevant parameters of a hydraulic system; establishing an oil supply pipeline model to obtain relevant parameters of the oil supply pipeline; establishing a CFD analysis model of a local area between a bearing and its corresponding oil spray orifice, and obtaining a minimum spray orifice flow velocity v of the bearing through CFD simulation and calculation. 1 ; Perform the above modeling steps for all bearings and their corresponding oil injection orifices; set multiple groups of main flow and oil temperature data, perform CFD simulation on the oil supply pipeline, and obtain first data; judge the first data: if it does not meet the design requirements, repeat steps S2 to S5 until it meets the design requirements; make an oil temperature-main flow-main oil pressure curve, and read the lubricable range of the bearing on the oil temperature-main flow-main oil pressure curve.

Description

Technical Field

[0001] The invention relates to the field of bearing lubrication design, and in particular to a bearing oil spray lubrication design method. Background Art

[0002] Bearings are one of the key components of rotating machinery. Whether a piece of mechanical equipment can fully exert its performance is closely related to whether the bearing is properly lubricated. Lubrication is a necessary condition to ensure the normal operation of bearings and plays an important role in improving the bearing's load-bearing capacity and service life. Especially under high speed and high pressure conditions, sending lubricating oil into the relative motion area of ​​the bearing to form a layer of lubricating oil film can effectively separate the relative motion area to reduce friction and wear.

[0003] At present, when designing pressure lubrication of bearings, usually only the amount of oil sprayed from the oil supply pipeline to the bearing at the designed operating temperature and rated flow rate is calculated. The influence of the relative position of the oil injection hole and the bearing on the actual oil intake of the bearing is not evaluated, and the lubrication condition of the bearing at non-design oil temperature is not considered. As a result, it is easy for the bearing lubrication to meet the requirements under the design conditions, but when it deviates from the design conditions, the bearing lubrication flow rate is less or even no lubrication is obtained.

[0004] At present, the most common way to judge whether the bearing lubrication meets the requirements is to observe the lubrication of the bearing by using a transparent shell model experiment. This experimental method can visually observe whether the bearing is oil lubricated, but it also has its limitations: First, the experiment cannot cover a large temperature range, such as fogging in the shell under extremely low temperature conditions, which makes observation difficult, and the shell is prone to oil leakage under high temperature conditions; second, it cannot cover a large speed change range. Due to the strength limitation of the transparent shell, it is impossible to conduct experiments at high speeds; third, after discovering that the bearing has poor lubrication, the key parameters for improving bearing lubrication cannot be directly given. Therefore, it is currently difficult to have a comprehensive understanding of the actual situation of lubrication when designing bearing oil injection lubrication, and it is difficult to propose improvement plans. The design can only be modified according to the experimental situation and re-tested, which greatly prolongs the development time of the lubrication system. Summary of the invention

[0005] In view of this, the present invention provides a bearing oil spray lubrication design method that can be used for the pressure oil supply lubrication design of the electromechanical coupling system and motor bearing of a hybrid electric vehicle.

[0006] The bearing oil spray lubrication design method provided by the present invention comprises the following steps:

[0007] S1: Set the maximum main oil pressure Pmax, oil temperature range and lubricating oil type of the hydraulic system;

[0008] S2: Establish an oil supply pipeline model and obtain relevant distance parameters from the oil injection orifice of the oil supply branch pipe to the lowest point of its corresponding bearing;

[0009] S3: Establish a CFD analysis model of the area between the bearing and its corresponding oil injection orifice, perform CFD simulation and calculation, and obtain the minimum orifice flow rate v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil injection orifice 1 .

