Lubricating oil circulation system design method and system for bearing heat dissipation

Abstract

The invention belongs to the technical field of aircraft lubricating oil heat management, and discloses a lubricating oil circulation system design method and system for bearing heat dissipation, and the method comprises the steps: carrying out the theoretical analysis of bearing heat production, and obtaining a bearing heat production calculation process; according to the bearing heat production calculation process, a submodel editor is used in AMESim to compile a bearing heat production calculation sub-model, and simulated heat input data is obtained; a one-dimensional lubricating oil circulation system simulation model is established in AMESim, and system-level input, output, dynamic behaviors and interaction parameters are obtained; a three-dimensional bearing part simulation model is constructed in STAR-CCM +, and inlet and outlet conditions, working condition parameters and interaction parameters are obtained; and running simulation. According to the invention, the heat dissipation performance of lubricating oil can be improved, the operation temperature of the bearing is effectively reduced, the stability and reliability of a system can be improved, and an advanced cooling scheme is provided for a new generation of high-performance aircrafts and engines.

Description

Technical Field

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

[0002] In modern aircraft 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 of mechanical equipment, the operating challenges of bearings in high-temperature and high-pressure environments have become increasingly prominent, and the existing lubricating oil cooling design methods have gradually revealed their limitations in meeting the heat dissipation requirements of the new generation of high-performance equipment.

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

[0004] In order 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, with the goal of improving 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 improved, providing an advanced cooling solution for a 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, the method comprising:

[0006] Conduct theoretical analysis on bearing heat generation and obtain the bearing heat generation calculation process;

[0007] According to the bearing heat generation calculation process, the bearing heat generation calculation submodel is compiled using the submodel editor in AMESim to obtain the simulated heat input data;

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

[0009] Build a 3D bearing component simulation model in STAR-CCM+ to obtain inlet and outlet conditions, operating parameters, and interaction parameters;

[0010] Run simulations based on heat input data, system-level inputs, outputs, dynamic behavior and interaction parameters, inlet and outlet conditions, operating parameters and interaction parameters.

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

[0012] Q bfr =CZρL 2 u 3 β′,

[0013] Among them, 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 roller, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of radial clearance on power loss, C2 is the bearing fluid dynamic 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] Among them, the structural parameters P include: the pitch circle diameter D of the short cylindrical roller bearing m , roller diameter D r , the effective length L of the short cylindrical roller, the number Z of the short cylindrical rollers, and the radial clearance h matched by the bearing;

[0016] Input parameters V0 include: bearing speed Rs, bearing radial load F r , the kinematic viscosity nu, density rho, thermal conductivity k of the lubricating oil, and the specific heat capacity Cp when the qualitative temperature is selected as the lubricating oil outlet temperature;

[0017] Output parameters V1 include: total bearing friction heat generation power Q;

[0018] The internal parameters V2 include: 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 generatrix, 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, TFFD04-1 in the Thermal hydraulic library in AMESim is used to define the physical properties of the lubricating oil, the TFMPT0-2 model in the Thermal hydraulic library in AMESim is used as the lubricating oil source, the TFL001-1 model in the Thermal hydraulic Resistance library in AMESim is used as the pipeline, the bearing heat generation calculation sub-model compiled in AMESim is used to calculate the bearing heat generation, TFPTS-1 in the Thermalhydraulic library in AMESim is used to define the reference temperature and reference pressure of the lubricating oil, the TFPRO model in the Thermal hydraulic library in 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 in AMESim is used to complete the modeling work of the bearing cavity joint simulation thermal analysis.

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

[0021] Establish a three-dimensional model of the fluid inside the bearing cavity; mesh the three-dimensional model of the fluid inside the bearing cavity to generate a three-dimensional model mesh; set the calculation domain model; set boundary conditions; set solver parameters; set stop criterion parameters; set link connections.

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

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

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

[0025] 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 input, output, dynamic behavior and interaction parameters;

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

[0027] The simulation module is used to run simulation based on heat input data, system-level input, output, dynamic behavior and interaction parameters, inlet and outlet conditions, operating parameters and interaction parameters.

