A design method and system for a lubricating oil circulation system for bearing heat dissipation

Abstract

The present invention belongs to the technical field of aircraft lubricating oil thermal management, and discloses a design method and system for a lubricating oil circulation system for bearing heat dissipation, including: conducting a theoretical analysis of bearing heat generation to obtain the calculation process of bearing heat generation; according to the bearing heat generation calculation process, using the submodel editor in AMESim to compile the bearing heat generation calculation submodel to obtain the simulated heat input data; establishing a one-dimensional lubricating oil circulation system simulation model in AMESim to obtain the system-level input, output, dynamic behavior, and interaction parameters; constructing a three-dimensional bearing component simulation model in STAR-CCM+ to obtain the inlet and outlet conditions, operating parameters, and interaction parameters; and running the simulation. The present invention can not only improve the heat dissipation performance of the lubricating oil, effectively reduce the operating temperature of the bearing, but also enhance the stability and reliability of the system, providing an advanced cooling solution for the new generation of high-performance aircraft and engines.

Description

Technical Field

[0001] The present invention relates to the technical field of aircraft lubricating oil thermal management, and specifically relates to a design method and system for a lubricating oil circulation system for bearing heat dissipation. Background Art

[0002] In modern aero-engines and high-performance mechanical systems, bearings are important components that support high-speed rotating parts, and are directly related to the stability and life of the system. With the continuous improvement of engine power and the integration level of mechanical equipment, the operation challenges of bearings in high-temperature and high-pressure environments have become increasingly prominent, and the existing lubricating oil cooling design methods are gradually showing limitations in meeting the heat dissipation requirements of the new generation of high-performance equipment.

[0003] As a key component of bearing cooling, the lubricating oil circulation system undertakes the task of providing efficient cooling for bearings in high-temperature and high-speed environments. However, in modern aircraft and engines, with the improvement of engine performance, the increase in heat load, and the strict requirements for space and weight, traditional lubricating oil cooling methods face many challenges. Therefore, the design of the lubricating oil circulation system urgently needs innovation, which not only needs to meet the requirements of efficient cooling, but also needs to ensure the reliability and durability of the system under extreme working conditions. Summary of the Invention

[0004] To solve the above technical problems, the present invention provides a design method and system for a lubricating oil circulation system for bearing heat dissipation, aiming to improve the cooling efficiency of the lubricating oil circulation system, comprehensively considering the temperature control, flow regulation, and circulation path optimization of the lubricating oil under different working conditions, and introducing a modular design based on simulation software to achieve precise control and efficient heat dissipation of the system. Through this method, not only can the heat dissipation performance of the lubricating oil be improved, the operating temperature of the bearing can be effectively reduced, but also the stability and reliability of the system can be enhanced, providing an advanced cooling solution for the new generation of high-performance aircraft and engines.

[0005] The present invention provides a design method for a lubricating oil circulation system for bearing heat dissipation, and the method includes:

[0006] Conduct a theoretical analysis of the heat generated by the bearing to obtain the calculation process of bearing heat generation;

[0007] According to the calculation process of bearing heat generation, use the submodel editor in AMESim to compile the bearing heat generation calculation submodel to obtain the simulated heat input data;

[0008] Establish a one-dimensional lubricating oil circulation system simulation model in AMESim to obtain the input, output, dynamic behavior, and interaction parameters at the system level;

[0009] Build a three-dimensional bearing component simulation model in STAR-CCM+ to obtain the inlet and outlet conditions, operating condition parameters, and interaction parameters;

[0010] Run the simulation according to the heat input data, system-level input, output, dynamic behavior, and interaction parameters, inlet and outlet conditions, operating conditions parameters, and interaction parameters.

[0011] Preferably, the bearing heat generation calculation process includes:

[0012] Q bfr = CZρL 2 u 3 β′,

[0013] where C1 is the bearing friction coefficient, Z is the number of rollers, ρ is the density of the lubricating oil used, L is the effective length of the rollers, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of the radial clearance on the power loss, C2 is the bearing hydrodynamic resistance coefficient, and C = C1 + C2 is the total bearing friction coefficient.

[0014] Preferably, the bearing heat generation calculation sub-model includes: structural parameter P, input parameter V0, output parameter V1, and internal parameter V2;

[0015] where the structural parameter P includes: the pitch diameter D of the short cylindrical roller bearing m , the diameter D of the rollers r , the effective length L of the short cylindrical rollers, the number Z of the short cylindrical rollers, and the radial clearance h matched by the bearing;

[0016] The input parameter V0 includes: the bearing speed Rs, the radial load F of the bearing r , the kinematic viscosity nu of the lubricating oil, the density rho, the thermal conductivity k, and the specific heat capacity Cp with the selected qualitative temperature as the lubricating oil outlet temperature;

[0017] The output parameter V1 includes: the total bearing friction heat generation power Q;

[0018] The internal parameter V2 includes: the circumferential speed v of the bearing cage, the lubricating oil Prandtl number Pr, the Reynolds number Re, the centrifugal force Fc of the rollers, the average load Fcp on the roller bus, the Euler coefficient Eu, the total resistance coefficient f, and the loss influence coefficient beta.

[0019] Preferably, in the one-dimensional lubricating oil circulation system simulation model, the TFFD04-1 in the Thermal hydraulic library of AMESim is used to define the physical properties of the lubricating oil, the TFMPT0-2 model in the Thermal hydraulic library of AMESim is used as the lubricating oil source, the TFL001-1 model in the Thermal hydraulic Resistance library of AMESim is used as the pipeline, the bearing heat generation calculation sub-model compiled in AMESim is used to calculate the bearing heat generation, the TFPTS-1 in the Thermal hydraulic library of AMESim is used to define the reference temperature and reference pressure of the lubricating oil, the TFPRO model in the Thermal hydraulic library of AMESim is used to reference the density, thermal conductivity, kinematic viscosity and specific heat capacity of the lubricating oil, and the DYNCOSIMNETWORK01-1 model in the Generic cosimulation library of AMESim is used to complete the modeling work of the combined simulation thermal analysis of the bearing cavity.