[0010] S4: Execute step S3 for all bearings and the corresponding oil injection orifices to obtain the minimum injection orifice flow rate v of the oil injection orifices corresponding to all bearings. 1 ;

[0011] S5: setting a plurality of sets of main flow and oil temperature data sets of the main oil supply pipeline, performing CFD simulation on the oil supply pipeline model according to the plurality of sets of main flow and oil temperature data sets, and obtaining a plurality of sets of first data corresponding to the plurality of sets of main flow and oil temperature data sets;

[0012] S6: Determine all the first data obtained in step S5 respectively. If the first data corresponding to any bearing does not meet the design requirements, repeat steps S2 to S5 for the oil injection orifice and the oil supply branch pipe corresponding to the bearing until the first data of the corresponding oil injection orifice meets the design requirements;

[0013] S7: Based on the main flow and oil temperature data set in step S6 and the first data, an oil temperature-main flow-main oil pressure curve is drawn, and the lubricable range of the bearing is read out on the oil temperature-main flow-main oil pressure curve.

[0014] Furthermore, the bearing oil spray lubrication design method further includes obtaining an optimal lubrication interval of the bearing based on the lubricable interval of the bearing and the recommended lubrication range of the bearing {Qmin, Qmax}, and the steps for obtaining the optimal lubrication interval of the bearing are as follows:

[0015] The recommended lubrication main flow range {Qmin, Qmax} is converted to the recommended nozzle flow rate range {vmin, vmax} through the conversion formula;

[0016] In step S7, a recommended nozzle flow rate range {vmin, vmax} curve is drawn on the oil temperature-main flow-main oil pressure curve diagram and the optimal lubrication range of the bearing is read out on the oil temperature-main flow-main oil pressure curve diagram.

[0017] Furthermore, the conversion formula is v=Q / A, wherein A is the area of ​​the injection orifice.

[0018] Furthermore, establishing the oil supply pipeline model in step S2 includes establishing an oil supply main pipe model, establishing an oil supply branch pipe model, and establishing a model of the space between the oil injection orifice of the oil supply branch pipe and its corresponding bearing.

[0019] Furthermore, the relevant distance parameters in step S2 include the horizontal distance S and the vertical distance h from the oil injection orifice to the lowest point of the bearing.

[0020] Furthermore, the CFD simulation and calculation are performed to obtain the minimum nozzle flow rate v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil spray orifice. 1 The steps are as follows:

[0021] According to the relevant distance parameters and the empirical formula, the minimum flow velocity v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil spray orifice is calculated. 0 ;

[0022] According to the minimum flow rate v 0 The CFD analysis model established was used to perform CFD calculation and CFD simulation on the oil supply pipeline model, and the minimum flow velocity v was corrected. 0 , obtain the minimum nozzle flow rate v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil spray orifice 1 ;

[0023] Furthermore, the empirical formula is v 0 =S / (2h / g) ^0.5 , where g is the acceleration due to gravity.

[0024] Furthermore, the first data in step S5 includes the main oil pressure P and the spray hole flow rate v corresponding to the bearing.

[0025] Furthermore, the design requirement in step S6 is: at the lowest operating temperature, the nozzle flow velocity v and the main oil pressure P both satisfy v>v 1 And P <Pmax。

[0026] Furthermore, the steps of making an oil temperature-main flow-main oil pressure curve diagram according to the main flow and oil temperature data set and the first data are as follows:

[0027] According to the main flow rate and oil temperature data set and the first data, a plurality of main flow rate isolines on the oil temperature-main flow rate-main oil pressure curve are drawn;

[0028] Through CFD simulation and calculation, the minimum nozzle flow velocity v of all bearings is obtained 1 The corresponding critical line;

[0029] Draw the minimum nozzle flow velocity v of all bearings on the oil temperature-main flow-main oil pressure curve 1 The corresponding critical line;

[0030] According to the set maximum main oil pressure Pmax, a maximum main oil pressure Pmax curve is drawn on the oil temperature-main flow-main oil pressure curve diagram.

[0031] The present invention establishes an oil supply pipeline model by presetting relevant parameters of the hydraulic system, and then quickly determines whether the bearing meets the design requirements at different working oil temperatures through a combination of CFD simulation and calculation. The present invention also includes obtaining the lubricated range of the bearing by making an oil temperature-main flow-main oil pressure curve and reading the lubricated range of the bearing on it according to the set conditions. The present invention also includes obtaining the optimal lubrication range of the bearing by converting the lubricated range of the bearing with the relevant data provided by the bearing manufacturer to obtain the optimal lubrication range of the bearing. The present invention provides a rapid and comprehensive evaluation method for the pressure oil supply lubrication design of the bearing, which is conducive to timely discovery and correction of problems in the design, greatly reducing the development time and development cost of the lubrication system.