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

[0029] Q bfr =CZρL 2 u 3 β′,

[0030] Among them, 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 roller, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of radial clearance on power loss, C2 is the bearing fluid dynamic 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] Among them, the structural parameters P include: the pitch circle diameter D of the short cylindrical roller bearing m , roller diameter D r , the effective length L of the short cylindrical roller, the number Z of the short cylindrical rollers, and the radial clearance h matched by the bearing;

[0033] Input parameters V0 include: bearing speed Rs, bearing radial load F r , the kinematic viscosity nu, density rho, thermal conductivity k of the lubricating oil, and the specific heat capacity Cp when the qualitative temperature is selected as the lubricating oil outlet temperature;

[0034] Output parameters V1 include: total bearing friction heat generation power Q;

[0035] The internal parameters V2 include: 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 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, TFFD04-1 in the Thermal hydraulic library in AMESim is used to define the physical properties of the lubricating oil, the TFMPT0-2 model in the Thermal hydraulic library in AMESim is used as the lubricating oil source, the TFL001-1 model in the Thermal hydraulic Resistance library in AMESim is used as the pipeline, the bearing heat generation calculation sub-model compiled in AMESim is used to calculate the bearing heat generation, TFPTS-1 in the Thermalhydraulic library in AMESim is used to define the reference temperature and reference pressure of the lubricating oil, the TFPRO model in the Thermal hydraulic library in 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 in AMESim is used to complete the modeling work of the bearing cavity joint simulation thermal analysis.

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

[0038] Establish a three-dimensional model of the fluid inside the bearing cavity; mesh the three-dimensional model of the fluid inside the bearing cavity to generate a three-dimensional model mesh; set the calculation domain model; set boundary conditions; set solver parameters; set stop criterion parameters; set link connections.

[0039] Compared with the prior art, the present invention has the following beneficial effects:

[0040] The present invention aims to provide a design method and system for a lubricating oil circulation system for bearing heat dissipation, which effectively controls the temperature rise of the bearing under extreme operating conditions through innovative design means, thereby improving the working reliability and life of the bearing assembly. This method optimizes the flow path and heat transfer efficiency of the lubricating oil through sophisticated thermal management technology to reduce the thermal load of the system and improve the cooling effect, thereby improving the thermal management level of the overall system. By using advanced computational simulation methods, this method not only achieves a compact structural design of the cooling system, but also reduces the system power consumption and mass by rationally configuring the fluid circulation scheme. In addition, while meeting the high-efficiency requirements of aircraft engines, the design provides greater flexibility to adapt to the bearing cooling requirements under complex working conditions. BRIEF DESCRIPTION OF THE DRAWINGS

[0041] In order to more clearly illustrate the technical solution of the present invention, the following briefly introduces the drawings required for use in the embodiments. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative labor.

[0042] Figure 1 A schematic flow chart of a method for designing a lubricating oil circulation system for bearing heat dissipation according to an embodiment of the present invention;

[0043] Figure 2 A schematic diagram of the relationship between the parameters of the AMESim software compiled model according to an embodiment of the present invention;

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

[0045] Figure 4 A schematic diagram of an AMESim one-dimensional system simulation model for thermal analysis of a bearing cavity according to an embodiment of the present invention;

[0046] Figure 5 A simplified schematic diagram of a three-dimensional model of fluid inside a bearing cavity according to an embodiment of the present invention;

[0047] Figure 6 A schematic diagram of a three-dimensional model grid according to an embodiment of the present invention;

[0048] Figure 7 This is a schematic diagram of the grid situation of the +X direction cross section of the inlet pipeline of an embodiment of the present invention. DETAILED DESCRIPTION

[0049] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within 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 be understood by people with ordinary skills in the field to which the present disclosure belongs. The "first", "second" and similar words used in the embodiments of the present disclosure do not indicate any order, quantity or importance, but are only used to distinguish different components. "Including" or "comprising" and similar words 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. "Connect" or "connected" and similar words are not limited to physical or mechanical connections, but can include electrical connections, whether direct or indirect. "Up", "down", "left", "right" and the like are only used to indicate relative positional relationships. When the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0051] In order to make the above-mentioned objects, features and advantages of the present invention more obvious and easy to understand, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0052] Embodiment 1

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

[0054] (I) Theoretical analysis of bearing heat generation: Complete the theoretical analysis of bearing heat generation and obtain the calculation process of bearing heat generation;

[0055] (ii) Compilation of bearing heat generation model: Based on the theoretical analysis and calculation process of bearing heat generation, the submodel editor is used in the AMESim software to compile the bearing heat generation calculation submodel to provide heat input data for subsequent simulations;

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

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

[0058] (V) Run the simulation.