[0020] Preferably, the three-dimensional bearing component simulation model includes:

[0021] Establish a three-dimensional model of the internal fluid of the bearing cavity; perform mesh division on the three-dimensional model of the internal fluid of the bearing cavity to generate a three-dimensional model mesh; set the computational domain model; set the boundary conditions; set the solver parameters; set the stop criterion parameters; set the link connection.

[0022] The present invention also provides a lubricating oil circulation system design system for bearing heat dissipation, which is used to implement any one of the above methods. The system includes: an analysis module, a compilation module, a one-dimensional model construction module, a three-dimensional model construction module, and a simulation module;

[0023] The analysis module is used to perform theoretical analysis on the bearing heat generation to obtain the bearing heat generation calculation process;

[0024] The compilation module is used to compile the bearing heat generation calculation sub-model in AMESim using the submodel editor according to the bearing heat generation calculation process to obtain the simulated heat input data;

[0025] The one-dimensional model construction module is used to establish a one-dimensional lubricating oil circulation system simulation model in AMESim to obtain the system-level input, output, dynamic behavior, and interaction parameters;

[0026] The three-dimensional model construction module is used to build a three-dimensional bearing component simulation model in STAR-CCM+ to obtain the inlet and outlet conditions, operating condition parameters, and interaction parameters;

[0027] The simulation module is used to perform simulations based on heat input data, system-level inputs, outputs, dynamic behaviors, and interaction parameters, inlet and outlet conditions, operating conditions parameters, and interaction parameters.

[0028] Preferably, the bearing heat generation calculation process includes:

[0029] Q bfr = CZρL 2 u 3 β′,

[0030] Where, C1 is the bearing friction coefficient, Z is the number of rollers, ρ is the density of the lubricating oil used, L is the effective length of the rollers, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of the radial clearance on the power loss, C2 is the bearing hydrodynamic resistance coefficient, and C = C1 + C2 is the total bearing friction coefficient.

[0031] Preferably, the bearing heat generation calculation sub-model includes: structural parameter P, input parameter V0, output parameter V1, and internal parameter V2;

[0032] Where, the structural parameter P includes: the pitch diameter D of the short cylindrical roller bearing m , the diameter D of the rollers r , the effective length L of the short cylindrical rollers, the number Z of the short cylindrical rollers, and the radial clearance h matched by the bearing;

[0033] The input parameter V0 includes: the bearing rotational speed Rs, the radial load F of the bearing r , the kinematic viscosity nu of the lubricating oil, the density rho, the thermal conductivity k, and the specific heat capacity Cp with the selected qualitative temperature being the lubricating oil outlet temperature;

[0034] The output parameter V1 includes: the total bearing friction heat generation power Q;

[0035] The internal parameter V2 includes: the circumferential speed v of the bearing cage, the lubricating oil Prandtl number Pr, the Reynolds number Re, the centrifugal force Fc of the rollers, the average load Fcp on the roller generatrix, the Euler coefficient Eu, the total resistance coefficient f, and the loss influence coefficient beta.

[0036] Preferably, in the one-dimensional lubricating oil circulation system simulation model, the TFFD04-1 in the Thermal hydraulic library of AMESim is used to define the physical properties of the lubricating oil, the TFMPT0-2 model in the Thermal hydraulic library of AMESim is used as the lubricating oil source, the TFL001-1 model in the Thermal hydraulic Resistance library of AMESim is used as the pipeline, the bearing heat generation calculation sub-model compiled in AMESim is used to calculate the bearing heat generation, the TFPTS-1 in the Thermal hydraulic library of AMESim is used to define the reference temperature and reference pressure of the lubricating oil, the TFPRO model in the Thermal hydraulic library of AMESim is used to reference the density, thermal conductivity, kinematic viscosity and specific heat capacity of the lubricating oil, and the DYNCOSIMNETWORK01-1 model in the Generic cosimulation library of AMESim is used to complete the modeling work of the combined simulation thermal analysis of the bearing cavity.

[0037] Preferably, the three-dimensional bearing component simulation model includes:

[0038] Establish a three-dimensional model of the fluid inside the bearing cavity; perform mesh division on the three-dimensional model of the fluid inside the bearing cavity to generate a three-dimensional model mesh; set the computational domain model; set the boundary conditions; set the solver parameters; set the stopping criterion parameters; set the link connection.

[0039] Compared with the prior art, the beneficial effects of the present invention are as follows:

[0040] The present invention aims to provide a design method and system for a lubricating oil circulation system for bearing heat dissipation, which can effectively control the temperature rise of the bearing under extreme operating conditions through innovative design means, and improve the working reliability and life of the bearing assembly. This method optimizes the flow path and heat transfer efficiency of the lubricating oil through precise thermal management technology to reduce the thermal load of the system and improve the cooling effect, thereby improving the overall thermal management level of the system. Using advanced computational simulation means, this method not only realizes the compact design of the cooling system, but also reduces the system power consumption and mass by reasonably configuring the fluid circulation scheme. In addition, while meeting the high-efficiency requirements of aero-engines, this design provides greater flexibility to meet the bearing cooling requirements under complex working conditions. Description of the Drawings

[0041] To more clearly illustrate the technical solutions of the present invention, the following briefly introduces the drawings required in the embodiments. Obviously, the drawings in the following description are only some embodiments of the present invention. For those of ordinary skill in the art, without creative efforts, other drawings can be obtained based on these drawings.