[0032] The above description is only an overview of the technical solution of the present invention. In order to more clearly understand the technical means of the present invention, it can be implemented in accordance with the contents of the specification. In order to make the above and other purposes, features and advantages of the present invention more obvious and easy to understand, the following specifically cites a preferred embodiment and describes it in detail with the accompanying drawings as follows. BRIEF DESCRIPTION OF THE DRAWINGS

[0033] Figure 1 This is a schematic diagram of the main process of the bearing oil spray lubrication design method provided by the present invention.

[0034] Figure 2 This is a schematic diagram of the relative position of the lowest point of the bearing to its corresponding oil injection orifice in the design method provided by the present invention.

[0035] Figure 3 A schematic diagram of the oil temperature-main flow-main oil pressure curve involved in the design method provided by the present invention.

[0036] Figure 4 A schematic diagram of a critical line is added to the oil temperature-main flow-main oil pressure curve.

[0037] Figure 5 A schematic diagram of the critical line and the maximum main oil pressure curve is added to the oil temperature-main flow-main oil pressure curve. DETAILED DESCRIPTION

[0038] In order to further explain the technical means and effects adopted by the present invention to achieve the predetermined invention purpose, the present invention is described in detail below in conjunction with the accompanying drawings and preferred embodiments.

[0039] See also Figure 1 The bearing oil injection lubrication design method of the present invention can be used for the pressure oil supply lubrication design of the electromechanical coupling system and motor bearing of a hybrid vehicle. The method comprises the following steps:

[0040] S1: Set the maximum main oil pressure Pmax, oil temperature range and lubricating oil type of the hydraulic system;

[0041] Specifically, in order to protect the seals of the hydraulic system, the maximum main oil pressure Pmax of the hydraulic system needs to be set. When setting the maximum main oil pressure Pmax of the hydraulic system, the maximum main oil pressure Pmax of the hydraulic system cannot be set too low. If it is set too low, when the working temperature is low, even if the oil pressure input to the oil supply main reaches the maximum main oil pressure Pmax, the flow rate of the oil injection orifice is still insufficient, and the lubricating oil cannot be sprayed to the bearing position, resulting in the bearing being unable to be lubricated. In this embodiment, Pmax is set to the opening critical value of the pressure relief valve, 3.8 bar. Since there is no one-way valve in the system of this embodiment, Pmin does not need to be set and is set to zero by default.

[0042] When setting the oil temperature range, it is necessary to refer to the working environment temperature range of the equipment. When setting the working environment temperature range of the equipment, it is necessary to set the lower limit of the working environment temperature, because the lower limit of the working environment temperature range of the equipment has the most serious impact on the flow of the hydraulic system. At low temperatures, the viscosity of the lubricating oil will rise sharply. Under the condition of a certain oil supply pressure, the flow in the oil supply pipeline will drop sharply. In this embodiment, the oil temperature range is -30°C to 100°C.

[0043] When setting the lubricating oil, the density, viscosity and surface tension of the oil need to be considered. The above three parameters of the lubricating oil are used as input conditions when performing CFD analysis in step S3 and step S5. Since the viscosity of the oil is greatly affected by the oil temperature, in the CFD calculation, the viscosity changes due to the change in oil temperature, which causes the main oil pressure and the flow rate v of each bearing nozzle calculated by CFD to change accordingly. When selecting the lubricating oil, the lower the low-temperature viscosity of the oil and the smaller the surface tension, the more beneficial it is to the lubrication of the bearing.

[0044] S2: Establish an oil supply pipeline model and obtain relevant distance parameters from the oil injection orifice of the oil supply branch pipe to the lowest point of its corresponding bearing;

[0045] Specifically, step S2 includes: establishing an oil supply pipeline model; and obtaining relevant distance parameters from the oil injection orifice of the oil supply branch pipe to the lowest point of its corresponding bearing according to the established oil supply pipeline model.