[0059] In this embodiment, (a) theoretical analysis of bearing heat generation

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

[0061] ① When the roller revolves around the center of the bearing 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 keeps revolving, it will rotate correspondingly inside the cage pocket, and the sliding friction heat will be generated when the roller rotates;

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

[0064] ④ Sliding friction heat is generated between the bottom of the bearing cage and the guide surface of the inner ring.

[0065] In addition to the friction heat of the bearing, when the bearing works normally under lubrication conditions, fluid dynamic resistance loss will be generated. The fluid dynamic resistance loss is specifically composed of the following four parts:

[0066] ① At the entrance of the roller and raceway contact area, the roller rotates and revolves, and the lubricating oil pumping and shear force produce fluid resistance loss;

[0067] ② At the entrance of the contact area between the rolling element and the cage pocket, the liquid pumping and shear force produce fluid resistance loss;

[0068] ③ Losses caused by the viscous shear force of the fluid between the inner and outer cylindrical surfaces of the cage and the inner and outer ring guide surfaces;

[0069] ④ At the interface between the roller and the gas-liquid two-phase fluid inside the bearing cavity, there is fluid resistance loss.

[0070] The calculation formula of frictional heating power is:

[0071] Q f =C1ZρL 2 u 3 β′ (1)

[0072] The calculation formula for fluid resistance loss is:

[0073] Q l =C2ZρL 2 u 3 β′ (2)

[0074] Therefore, the calculation formula for the total heat generation power of the bearing friction 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 roller, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of radial clearance on power loss, C2 is the bearing fluid dynamic resistance coefficient, and C=C1+C2 is the total bearing friction coefficient.

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

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

[0079]

[0080] Where: D m (Unit: m) Pitch diameter of short cylindrical roller bearing, D b (Unit: m) is the roller diameter, and n (Unit: r / min) is the bearing speed.

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

[0082] Pr=Cn ρ v / k (5)

[0083] ③Calculate the Reynolds coefficient Re:

[0084]

[0085] Where Re is the Reynolds number of the oil flow calculated with the peripheral 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) is the effective length of the short cylindrical roller, 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, C p The specific heat capacity when the qualitative temperature is selected as the lubricating oil outlet temperature.

[0086] ④Calculate 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] ⑤Calculate the average load F acting on the roller generatrix 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, the number of short cylindrical rollers.

[0091] ⑥Calculate the Euler coefficient Eu:

[0092] Eu=10F cp / ρ(uL) 2 (9)

[0093] ⑦Calculate 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] ⑧The radial clearance of the bearing will have a certain impact on the heat generation power. In the calculation of the heat generation power, it is necessary to add a multiplication coefficient for correction. The loss influence coefficient is expressed as β, and the calculation formula is:

[0096] β=1+1.7(0.1-h) (11)

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

[0098] In this embodiment, (ii) bearing heat generation model compilation

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

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

[0101] ②V0: input parameters, i.e. parameters that the model needs to input or introduce;

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

[0103] ④V2: internal parameters, i.e. the parameters calculated within the model.

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

[0105] In the present invention, each data is respectively:

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

[0107] ②V0: 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) and the specific heat capacity when the qualitative temperature is selected as the lubricating oil outlet temperature.

[0108] ③V1: Q (unit: W) total heat generation power of bearing friction.

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

[0110] To compile a submodel, follow these steps:

[0111] ①Draw the icon

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

[0113] Click OK to exit editing.

[0114] ②Parameter setting

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

[0116] Table 1 Ports parameter setting table

[0117]

[0118] Table 2 Internal variables parameter setting table

[0119]

[0120] Table 3 Real parameters parameter setting table

[0121]

[0122]

[0123] ③Model encoding

[0124] Click generate submodel code and open submodel code in sequence to open the coding 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 5real parameters:

[0139] Dm Bearing pitch circlediameter[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 1variable:

[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 1variable:

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

[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 compile current submodel.