[0042] Figure 1 Schematic diagram of the design method flow of a lubricating oil circulation system for bearing heat dissipation according to an embodiment of the present invention;

[0043] Figure 2 Schematic diagram of the parameter relationship of the AMESim software compilation model according to an embodiment of the present invention;

[0044] Figure 3 Schematic diagram of the drawing icon of BHC according to an embodiment of the present invention;

[0045] Figure 4 Schematic diagram of the one-dimensional system simulation model of the bearing chamber thermal analysis AMESim according to an embodiment of the present invention;

[0046] Figure 5 Schematic diagram of the simplified three-dimensional model of the internal fluid of the bearing chamber according to an embodiment of the present invention;

[0047] Figure 6 Schematic diagram of the three-dimensional model mesh according to an embodiment of the present invention;

[0048] Figure 7 Schematic diagram of the cross-sectional mesh situation of the inlet pipe in the +X direction according to an embodiment of the present invention. Specific implementation manners

[0049] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the drawings in the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, rather than all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts belong to the scope of protection of the present invention.

[0050] It should be noted that, unless otherwise defined, the technical terms or scientific terms used in the embodiments of the present disclosure should have the ordinary meanings understood by those of ordinary skill in the art to which the present disclosure belongs. The "first", "second" and similar terms used in the embodiments of the present disclosure do not indicate any order, quantity or importance, but are only used to distinguish different components. Words such as "including" or "comprising" mean that the elements or objects appearing before the word cover the elements or objects listed after the word and their equivalents, without excluding other elements or objects. Words such as "connected" or "coupled" are not limited to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "Upper", "lower", "left", "right", etc. are only used to represent relative positional relationships, and when the absolute position of the object being described changes, the relative positional relationship may also change accordingly.

[0051] To make the above objects, features and advantages of the present invention more obvious and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0052] Embodiment 1

[0053] As Figure 1 shown, the embodiment of the present invention provides a design method for a lubricating oil circulation system for bearing heat dissipation.

[0054] (1) Theoretical analysis of bearing heat generation: Complete the theoretical analysis of bearing heat generation to obtain the bearing heat generation calculation process.

[0055] (2) Compilation of bearing heat generation model: According to the bearing heat generation theoretical analysis calculation process, use submodeleditor in AMESim software to compile the bearing heat generation calculation submodel to provide heat input data for subsequent simulations.

[0056] (3) One-dimensional lubricating oil circulation system simulation modeling: Establish a one-dimensional system-level simulation model in AMESim, and define the system-level input, output, dynamic behavior, and interaction parameters.

[0057] (4) Three-dimensional bearing component simulation modeling: Build a three-dimensional simulation model of bearing cavity fluid heat transfer in STAR-CCM+, and define the inlet and outlet conditions, operating parameters, and interaction parameters, etc.

[0058] (5) Run the simulation.

[0059] In this embodiment, (1) Theoretical analysis of bearing heat generation

[0060] The research object of this patent is a centripetal short cylindrical roller bearing, and the heat generation consists of the following four parts:

[0061] ① When the roller revolves around the bearing center along the raceway between the inner and outer rings, sliding friction heat will be generated between the roller and the raceway;

[0062] ② While the roller is revolving, it will rotate accordingly inside the pocket of the cage. When the roller rotates, sliding friction heat will be generated;

[0063] ③ Sliding friction heat will be generated between the two end faces of the roller and the side faces of the rib of the bearing ring;

[0064] ④ Sliding friction heat will be generated between the bottom of the bearing cage and the guiding surface for the inner ring.

[0065] To remove the frictional heat of the bearing, when the bearing operates normally under lubricating oil lubrication conditions, hydrodynamic resistance losses will be generated. The hydrodynamic resistance losses are specifically composed of the following four parts:

[0066] ① At the inlet of the contact area between the roller and the raceway, the roller has rotation and revolution, and the lubricating oil is pumped in and the shear force generates hydrodynamic resistance losses;

[0067] ② At the inlet of the contact area between the rolling element and the pocket of the cage, the liquid is pumped in and the shear force generates hydrodynamic resistance losses;

[0068] ③ Losses generated by the fluid viscous shear force between the inner and outer cylindrical surfaces of the cage and the guiding surfaces of the inner and outer rings;

[0069] ④ At the interface between the roller and the gas-liquid two-phase fluid inside the bearing cavity, hydrodynamic resistance losses are accompanied.

[0070] The calculation formula for the frictional heat generation power is:

[0071] Q f =C1ZρL 2 u 3 β′ (1)

[0072] The calculation formula for the hydrodynamic resistance losses is:

[0073] Q l =C2ZρL 2 u 3 β′ (2)

[0074] Therefore, the calculation formula for the total frictional heat generation power of the bearing is:

[0075] Q bfr =CZρL 2 u 3 β′ (3)

[0076] In the above formulas, C1 is the bearing friction coefficient, Z is the number of rollers, ρ is the density of the lubricating oil used, L is the effective length of the rollers, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of the radial clearance on the power loss, C2 is the bearing hydrodynamic resistance coefficient, and C = C1 + C2 is the total bearing friction coefficient.

[0077] The calculation method of the total bearing friction coefficient is as follows:

[0078] ① Calculate the circumferential speed u of the bearing cage:

[0079]

[0080] In the formula: D m (unit: m) is the pitch diameter of the short cylindrical roller bearing, D b (unit: m) is the diameter of the roller, and n (unit: r / min) is the bearing speed.

[0081] ② Calculate the Prandtl number Pr of the lubricating oil:

[0082] Pr = Cn ρ v / k (5)

[0083] ③ Calculate the Reynolds number Re:

[0084]

[0085] In the formula, Re is the Reynolds number of the lubricating oil flow calculated with the circumferential speed of the bearing cage as the characteristic speed and the roller length as the characteristic dimension. L (unit: m) is the effective length of the short cylindrical roller, v (unit: m 2 / s) is the kinematic viscosity of the lubricating oil, ρ (unit: kg / m 3 ) is the density, k (unit: W / K / m) is the thermal conductivity, and C p is the specific heat capacity with the selected qualitative temperature as the lubricating oil outlet temperature.

[0086] ④ Calculate the centrifugal force F of the roller c (unit: daN):

[0087] F c = 1.225×10 3 ×(L 2 u 3 / D m ) (7)

[0088] ⑤ Calculate the average load F acting on the roller busbar cp (unit: daN):

[0089] F cp = (2.9F r + ZFc ) / 2Z (8)

[0090] In the formula, F r (unit: daN) is the radial load of the bearing, and Z is the number of short cylindrical rollers.