[0046] Please also read Figure 2 , establishing the oil supply pipeline model includes establishing an oil supply main pipe model, establishing an oil supply branch pipe model and establishing a spatial model of the area between the oil injection orifice of the oil supply branch pipe and its corresponding bearing, and the relevant distance parameters that need to be obtained include the horizontal distance S and the vertical distance h from the oil injection orifice to the lowest point of the bearing. In this embodiment, the oil supply branches that need to be modeled include the oil supply branches corresponding to the front bearing of the drive motor, the rear bearing of the drive motor, the rear bearing of the intermediate shaft and the front bearing of the intermediate shaft.

[0047] To establish the oil supply main pipe model, it is necessary to determine the main flow range of the oil supply main pipe, and to establish the oil supply branch pipe model, it is necessary to determine the flow range of the oil supply branch pipe. Since the oil injection orifice diameter of the oil supply branch pipe determines the minimum lubrication flow of the corresponding bearing, and the sum of the flow of all oil supply branches is the flow of the oil supply main pipe, when establishing the oil supply pipeline model, once the diameter D of the oil injection orifice of all oil supply branches is set, the flow range of the oil supply branch pipe and the main flow range of the oil supply main pipe are also set.

[0048] S3: Establishing a CFD analysis model of the area between the bearing and its corresponding oil injection orifice, performing CFD simulation and calculation, and obtaining the minimum orifice flow rate v1 at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil injection orifice;

[0049] Further, the steps of CFD simulation and calculation are as follows:

[0050] According to the relevant distance parameters and the empirical formula, the minimum flow velocity v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil spray orifice is calculated. 0 ;

[0051] According to the minimum flow rate v 0 The CFD analysis model is used to perform CFD calculation and CFD simulation on the oil supply pipeline model to correct the minimum flow velocity v 0 , obtain the minimum nozzle flow rate v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil spray orifice 1 ;

[0052] Specifically, before performing CFD calculations, an estimated minimum flow velocity v is obtained through the estimated correction method. 0 To improve the acquisition of the actual minimum nozzle velocity v 1 efficiency.

[0053] Since CFD simulation itself is time-consuming, if there is no estimate close to the actual value, the only way is to narrow the range of the actual value by repeatedly guessing and designing within a larger data range. This process may require multiple adjustments. However, the minimum flow velocity v calculated by the empirical formula 0 After this initial value, the minimum nozzle flow rate v is obtained. 1 The number of CFD simulations and CFD calculations required will be reduced a lot, greatly improving work efficiency.

[0054] According to the empirical formula v 0 =S / (2h / g) ^0.5 The relative position relationship between the oil injection orifice and the lowest point of the bearing determines the minimum flow rate v at which the bearing can be lubricated by its corresponding oil injection orifice. 0 , in this embodiment, Figure 2The horizontal distance S from the lowest point of the bearing to its corresponding oil injection orifice is 30 mm, and the vertical distance h is 10 mm. The minimum flow rate v at which the bearing can be lubricated by its corresponding oil injection orifice can be calculated. 0 It is 0.66m / s.

[0055] According to the empirical formula, v 0 The flow rate of the nozzle is 0.66m / s. Through CFD simulation, the oil column is sprayed into the bearing just by adjusting the flow rate of the nozzle. Under the condition of considering the influence of air resistance and surface tension, the flow rate of the nozzle is corrected by CFD calculation. The simulation correction obtains the minimum nozzle flow rate v at which the bearing can be lubricated by its corresponding oil injection orifice. 1 It is 0.78m / s, that is, when the flow rate of the oil injection orifice is lower than 0.78m / s, the corresponding bearing cannot be lubricated normally.

[0056] S4: Execute step S3 for all bearings and the corresponding oil injection orifices to obtain the minimum injection orifice flow rate v of the oil injection orifices corresponding to all bearings. 1 ;

[0057] Specifically, in this embodiment, the bearings include a front bearing of the driving motor, a rear bearing of the driving motor, a rear bearing of the intermediate shaft and a front bearing of the intermediate shaft, and these bearings need to be subjected to step S3.