[0238] ④Complete compilation

[0239] Click 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 AMESim one-dimensional system simulation model for thermal analysis of bearing cavity is used to provide and receive key data for three-dimensional heat transfer simulation analysis of bearing cavity.

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

[0243] The model includes the following key parts:

[0244] ① Definition of Lubricating Oil

[0245] The physical property parameters of lubricating oil are defined by using TFFD04-1 in the Thermal hydraulic library in AMESim, which is convenient for subsequent simulation calls. The present invention uses 4050 lubricating oil as the coolant for engine lubrication and cooling.

[0246] ②Lubricating oil source

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

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

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

[0250] Table 4

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

[0252] ③ Pipeline system

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

[0254] Use the TFL001-1 model from the Thermal Hydraulic Resistance library in AMESim as the pipeline.

[0255] ④ Calculation of bearing heat generation

[0256] The bearing heat generation calculation model compiled in Part (II) of AMESim is used to calculate the bearing heat generation.

[0257] ⑤ Reference 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 in 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 in AMESim.

[0260] ⑥Joint simulation module

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

[0262] The joint 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 parameters Input / Output 1 Out_T enter 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, (four) three-dimensional bearing component simulation modeling

[0269] ①Build a physical model

[0270] Down Figure 5 , which is a three-dimensional model of the internal fluid of the bearing cavity that is simplified from the aircraft engine bearing cavity selected for research according to the present invention.

[0271] Among them, the lubricating oil inlet is a direct injection type oil inlet, the distribution position is symmetrical on the left and right, the axial position is 30° with the axis of the rotation direction, and the oil outlet is located in the middle of the axis below the bearing cavity.

[0272] ② Grid division

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

[0274] The mesh model selected is: Surface reconstruction - Automatic surface repair - Polyhedron mesh, and the important parameter settings are as shown in Table 7:

[0275] Table 7

[0276] parameter value Basic size 1mm Target surface size 50％ Minimum surface size 10％ Surface mesh growth rate 1.3 Volume growth rate 1.2 Maximum tetrahedron size 100％

[0277] The generated mesh is as follows Figure 6 , Figure 7 As shown:

[0278] ③ Computational domain model settings

[0279] For the fluid domain, the model choices are: 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 Euler phase fluid model is set up as follows:

[0281] Phase 1: High temperature gas

[0282] Calculations for high temperature gases are performed using the ideal gas equation of state.

[0283] Phase 2: Lubricating oil

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

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

[0286] Table 8

[0287] parameter value Inlet1 Speed ​​​​entry Inlet2 Speed ​​​​entry Outlet exit S2 Total heat source

[0288] ⑤ The solver parameter settings are shown in Table 9.

[0289] Table 9

[0290] parameter value Time step 0.1s Time Discrete Second order

[0291] ⑥ The stop criterion parameter settings are shown in Table 10.

[0292] Table 10

[0293] parameter value Maximum internal iterations 5 times Maximum internal time 15s

[0294] ⑦Link connection settings

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

[0296] Table 11

[0297]

[0298] (V) Simulation operation

[0299] The steps for running the simulation are:

[0300] ①Open amesim simulation;

[0301] ②Click the link in starccm+;

[0302] ③Open starccm+ simulation.

[0303] The technical solution of the present invention,

[0304] ① Custom compiled heat generation calculation model: This method uses a custom compiled heat generation calculation model to simulate the heating behavior of bearings and their surrounding structures with higher accuracy. By custom modeling the heat generation characteristics under different working conditions, this method can accurately match the cooling requirements for various working conditions and achieve dynamic matching of heat sources and heat dissipation paths. At the same time, the calculation method based on custom compilation can optimize the heat transfer details during the oil cooling process, effectively improving the overall heat dissipation performance and design reliability of the cooling system, thereby better meeting the application requirements under high temperature and extreme working conditions.

[0305] ② Improve design efficiency based on one-dimensional and three-dimensional joint simulation design: This method adopts a design concept that combines one-dimensional fluid network simulation with three-dimensional thermal structure coupling simulation to optimize the oil circulation path from multiple dimensions. Through one-dimensional simulation, the overall flow field is quickly analyzed, and then combined with three-dimensional simulation to accurately simulate the temperature distribution and complex thermal load characteristics of the bearing area, the oil flow path is optimized and the heat transfer performance is improved. 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 embodiment of the present disclosure can be performed by a single device, such as a computer or a server. The method of the present embodiment can also be applied in a distributed scenario and completed by multiple devices cooperating with each other. In the case of such a distributed scenario, one of the multiple devices can only perform one or more steps in the method of the embodiment of the present disclosure, and the multiple devices will interact with each other to complete the described method.