[0091] ⑥ Calculate the Euler coefficient Eu:

[0092] Eu = 10F cp / ρ(uL) 2 (9)

[0093] ⑦ Calculate the total resistance coefficient C:

[0094] C = 1.26Re -0.5 Eu 0.5 Pr 0 +46.5×10 3 Re -1 Pr -0.8 (10)

[0095] ⑧ The radial clearance of the bearing will have a certain impact on the heat generation power, and a coefficient needs to be multiplied for correction in the heat generation power calculation. Its loss influence coefficient is expressed as β, and the calculation formula is:

[0096] β = 1 + 1.7(0.1 - h) (11)

[0097] Where h (unit: mm) is the radial clearance matched by the bearing.

[0098] In this embodiment, (2) Compilation of the bearing heat generation model

[0099] When compiling the bearing heat generation calculation sub - model using AMESim, it is necessary to determine various data in the model. Generally speaking, the sub - model data is divided into four types:

[0100] ① P: Structural parameters, generally the model structure size parameters;

[0101] ② V0: Input parameters, that is, the parameters that need to be input or introduced into the model;

[0102] ③ V1: Output parameters, that is, the parameters that the model needs to output;

[0103] ④ V2: Internal parameters, that is, the parameters for internal calculation in the model.

[0104] The relationship of the sub - model parameters of the AMESim software is as Figure 2 shown:

[0105] In the present invention, the various data are respectively:

[0106] ① P: D m(Unit: m) Pitch diameter of the short cylindrical roller bearing, D r (Unit: m) Diameter of the roller, L (Unit: m) is the effective length of the short cylindrical roller, Z is the number of short cylindrical rollers, h (Unit: mm) is the radial clearance matched by the bearing

[0107] ② V0: Rs (Unit: r / min) Bearing speed, F r (Unit: daN) Radial load of the bearing, nu (Unit: cst) Kinematic viscosity of the lubricating oil, rho (Unit: g / cm 3 ) Density, k (Unit: W / K / m) Thermal conductivity, Cp (Unit: J / kg / K) Specific heat capacity at the selected qualitative temperature of the lubricating oil outlet temperature

[0108] ③ V1: Q (Unit: W) Total heat generation power of bearing friction

[0109] ④ V2: Circumferential speed v of the bearing cage, Prandtl number Pr of the lubricating oil, Reynolds number Re, centrifugal force Fc (Unit: daN) of the roller, average load Fcp (Unit: daN) on the roller bus, Euler coefficient Eu, total resistance coefficient f, loss influence coefficient denoted as beta

[0110] Compile the submodel according to the following steps:

[0111] ① Draw the icon

[0112] Right-click on Signal, Control library, click Add component submodel, edit Name as BHC, Descripti-on as bearing heat circulation, click Draw icon, and draw the icon as Figure 3 shown below:

[0113] Click OK to exit the editing

[0114] ② Parameter settings

[0115] Click Tools and Submodel Editor in sequence to enter the model editing module; select the BHC model created above and click open; set Ports, Internal variables, and Real parameters, and the setting results are shown in Table 1, Table 2, and Table 3 below:

[0116] Table 1 Parameter settings table for Ports

[0117]

[0118] Table 2 Parameter settings table for Internal variables

[0119]

[0120] Table 3 Real parameters parameter setting table

[0121]

[0122]

[0123] ③ Model encoding

[0124] Click generate submodel code and open submodel code in sequence to open the encoding interface and enter the following program:

[0125] / *Submodel BHC skeleton created by AME Submodelediting utility

[0126] ??10?14 17:57:14 2024* /

[0127] #include<math.h>

[0128] #include<stdio.h>

[0129] #include<stdlib.h>

[0130] #include<assert.h>

[0131] #include"ameutils.h"

[0132] / *

[0133] *******************************************************************************

[0134] ******************************************************************************** /

[0135] #define_SUBMODELNAME_"BHC"

[0136] / *>>>>>>>>>>>>Insert Private Code Here.* /

[0137] / *<<<<<<<<<<<<End of Private Code.* /

[0138] / *There are 5 real parameters:

[0139] Dm Bearing pitch circle diameter [m]

[0140] Dr roller diameter [m]

[0141] L roller length [m]

[0142] Z roller number [null]

[0143] h radial clearance [mm -> m]

[0144] * /

[0145] void bhcin_(int *n, double rp[5])

[0146] {

[0147] int loop, error;

[0148] / *>>>>>>>>>>>>Extra Initialization Function Declarations Here.* / / *<<<<<<<<<<<<End of Extra Initialization declarations.* / double Dm, Dr, L, Z, h;

[0149] Dm = rp[0];

[0150] Dr = rp[1];

[0151] L = rp[2];

[0152] Z = rp[3];

[0153] h = rp[4];

[0154] loop = 0;

[0155] error = 0;

[0156] / *

[0157] If necessary, check values of the following:

[0158] rp[0..4]

[0159] * /

[0160] / *>>>>>>>>>>>>Initialization Function Check Statements.* /

[0161] / *<<<<<<<<<<<<End of Initialization Check Statements.* / if(ameHandleSubmodelError(_SUBMODELNAME_, *n, error)){

[0162] return;

[0163] }

[0164] / *Common->SI units conversions.* /

[0165] rp[4] *= 1.00000000000000e-03;

[0166] h = rp[4];

[0167] / *>>>>>>>>>>>>Initialization Function Executable Statements. * / / *<<<<<<<<<<<<End of Initialization Executable Statements.* / }

[0168] / *There are 7 ports.