[0058] S5: setting a plurality of sets of main flow and oil temperature data sets of the main oil supply pipeline, performing CFD simulation on the oil supply pipeline model according to the plurality of sets of main flow and oil temperature data sets, and obtaining a plurality of sets of first data corresponding to the plurality of sets of main flow and oil temperature data sets;

[0059] The range of the main flow data is derived from the evaluation of the total oil demand for equipment cooling and lubrication. In this embodiment, the main flow range is set to 1L / min to 12 / min, and the oil temperature data is set to -30°C to 100°C according to step S1. The selection of the data group interval is to draw the oil temperature-main flow-main oil pressure curve with a certain drawing accuracy. In this embodiment, the oil temperature data acquisition interval is 5°C, and the main flow data acquisition interval is 1L / min.

[0060] Please also read Figure 3 Specifically, through CFD simulation, multiple groups of first data corresponding to the main flow rate and oil temperature are obtained from multiple groups of main flow rate and oil temperature data, and the first data include the main oil pressure P and the nozzle flow velocity v corresponding to the bearing.

[0061] S6: Determine all the first data obtained in step S5 respectively. If the first data corresponding to any bearing does not meet the design requirements, repeat steps S2 to S5 for the oil injection orifice and the oil supply branch pipe corresponding to the bearing until the first data of the corresponding oil injection orifice meets the design requirements;

[0062] Specifically, the design requirements are: at the lowest operating temperature, the nozzle flow velocity v and the main oil pressure P satisfy v>v 1 And P <Pmax。

[0063] S7: according to the main flow rate and oil temperature data set in step S6 and the plurality of first data sets, an oil temperature-main flow rate-main oil pressure curve is drawn, and the lubricable range of the bearing is read out on the oil temperature-main flow rate-main oil pressure curve;

[0064] Furthermore, the steps of making the oil temperature-main flow-main oil pressure curve diagram in step S7 are as follows:

[0065] According to the main flow rate and oil temperature data set in step S6 and the plurality of first data sets, a plurality of main flow rate isolines are drawn on the oil temperature-main flow rate-main oil pressure curve diagram;

[0066] Through CFD simulation and calculation, the minimum nozzle flow velocity v of all bearings is obtained 1 The corresponding critical line;

[0067] Draw the minimum nozzle flow velocity v of all bearings on the oil temperature-main flow-main oil pressure curve 1 The corresponding critical line;

[0068] According to the maximum main oil pressure Pmax set in step S1, a maximum main oil pressure Pmax curve is drawn on the oil temperature-main flow-main oil pressure curve diagram.

[0069] Please also read Figure 4 Specifically, the oil temperature-main flow-main oil pressure curve includes a plurality of main flow isolines. After obtaining the main oil pressure and oil temperature through the sensor, the main oil pressure and oil temperature can be checked. Figure 4 The main flow in the oil supply main pipe is obtained by using the main flow isovolumetric line on the surface.

[0070] Please also read Figure 5 , the minimum nozzle flow velocity v of all bearings 1 The corresponding critical line is essentially also the isometry line of the main flow. In this embodiment, the minimum nozzle velocity v corresponding to the nozzle of the front bearing of the intermediate shaft is 1When the oil temperature is 0℃, CFD calculation shows that when the main flow is 1.5L / min, the nozzle velocity v of the hole is less than 0.78m / s, and when the main flow is 2L / min, the nozzle velocity v of the hole is greater than 0.78m / s. Theoretically, when the nozzle velocity v of the hole is equal to 0.78m / s, the main flow of the oil supply main pipe will be between 1.5L / min and 2L / min. However, in order to increase the safety factor of the system, it is safer to take the main flow as 2L / min, that is, to set the critical line at 2L / min without further calculating the real main flow critical value between 1.5L / min and 2L / min.