[0307] It should be noted that some embodiments of the present disclosure are described above. Other embodiments are within the scope of the attached claims. In some cases, it should be understood that the size of the serial number of each step in the above embodiment does not mean the order of execution, and the execution order of each process should be determined by its function and internal logic, and should not constitute any limitation on the implementation process of the embodiment of the present invention. The actions or steps recorded in the claims can be performed in an order different from that in the above embodiment and still achieve the desired results. In addition, the process depicted in the accompanying drawings does not necessarily require the specific order or continuous order shown to achieve the desired results. In some embodiments, multitasking and parallel processing are also possible or may be advantageous.

[0308] Embodiment 2

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

[0310] The analysis module is used to perform theoretical analysis on the heat generation of the bearing and obtain the calculation process of the heat generation of the bearing;

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

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

[0313] The 3D model building module is used to build a 3D bearing component simulation model in STAR-CCM+ to obtain the inlet and outlet conditions, operating parameters, and interaction parameters;

[0314] 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 parameters and interaction parameters.

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

[0316] Q bfr =CZρL 2 u 3 β′,

[0317] Among them, 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 roller, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of radial clearance on power loss, C2 is the bearing fluid dynamic 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 circle diameter D of the short cylindrical roller bearing m , roller diameter D r , the effective length L of the short cylindrical roller, the number Z of the short cylindrical rollers, and the radial clearance h matched by the bearing;

[0320] Input parameters V0 include: bearing speed Rs, bearing radial load F r, the kinematic viscosity nu, density rho, thermal conductivity k of the lubricating oil, and the specific heat capacity Cp when the qualitative temperature is selected as the lubricating oil outlet temperature;

[0321] Output parameters V1 include: total bearing friction heat generation power Q;

[0322] The internal parameters V2 include: 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 generatrix, 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, TFFD04-1 in the Thermal hydraulic library in AMESim is used to define the physical properties of the lubricating oil, the TFMPT0-2 model in the Thermal hydraulic library in AMESim is used as the lubricating oil source, the TFL001-1 model in the Thermal hydraulic Resistance library in AMESim is used as the pipeline, the bearing heat generation calculation sub-model compiled in AMESim is used to calculate the bearing heat generation, TFPTS-1 in the Thermal hydraulic library in AMESim is used to define the reference temperature and reference pressure of the lubricating oil, the TFPRO model in the Thermal hydraulic library in 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 in AMESim is used to complete the modeling work of the bearing cavity joint simulation thermal analysis.

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

[0325] Establish a three-dimensional model of the fluid inside the bearing cavity; mesh the three-dimensional model of the fluid inside the bearing cavity to generate a three-dimensional model mesh; set the calculation domain model; set boundary conditions; set solver parameters; set stop criterion parameters; set link connections.

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

[0327] It should be noted that the above-mentioned 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 is not specifically limited to this.

[0328] For example, a "module" may be a software program, a hardware circuit, or a combination of the two 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 dedicated processor, or a group processor, etc.) and a memory for executing one or more software or firmware programs, a combined logic circuit, and / or other suitable components that support the described functions.

[0329] The 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 principles of the embodiments of the present disclosure should be included in the scope of protection of the present disclosure.

Claims

1. A design method for a lubricating oil circulation system for bearing heat dissipation, characterized in that: The method comprises: Conduct theoretical analysis on bearing heat generation and obtain the bearing heat generation calculation process; According to the bearing heat generation calculation process, the bearing heat generation calculation sub-model is compiled using submodeleditor in AMESim to obtain the simulated heat input data; A one-dimensional lubricating oil circulation system simulation model was established in AMESim to obtain the input, output, dynamic behavior and interaction parameters at the system level; Build a 3D bearing component simulation model in STAR-CCM+ to obtain inlet and outlet conditions, operating parameters, and interaction parameters; Run simulations based on heat input data, system-level inputs, outputs, dynamic behavior and interaction parameters, inlet and outlet conditions, operating parameters and interaction parameters.