[0169] Port 1 has 1 variable:

[0170] 1 Rs rotary speed [rev / min -> rad / s] basic variable input Port 2 has 1 variable:

[0171] 1 Q Heat [W] basic variable output

[0172] Port 3 has 1 variable:

[0173] 1 Fr Load [daN -> N] basic variable input

[0174] Port 4 has 1 variable:

[0175] 1 k thermal conductivity [W / m / K] basic variable input Port 5 has 1 variable:

[0176] 1 nu kinematic [cSt -> m**2 / s] basic variable input Port 6 has 1 variable:

[0177] 1 rho density [kg / m**3] basic variable input

[0178] Port 7 has 1 variable:

[0179] 1 Cp Isobaric specific heat capacity [J / kg / K] basic variable input

[0180] * /

[0181] / *There are 8 internal variables.

[0182] 1 v peripheral speed [m / s] basic variable

[0183] 2 Pr Prandtl number [null] basic variable

[0184] 3 Re Reynolds number [null] basic variable

[0185] 4 Fc centrifugal force [daN -> N] basic variable

[0186] 5 Fcp average load [daN -> N] basic variable

[0187] 6 Eu Euler number [null] basic variable

[0188] 7 f Total drag coefficient[null]basic variable

[0189] 8 beta influence coefficient[null]basic variable

[0190] * /

[0191] void bhc_(int*n,double*Rs,double*Q,double*Fr,double*k

[0192] ,double*nu,double*rho,double*Cp,double*v,double*Pr

[0193] ,double*Re,double*Fc,double*Fcp,double*Eu,double*f

[0194] ,double*beta,double rp[5])

[0195] {

[0196] int loop;

[0197] / *>>>>>>>>>>>>Extra Calculation Function Declarations Here.* / / *<<<<<<<<<<<<End of Extra Calculation declarations.* / double Dm,Dr,L,Z,h;

[0198] Dm = rp[0];

[0199] Dr = rp[1];

[0200] L = rp[2];

[0201] Z = rp[3];

[0202] h = rp[4];

[0203] loop = 0;

[0204] / *Common->SI units conversions.* /

[0205] *Rs *= 1.04719755119660e-01;

[0206] *Fr* = 1.00000000000000e+01;

[0207] *nu* = 1.00000000000000e-06;

[0208] / *

[0209] Set all submodel outputs below:

[0210] *Q =??;

[0211] *v =??;

[0212] *Pr =??;

[0213] *Re =??;

[0214] *Fc =??;

[0215] *Fcp =??;

[0216] *Eu =??;

[0217] *f =??;

[0218] *beta =??;

[0219] * /

[0220] / *>>>>>>>>>>>>Calculation Function Executable Statements.* / *v = acos(-1) * (Dm - Dr) * (*Rs* * 60 / 2 / acos(-1)) / 120;

[0221] *Pr = (*Cp) * (*rho) * (*nu) / (*k);

[0222] *Re = (*v) * (Dr) / (*nu);

[0223] *Fc = 1225 * pow(L, 3) * pow(*v, 2) / (Dm) * 10;

[0224] *Fcp = (2.92 * (*Fr / 10) + Z * (*Fc / 10)) / 2 / Z * 10;

[0225] *Eu = 10 * (*Fcp) / pow(L, 2) / pow(*v, 2) / (*rho);

[0226] *f = 1.26 * pow(*Re, -0.5) * pow(*Eu, 0.5) + 46.5 * 1000 * pow(*Re, -1) * pow(*Pr, -0.8);

[0227] *beta = 1 + 1.7 * (0.1 - h);

[0228] *Q = (*f) * (*beta) * (Z) * (*rho) * pow(L, 2) * pow(*v, 3);

[0229] / *<<<<<<<<<<<<End of Calculation Executable Statements.* /

[0230] / *SI->Common units conversions.* /

[0231] *Rs / = 1.04719755119660e-01;

[0232] *Fr / = 1.00000000000000e+01;

[0233] *nu / = 1.00000000000000e-06;

[0234] *Fc / = 1.00000000000000e+01;

[0235] *Fcp / = 1.00000000000000e+01;

[0236] }

[0237] Click to compile the current submodel.

[0238] ④ Complete compilation

[0239] Click to save, close the Submodel Editor interface, and complete the compilation of the bearing heat generation model.

[0240] In this embodiment, (III) One-dimensional lubricating oil circulation system simulation modeling

[0241] The bearing chamber thermal analysis AMESim one-dimensional system simulation model is used to provide and receive key data for the three-dimensional heat transfer simulation analysis of the bearing chamber.

[0242] Establish a complete one-dimensional system-level simulation model in AMESim as Figure 4 shown:

[0243] The model includes the following key parts:

[0244] ① Definition of lubricating oil

[0245] The physical properties of the lubricating oil are defined using TFFD04 - 1 in the Thermal hydraulic library of AMESim for subsequent simulation calls. In this invention, 4050 lubricating oil is used as the coolant for engine lubrication and cooling.

[0246] ② Lubricating oil source

[0247] The lubricating oil source is used to provide lubricating oil at a certain temperature, pressure, and flow rate.

[0248] The TFMPT0 - 2 model in the Thermal hydraulic library of AMESim is used as the lubricating oil source.

[0249] The input parameters of the lubricating oil in this invention are as shown in Table 4 below:

[0250] Table 4

[0251] parameter numerical value unit temperature 100 ℃ pressure 10 BarA flow rate 0.04 kg / s

[0252] ③ Pipeline system

[0253] The function of the pipeline system is to transport the lubricating oil from the oil tank to the bearing cavity and then flow out from the bearing cavity to the cooler.

[0254] The TFL001 - 1 model in the Thermal hydraulic Resistance library of AMESim is used as the pipeline.

[0255] ④ Calculation of bearing heat generation

[0256] The bearing heat generation is calculated using the bearing heat generation calculation model compiled in part (two) of AMESim.

[0257] ⑤ Referencing of lubricating oil physical property parameters

[0258] The reference temperature and reference pressure of the lubricating oil are defined using TFPTS - 1 in the Thermal hydraulic library of AMESim.

[0259] The density, thermal conductivity, kinematic viscosity, and specific heat capacity of the lubricating oil are referenced using the TFPRO model in the Thermal hydraulic library of AMESim.