[0071] Furthermore, the minimum nozzle flow rate v of all bearings is obtained by the above method. 1 The corresponding critical line is the lubrication critical value curve of the corresponding bearing. The nozzle velocity v represented by the nozzle velocity v isoline on the left side of these curves is lower than the minimum nozzle velocity v of the bearing. 1 , cannot be lubricated.

[0072] Please also read Figure 5 Specifically, the maximum main oil pressure Pmax has been set to 3.8 bar in step S1. When the main oil pressure exceeds this value, the pressure relief valve will open automatically, and the main oil pressure will therefore no longer be able to increase.

[0073] Specifically, the lubricated area of ​​the bearing can be read from the non-shaded area on the oil temperature-main flow-main oil pressure curve. In this embodiment, under the premise that the current maximum oil pressure is 3.8 bar, the bearing lubrication system design can meet the bearing lubrication requirements above the oil temperature of -5°C.

[0074] Furthermore, the present invention also includes obtaining the optimal lubrication interval of the bearing based on the lubricable interval of the bearing and the recommended lubrication range {Qmin, Qmax} of the bearing provided by the bearing manufacturer, and the steps for obtaining the optimal lubrication interval of the bearing are as follows:

[0075] The recommended lubrication main flow range {Qmin, Qmax} provided by the bearing manufacturer is converted into the recommended nozzle flow rate range {vmin, vmax} by using the conversion formula;

[0076] Specifically, the conversion formula is v=Q / A, where A is the area of ​​the injection orifice and Q is the flow rate.

[0077] In the same manner as the critical line corresponding to the minimum nozzle flow velocity v1 of the bearing is drawn in step S7, a critical line corresponding to the recommended nozzle flow velocity range {vmin, vmax} is drawn on the oil temperature-main flow-main oil pressure curve in step S7;

[0078] Read the optimal lubrication range of the bearing on the oil temperature-main flow-main oil pressure curve.

[0079] In summary, the present invention establishes an oil supply pipeline model by presetting the relevant parameters of the hydraulic system, and then quickly determines whether the bearing meets the design requirements at different working oil temperatures through a combination of CFD simulation and calculation. The present invention also includes obtaining the lubricated range of the bearing by making an oil temperature-main flow-main oil pressure curve and reading the lubricated range of the bearing on it according to the set conditions. The present invention also includes obtaining the optimal lubrication range of the bearing by converting the lubricated range of the bearing with the relevant data provided by the bearing manufacturer to obtain the optimal lubrication range of the bearing. The present invention provides a rapid and comprehensive evaluation method for the pressure oil supply lubrication design of the bearing, which is conducive to timely discovery and correction of problems in the design, greatly reducing the development time and development cost of the lubrication system.

[0080] The above description is only a preferred embodiment of the present invention and does not limit the present invention in any form. Although the present invention has been disclosed as a preferred embodiment as above, it is not used to limit the present invention. Any technician familiar with this profession can make some changes or modifications to equivalent embodiments of equivalent changes using the technical contents disclosed above without departing from the scope of the technical solution of the present invention. However, any simple modification, equivalent change and modification made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solution of the present invention still fall within the scope of the technical solution of the present invention.

Claims

1. A bearing oil spray lubrication design method, characterized in that: The bearing oil spray lubrication design method comprises the following steps: S1: Set the maximum main oil pressure Pmax, oil temperature range and lubricating oil type of the hydraulic system; S2: Establish an oil supply pipeline model and obtain relevant distance parameters from the oil injection orifice of the oil supply branch pipe to the lowest point of its corresponding bearing; S3: Establish a CFD analysis model of the area between the bearing and its corresponding oil injection orifice, perform CFD simulation and calculation, and obtain the minimum orifice flow rate v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil injection orifice 1 ; S4: Execute step S3 for all bearings and the corresponding oil injection orifices to obtain the minimum injection orifice flow rate v of the oil injection orifices corresponding to all bearings. 1 ; S5: setting a plurality of sets of main flow and oil temperature data sets of the main oil supply pipeline, performing CFD simulation on the oil supply pipeline model according to the plurality of sets of main flow and oil temperature data sets, and obtaining a plurality of sets of first data corresponding to the plurality of sets of main flow and oil temperature data sets; S6: Determine all the first data obtained in step S5 respectively. If the first data corresponding to any bearing does not meet the design requirements, repeat steps S2 to S5 for the oil injection orifice and the oil supply branch pipe corresponding to the bearing until the first data of the corresponding oil injection orifice meets the design requirements; S7: according to the main flow rate and oil temperature data set in step S6 and the first data, an oil temperature-main flow rate-main oil pressure curve is drawn, and the lubricable range of the bearing is read out on the oil temperature-main flow rate-main oil pressure curve; The first data in step S5 includes the main oil pressure P and the nozzle flow velocity v corresponding to the bearing.