2. The method according to claim 1, characterized in that The bearing heat generation calculation process includes: Q bfr =CZρL 2 you 3 b′, Among them, 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 roller, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of radial clearance on power loss, C2 is the bearing fluid dynamic resistance coefficient, and C=C1+C2 is the total bearing friction coefficient.

3. The method according to claim 1, characterized in that 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 parameters P include: the pitch circle diameter D of the short cylindrical roller bearing m , roller diameter D r , the effective length L of the short cylindrical roller, the number Z of the short cylindrical rollers, and the radial clearance h matched by the bearing; Input parameters V0 include: bearing speed Rs, bearing radial load F r , the kinematic viscosity nu, density rho, thermal conductivity k of the lubricating oil, and the specific heat capacity Cp when the qualitative temperature is selected as the lubricating oil outlet temperature; Output parameters V1 include: total bearing friction heat generation power Q; The internal parameters V2 include: 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 generatrix, the Euler coefficient Eu, the total resistance coefficient f, and the loss influence coefficient beta.

4. The method according to claim 1, characterized in that: In the one-dimensional lubricating oil circulation system simulation model, 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 hydraulicResistance 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, 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 joint simulation thermal analysis of the bearing cavity.

5. The method according to claim 1, characterized in that The 3D bearing component simulation model includes: Establish a three-dimensional model of the fluid inside the bearing cavity; mesh the three-dimensional model of the fluid inside the bearing cavity to generate a three-dimensional model mesh; set the calculation domain model; set boundary conditions; set solver parameters; set stop criterion parameters; set link connections.

6. A lubricating oil circulation system design system for bearing heat dissipation, the system is used to implement the method according to any one of claims 1 to 5, characterized in that: The system comprises: an analysis module, a compilation module, a one-dimensional model building module, a three-dimensional model building module and a simulation module; The analysis module is used to perform theoretical analysis on the heat generation of the bearing and obtain the calculation process of the heat generation of the bearing; The compiling module is used to compile the bearing heat generation calculation submodel using the submodel editor in AMESim according to the bearing heat generation calculation process to obtain 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 input, output, dynamic behavior and interaction parameters; The three-dimensional model building module is used to build a three-dimensional bearing component simulation model in STAR-CCM+ to obtain inlet and outlet conditions, operating parameters and interaction parameters; The simulation module is used to run simulation based on heat input data, system-level input, output, dynamic behavior and interaction parameters, inlet and outlet conditions, operating parameters and interaction parameters.

7. The system according to claim 6, characterized in that The bearing heat generation calculation process includes: Q bfr =CZρL 2 you 3 b′, Among them, 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 roller, u is the circumferential speed of the bearing cage, β′ is the influence coefficient of radial clearance on power loss, C2 is the bearing fluid dynamic resistance coefficient, and C=C1+C2 is the total bearing friction coefficient.

8. The system according to claim 6, characterized in that 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 parameters P include: the pitch circle diameter D of the short cylindrical roller bearing m , roller diameter D r , the effective length L of the short cylindrical roller, the number Z of the short cylindrical rollers, and the radial clearance h matched by the bearing; Input parameters V0 include: bearing speed Rs, bearing radial load F r , the kinematic viscosity nu, density rho, thermal conductivity k of the lubricating oil, and the specific heat capacity Cp when the qualitative temperature is selected as the lubricating oil outlet temperature; Output parameters V1 include: total bearing friction heat generation power Q; The internal parameters V2 include: 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 generatrix, the Euler coefficient Eu, the total resistance coefficient f, and the loss influence coefficient beta.

9. The system according to claim 6, characterized in that In the one-dimensional lubricating oil circulation system simulation model, 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 hydraulicResistance 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, 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 joint simulation thermal analysis of the bearing cavity.

10. The system according to claim 6, characterized in that The 3D bearing component simulation model includes: Establish a three-dimensional model of the fluid inside the bearing cavity; mesh the three-dimensional model of the fluid inside the bearing cavity to generate a three-dimensional model mesh; set the calculation domain model; set boundary conditions; set solver parameters; set stop criterion parameters; set link connections.

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