[0260] ⑥ Combined simulation module

[0261] The DYNCOSIMNETWORK01 - 1 model in the Generic cosimulation library of AMESim is used to complete the modeling work of the combined simulation thermal analysis of the bearing cavity.

[0262] The co-simulation parameters of the one-dimensional system DYNCOSIMNETWORK01-1 model are set as shown in Table 5:

[0263] Table 5

[0264] parameter value mode server server port 60000 sample time 0.1s

[0265] The input and output node conditions are shown in Table 6:

[0266] Table 6

[0267] node corresponding parameter input / output 1 Out_T input 2 In1_m output 3 In2_m output 4 In1_T output 5 In2_T output 6 q output 7 N1 output 8 N2 output

[0268] In this embodiment, (4) 3D bearing component simulation modeling

[0269] ① Establish a physical model

[0270] down Figure 5 , which is a 3D internal fluid model of the bearing cavity simplified from the aero-engine bearing cavity selected for the research of the present invention.

[0271] Among them, the lubricating oil inlet is a direct injection inlet, and its distribution position is symmetrically distributed left and right. The axial position forms an angle of 30° with the axis of the rotation direction, and the outlet is located in the middle of the axis below the bearing cavity.

[0272] ② Mesh generation

[0273] Use the starccm+ software to process the mesh of the simplified bearing cavity model.

[0274] The mesh model is selected as: surface reconstruction - automatic surface repair - polyhedral mesh. The important parameters are set as shown in Table 7:

[0275] Table 7

[0276] parameter value basic dimension 1mm target surface dimension 50％ minimum surface dimension 10％ surface mesh growth rate 1.3 volume growth rate 1.2 maximum tetrahedron dimension 100％

[0277] The generated mesh conditions are as follows Figure 6 , Figure 7 as shown:

[0278] ③ Computational domain model setting

[0279] For the fluid domain, the model is selected as: 3D - multiphase - multiphase interaction - volume of fluid (VOF) - separated flow - gradient - implicit unsteady - turbulence - Reynolds Navier - Stokes - k - Epsilon turbulence - realizable k - Epsilon two - layer model - wall distance - two - layer full y+ wall treatment - separated multiphase temperature - solution scheme interpolation - gravity - co - simulation - simcenter amesim.

[0280] The multiphase Eulerian phase fluid model is set as follows:

[0281] Phase 1: High-temperature gas

[0282] The ideal gas law is used to calculate the high-temperature gas.

[0283] Phase 2: Lubricating oil

[0284] 4050 aviation lubricating oil is used to cool the bearings.

[0285] ④ The boundary conditions are set as shown in Table 8,

[0286] Table 8

[0287] parameter value Inlet1 velocity inlet Inlet2 velocity inlet Outlet outlet S2 total heat source

[0288] ⑤ The solver parameters are set as shown in Table 9,

[0289] Table 9

[0290] parameter value time step 0.1s time discretization second order

[0291] ⑥ The stop criterion parameters are set as shown in Table 10,

[0292] Table 10

[0293] parameter value maximum internal iteration 5 times maximum internal time 15s

[0294] ⑦ link connection settings

[0295] The external link parameters for connecting to Amesim are set as Table 11:

[0296] Table 11

[0297]

[0298] (V) Simulation run

[0299] The steps for the simulation run are as follows:

[0300] ① Start the Amesim simulation;

[0301] ② Click Connect in the link of StarCCM+;

[0302] ③ Start the StarCCM+ simulation.

[0303] The technical solution of the present invention,

[0304] ①Custom-compiled heat generation calculation model: This method adopts a custom-compiled heat generation calculation model to simulate the heat generation behavior of the bearing and its surrounding structures with higher precision. By customizing the modeling of the heat generation characteristics under different working conditions, this method can accurately match the cooling requirements for various working conditions and achieve the dynamic matching of the heat source and the heat dissipation path. At the same time, based on the custom-compiled calculation method, the details of heat transfer during the lubricating oil cooling process can be optimized, effectively improving the overall heat dissipation performance of the cooling system and the reliability of the design, so as to better meet the application requirements under high-temperature and extreme working conditions.

[0305] ②Design efficiency improvement based on one-dimensional and three-dimensional combined simulation: This method adopts the design idea of combining one-dimensional fluid network simulation and three-dimensional thermal structure coupling simulation to optimize the lubricating oil circulation path from multiple dimensions. Through one-dimensional simulation for the rapid analysis of the overall flow field, and then combined with three-dimensional simulation to accurately simulate the temperature distribution in the bearing area and its complex heat load characteristics, the optimization of the lubricating oil flow path and the improvement of the heat transfer performance are achieved. This method can greatly improve the design efficiency while maintaining a high design accuracy, providing effective support for the development and iteration of the cooling system.

[0306] It should be noted that the method of the embodiments of the present disclosure can be executed by a single device, such as a computer or a server. The method of this embodiment can also be applied to a distributed scenario and completed by multiple devices cooperating with each other. In such a distributed scenario, one of the multiple devices can only execute one or more steps of the method of the embodiments of the present disclosure, and these multiple devices will interact with each other to complete the described method.

[0307] It should be noted that some embodiments of the present disclosure have been described above. Other embodiments are within the scope of the appended claims. In some cases, it should be understood that the magnitudes of the sequence numbers of the steps in the above embodiments do not mean the order of execution. The execution order of each process should be determined by its function and internal logic, and should not constitute any limitation to the implementation process of the embodiments of the present invention. The actions or steps recited in the claims can be executed in a different order from that in the above embodiments and still achieve the desired results. Additionally, the processes depicted in the drawings do not necessarily require the specific order or continuous order shown to achieve the desired results. In certain embodiments, multitasking and parallel processing are also possible or may be advantageous.