2. The bearing oil spray lubrication design method according to claim 1 is characterized in that: The bearing oil spray lubrication design method further includes obtaining an optimal lubrication interval of the bearing based on the lubricable interval of the bearing and the recommended lubrication range of the bearing {Qmin, Qmax}, and the steps for obtaining the optimal lubrication interval of the bearing are as follows: The recommended lubrication main flow range {Qmin, Qmax} is converted to the recommended nozzle flow rate range {vmin, vmax} through the conversion formula; In step S7, a recommended nozzle flow rate range {vmin, vmax} curve is drawn on the oil temperature-main flow-main oil pressure curve diagram and the optimal lubrication range of the bearing is read out on the oil temperature-main flow-main oil pressure curve diagram.

3. The bearing oil spray lubrication design method according to claim 2 is characterized in that: The conversion formula is v=Q / A, where A is the area of ​​the injection orifice and Q is the flow rate.

4. The bearing oil spray lubrication design method according to claim 1 is characterized in that: The establishment of the oil supply pipeline model in step S2 includes establishing an oil supply main pipe model, establishing an oil supply branch pipe model, and establishing a model of the space between the oil injection orifice of the oil supply branch pipe and its corresponding bearing.

5. The bearing oil spray lubrication design method according to claim 1 is characterized in that: The relevant distance parameters in step S2 include the horizontal distance S and the vertical distance h from the oil injection orifice to the lowest point of the bearing.

6. The bearing oil spray lubrication design method according to claim 1 is characterized in that: The CFD simulation and calculation are performed to obtain the minimum nozzle flow rate v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil spray orifice. 1 The steps are as follows: According to the relevant distance parameters and the empirical formula, the minimum flow velocity v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil spray orifice is calculated. 0 ; According to the minimum flow rate v 0 The CFD analysis model established was used to perform CFD calculation and CFD simulation on the oil supply pipeline model, and the minimum flow velocity v was corrected. 0 , obtain the minimum nozzle flow rate v at which the bearing can be lubricated by the lubricating oil sprayed from its corresponding oil spray orifice 1 .

7. The bearing oil spray lubrication design method according to claim 6 is characterized in that: The empirical formula is v 0 =S / (2h / g) ^0.5 , where g is the acceleration of gravity; S is the horizontal distance from the lowest point of the bearing to its corresponding oil injection orifice; and h is the vertical distance from the lowest point of the bearing to its corresponding oil injection orifice.

8. The bearing oil spray lubrication design method according to claim 1, characterized in that: The design requirement in step S6 is: at the lowest operating temperature, the nozzle flow velocity v and the main oil pressure P both satisfy v>v 1 And P <Pmax。 9. The bearing oil spray lubrication design method according to claim 1, characterized in that: The steps of making an oil temperature-main flow-main oil pressure curve diagram according to the main flow and oil temperature data set and the first data are as follows: According to the main flow rate and oil temperature data set and the first data, a plurality of main flow rate isolines on the oil temperature-main flow rate-main oil pressure curve are drawn; Through CFD simulation and calculation, the minimum nozzle flow velocity v of all bearings is obtained 1 The corresponding critical line; Draw the minimum nozzle flow velocity v of all bearings on the oil temperature-main flow-main oil pressure curve 1 The corresponding critical line; According to the set maximum main oil pressure Pmax, a maximum main oil pressure Pmax curve is drawn on the oil temperature-main flow-main oil pressure curve diagram.

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