[0308] Embodiment 2

[0309] Based on the same inventive concept, corresponding to the methods of any of the above embodiments, the present invention also provides a lubricating oil circulation system design system for bearing heat dissipation, which is used to implement any of the above-mentioned methods, including an analysis module, a compilation module, a one-dimensional model construction module, a three-dimensional model construction module, and a simulation module;

[0310] The analysis module is used to conduct a theoretical analysis of the heat generation of the bearing to obtain the calculation process of bearing heat generation;

[0311] The compilation module is used to compile the bearing heat generation calculation sub-model in AMESim using the submodeleditor according to the bearing heat generation calculation process to obtain the heat input data for simulation;

[0312] The one-dimensional model construction module is used to establish a one-dimensional lubricating oil circulation system simulation model in AMESim to obtain the input, output, dynamic behavior, and interaction parameters at the system level;

[0313] The three-dimensional model construction module is used to construct a three-dimensional bearing component simulation model in STAR-CCM+ to obtain the inlet and outlet conditions, operating conditions parameters, and interaction parameters;

[0314] The simulation module is used to run the simulation according to the heat input data, the input, output, dynamic behavior, and interaction parameters at the system level, the inlet and outlet conditions, the operating conditions parameters, and the interaction parameters.

[0315] In this embodiment, the calculation process of bearing heat generation includes:

[0316] Q bfr = CZρL 2 u 3 β′,

[0317] where C1 is the bearing friction coefficient, Z is the number of rollers, ρ is the density of the lubricating oil used, L is the effective length of the rollers, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of the radial clearance on the power loss, C2 is the bearing hydrodynamic resistance coefficient, and C = C1 + C2 is the total bearing friction coefficient.

[0318] In this embodiment, the bearing heat generation calculation sub-model includes: structural parameters P, input parameters V0, output parameters V1, and internal parameters V2;

[0319] Among them, the structural parameters P include: the pitch diameter D of the short cylindrical roller bearing m , the diameter D of the rollers r , the effective length L of the short cylindrical rollers, the number Z of the short cylindrical rollers, and the radial clearance h matched by the bearing;

[0320] The input parameters V0 include: the bearing speed Rs, the radial load F of the bearing r, the kinematic viscosity nu of the lubricating oil, the density rho, the thermal conductivity k, and the specific heat capacity Cp with the selected reference temperature being the outlet temperature of the lubricating oil;

[0321] The output parameter V1 includes: the total heat generation power Q of the bearing friction;

[0322] The internal parameter V2 includes: the circumferential speed v of the bearing cage, the Prandtl number Pr of the lubricating oil, the Reynolds number Re, the centrifugal force Fc of the roller, the average load Fcp on the roller bus, the Euler coefficient Eu, the total resistance coefficient f, and the loss influence coefficient beta.

[0323] In this embodiment, in the one-dimensional lubricating oil circulation system simulation model, the physical properties of the lubricating oil are defined using TFFD04-1 in the Thermal hydraulic library of AMESim, the TFMPT0-2 model in the Thermal hydraulic library of AMESim is used as the lubricating oil source, the TFL001-1 model in the Thermal hydraulic Resistance library of AMESim is used as the pipeline, the bearing heat generation calculation sub-model compiled in AMESim is used to calculate the bearing heat generation, the reference temperature and reference pressure of the lubricating oil are defined using TFPTS-1 in the Thermal hydraulic library of AMESim, the density, thermal conductivity, kinematic viscosity, and specific heat capacity of the lubricating oil are referenced using the TFPRO model in the Thermal hydraulic library of AMESim, and the DYNCOSIMNETWORK01-1 model in the Generic cosimulation library of AMESim is used to complete the modeling work of the combined simulation thermal analysis of the bearing cavity.

[0324] In this embodiment, the three-dimensional bearing component simulation model includes:

[0325] Establish a three-dimensional model of the internal fluid in the bearing cavity; perform mesh division on the three-dimensional model of the internal fluid in the bearing cavity to generate a three-dimensional model mesh; set the computational domain model; set the boundary conditions; set the solver parameters; set the stopping criterion parameters; set the link connection.

[0326] The system of the above embodiment is used to implement the corresponding lubricating oil circulation system design method for bearing heat dissipation in any of the foregoing embodiments, and has the beneficial effects of the corresponding method embodiments, which will not be elaborated here.

[0327] It should be noted that the above lubricating oil circulation system design system for bearing heat dissipation is embodied in the form of functional units. The term "module" here can be implemented in the form of software and / or hardware, and no specific limitation is made in this regard.

[0328] For example, a "module" may be a software program, a hardware circuit, or a combination of both that implements the above functions. The hardware circuit may include an application specific integrated circuit (ASIC), an electronic circuit, a processor (such as a shared processor, a proprietary processor, or a group of processors, etc.) for executing one or more software or firmware programs, and a memory, a merged logic circuit, and / or other suitable components that support the described functions.

[0329] Embodiments of the present disclosure are intended to cover all such substitutions, modifications, and variations that fall within the broad scope of the appended claims. Therefore, any omissions, modifications, equivalent substitutions, improvements, etc. made within the spirit and principle of the embodiments of the present disclosure shall be included within the protection scope of the present disclosure.

Claims

1. A design method for a lubricating oil circulation system for bearing heat dissipation, characterized in that, The method includes: Conduct a theoretical analysis of the bearing heat generation to obtain the bearing heat generation calculation process; According to the bearing heat generation calculation process, use the submodel editor in AMESim to compile the bearing heat generation calculation submodel to obtain the simulated heat input data; Establish a one-dimensional lubricating oil circulation system simulation model in AMESim to obtain the system-level input, output, dynamic behavior, and interaction parameters; Construct a three-dimensional bearing component simulation model in STAR-CCM+ to obtain the inlet and outlet conditions, operating conditions parameters, and interaction parameters; Run the simulation according to the heat input data, the system-level input, output, dynamic behavior, and interaction parameters, the inlet and outlet conditions, the operating conditions parameters, and the interaction parameters; In the one-dimensional lubricating oil circulation system simulation model, use TFFD04-1 in the Thermal hydraulic library in AMESim to define the physical properties parameters of the lubricating oil, use the TFMPT0-2 model in the Thermal hydraulic library in AMESim as the lubricating oil source, use the TFL001-1 model in the Thermal hydraulic Resistance library in AMESim as the pipeline, use the compiled bearing heat generation calculation submodel in AMESim to calculate the bearing heat generation, use TFPTS-1 in the Thermal hydraulic library in AMESim to define the reference temperature and reference pressure of the lubricating oil, use the TFPRO model in the Thermal hydraulic library in AMESim to reference the density, thermal conductivity, kinematic viscosity, and specific heat capacity of the lubricating oil, and use the DYNCOSIMNETWORK01-1 model in the Generic cosimulation library in AMESim to complete the modeling work of the combined simulation thermal analysis of the bearing cavity; The three-dimensional bearing component simulation model includes: Establish a three-dimensional model of the fluid inside the bearing cavity; perform mesh division on the three-dimensional model of the fluid inside the bearing cavity to generate the three-dimensional model mesh; set the computational domain model; set the boundary conditions; set the solver parameters; set the stopping criterion parameters; set the link connection.

2. The method according to claim 1, wherein The bearing heat generation calculation process includes: ， Among them, is the bearing friction coefficient, is the number of rollers, is the density of the lubricating oil used, is the effective length of the roller, is the circumferential speed of the bearing cage, is the influence coefficient of radial clearance on power loss, is the bearing hydrodynamic resistance coefficient, is the total bearing friction coefficient.

3. The method according to claim 1, characterized in that, The bearing heat generation calculation submodel includes: structural parameter P, input parameter V0, output parameter V1, and internal parameter V2; Among them, the structural parameter P includes: the pitch diameter of the short cylindrical roller bearing , the diameter of the roller , the effective length of the short cylindrical roller , the number of short cylindrical rollers , the radial clearance matched by the bearing ; The input parameter V0 includes: the bearing rotational speed Rs, the radial load of the bearing , the kinematic viscosity nu of the lubricating oil, the density rho, the thermal conductivity k, and the specific heat capacity Cp with the selected reference temperature being the lubricating oil outlet temperature; The output parameter V1 includes: the total bearing friction heat generation power Q; The internal parameter V2 includes: the circumferential speed v of the bearing cage, the Prandtl number Pr of the lubricating oil, the Reynolds number Re, the centrifugal force Fc of the roller, the average load Fcp on the roller bus, the Euler coefficient Eu, the total resistance coefficient f, and the loss influence coefficient beta.

4. A lubricating oil circulation system design system for bearing heat dissipation, the system being used to implement the method described in any one of claims 1-3, characterized in that, The system includes: an analysis module, a compilation module, a one-dimensional model construction module, a three-dimensional model construction module, and a simulation module; The analysis module is used to conduct a theoretical analysis of the bearing heat generation to obtain the bearing heat generation calculation process; The compilation module is used to compile the bearing heat generation calculation submodel in AMESim according to the bearing heat generation calculation process to obtain the simulated heat input data; The one-dimensional model building module is used to establish a one-dimensional lubricating oil circulation system simulation model in AMESim to obtain system-level inputs, outputs, dynamic behaviors, and interaction parameters; The three-dimensional model building module is used to establish a three-dimensional bearing component simulation model in STAR-CCM+ to obtain inlet and outlet conditions, operating conditions parameters, and interaction parameters; The simulation module is used to run simulations based on heat input data, system-level inputs, outputs, dynamic behaviors, and interaction parameters, inlet and outlet conditions, operating conditions parameters, and interaction parameters; In the one-dimensional lubricating oil circulation system simulation model, the TFFD04-1 in the Thermal hydraulic library of AMESim is used to define the physical properties of the lubricating oil, the TFMPT0-2 model in the Thermal hydraulic library of AMESim is used as the lubricating oil source, the TFL001-1 model in the Thermal hydraulic Resistance library of AMESim is used as the pipeline, the bearing heat generation calculation sub-model compiled in AMESim is used to calculate the bearing heat generation, the TFPTS-1 in the Thermal hydraulic library of AMESim is used to define the reference temperature and reference pressure of the lubricating oil, the TFPRO model in the Thermalhydraulic library of AMESim is used to reference the density, thermal conductivity, kinematic viscosity, and specific heat capacity of the lubricating oil, and the DYNCOSIMNETWORK01-1 model in the Generic cosimulation library of AMESim is used to complete the modeling work of the combined simulation thermal analysis of the bearing cavity; The three-dimensional bearing component simulation model includes: Establish a three-dimensional model of the fluid inside the bearing cavity; perform mesh division on the three-dimensional model of the fluid inside the bearing cavity to generate a three-dimensional model mesh; set the computational domain model; set boundary conditions; set solver parameters; set stop criterion parameters; set link connections.

5. The system according to claim 4, characterized in that, The bearing heat generation calculation process includes: ， Among them, is the bearing friction coefficient, is the number of rollers, is the density of the lubricating oil used, is the effective length of the roller, is the circumferential speed of the bearing cage, is the influence coefficient of radial clearance on power loss, is the bearing hydrodynamic resistance coefficient, is the total bearing friction coefficient.

6. The system according to claim 4, wherein The bearing heat generation calculation sub-model includes: structural parameter P, input parameter V0, output parameter V1, and internal parameter V2; Among them, the structural parameter P includes: the pitch diameter of the short cylindrical roller bearing , the diameter of the roller , the effective length of the short cylindrical roller , the number of short cylindrical rollers , the radial clearance matched by the bearing ; The input parameter V0 includes: the rotational speed Rs of the bearing, and the radial load of the bearing , the kinematic viscosity nu of the lubricating oil, the density rho, the thermal conductivity k, and the specific heat capacity Cp with the selected reference temperature being the outlet temperature of the lubricating oil; The output parameter V1 includes: the total bearing friction heat generation power Q; The internal parameter V2 includes: the circumferential speed v of the bearing cage, the Prandtl number Pr of the lubricating oil, the Reynolds number Re, the centrifugal force Fc of the roller, the average load Fcp on the roller bus, the Euler coefficient Eu, the total resistance coefficient f, and the loss influence coefficient beta.

Images