CN112580242B - Method and device for correcting wear profile of engine main bearing - Google Patents
Method and device for correcting wear profile of engine main bearing Download PDFInfo
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- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
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Abstract
The invention discloses a method and a device for correcting a wear profile of an engine main bearing, belonging to the technical field of engine bearing power, wherein the method comprises the following steps: establishing an elastic hydrodynamic lubrication analysis model of the main bearing, and carrying out simulation analysis on the elastic hydrodynamic lubrication condition of the main bearing; based on the elastic liquid dynamic lubrication simulation analysis result of the main bearing, correcting the design molded line of the main bearing by utilizing a finite difference grid, and establishing a wear molded line of the main bearing so as to simulate a stable state achieved after the main bearing is in running-in; and optimizing and analyzing the elastic hydrodynamic lubrication analysis model of the main bearing by using the wear molded line of the main bearing. According to the invention, a steady state achieved after the main bearing is in running-in is simulated through the wear molded line of the main bearing, and the actual working state of the main bearing is better met, so that the simulation precision of the elastic dynamic lubrication analysis of the main bearing is improved, and the misjudgment rate of the reliable durability of the main bearing is reduced.
Description
Technical Field
The invention belongs to the technical field of engine bearing power, and particularly relates to a method and a device for correcting a wear profile of an engine main bearing.
Background
The main bearing is a main bearing part for converting the linear motion of the piston of the internal combustion engine into the rotary motion of the crankshaft, and is also an important friction pair in the working process of the internal combustion engine. In actual work, due to the effects of factors such as inclination and deformation of a journal, the surface appearance effect of a bearing and the like, the edge of the bearing is abraded, the lubrication condition of the main bearing is seriously deteriorated, the service life of the main bearing is shortened, and the reliability and the durability of the internal combustion engine are directly influenced.
The main bearing is special in structural form, bears the action of periodically changed dynamic loads such as gas explosion pressure, inertia force of a piston connecting rod group and the like in work, and simultaneously bears severe working conditions such as high speed, high pressure, high temperature, engine oil deterioration and the like, the main bearing can cause vibration deterioration due to poor lubrication, the vibration of the main bearing can be used as an excitation source to cause additional vibration of the whole machine, so that the vibration noise characteristic of the whole machine is deteriorated, the power reduction of the whole machine can be caused in severe cases, and even the crankshaft can be broken. Therefore, the response condition of the elastic dynamic lubrication of the main bearing of the crankshaft is a key factor influencing the reliability and durability of the internal combustion engine, the vibration of the whole engine and the noise level.
At present, the main bearing elastic fluid dynamic lubrication simulation is to judge the lubrication condition of the main bearing by analyzing parameters such as rough contact pressure, average heat load, minimum oil film thickness and the like. If the simulation result shows that the main bearing is eccentric and the edge heat load is too high, the main bearing is judged to have risks of excessive abrasion and tile burning, and the reliability and durability can not meet the design and development target.
The patent application CN107665286A is referred to and discloses an engine bearing dynamics analysis method, which comprises the steps of firstly determining relevant three-dimensional data of an engine and a connecting rod assembly, counting engine result information and relevant information of connecting rod system parts, selecting an EHD special module, establishing an engine bearing dynamics analysis model, carrying out grid division on the model and reducing the model, carrying out dynamics simulation by utilizing the reduced engine dynamics module and an exb dynamics file, obtaining results of oil films, engine oil and the like of bearings under specific working conditions from simulation results, evaluating the results, and optimizing and analyzing structures and parameters of a bearing seat structure and the bearings if the results do not meet requirements.
However, the elastic dynamic lubrication simulation analysis of the existing main bearing does not consider that a running-in process exists between the main bearing and the main journal in the actual running process of the engine, and the main bearing generates a certain abrasion loss in the running-in process, so that misjudgment on the evaluation of the reliable durability of the main bearing is easily caused. And after misjudgment, the main bearing needs to be re-selected, and the main means is to upgrade or thicken the main bearing material or optimize the structural parameters of the main bearing, including the width, the diameter, the oil hole, the oil groove and the like of the main bearing. The material upgrading or thickening of the main bearing can cause the problems of increased part cost, difficult arrangement of the main bearing and the like; by optimizing the structural parameters of the main bearing, the design and verification period of the main bearing can be prolonged, and development resources are wasted.
Disclosure of Invention
Aiming at the defects or the improvement requirements in the prior art, the invention provides a method and a device for correcting the wear profile of the main bearing of the engine.
To achieve the above object, according to one aspect of the present invention, there is provided a wear profile modification method of an engine main bearing, comprising:
s1: establishing an elastic hydrodynamic lubrication analysis model of the main bearing, and carrying out simulation analysis on the elastic hydrodynamic lubrication condition of the main bearing;
s2: based on the elastic liquid dynamic lubrication simulation analysis result of the main bearing, correcting the design molded line of the main bearing by utilizing a finite difference grid, and establishing a wear molded line of the main bearing so as to simulate a stable state achieved after the main bearing is in running-in;
s3: and optimizing and analyzing the elastic hydrodynamic lubrication analysis model of the main bearing by using the wear molded line of the main bearing.
In some alternative embodiments, step S1 includes:
s1.1: establishing a finite element model of the power assembly, wherein the main bearing adopts a first-order hexahedral mesh, and a plurality of layers of meshes are uniformly arranged in the thickness direction; the circumferential grid nodes are uniformly distributed; the axial grid nodes are unevenly distributed and are centrosymmetric about the width direction of the main bearing, and the grid lengths are sequentially decreased from the center of the main bearing to two sides;
s1.2: based on a finite element model of the power assembly, completing modular modeling of the flexible body units, completing parametric modeling of the connecting units, completing the definition of dynamic global parameters and load boundary conditions, and establishing a multi-body dynamic model of the power assembly by utilizing a reduced substructure;
s1.3: based on a multi-body dynamic model of the power assembly, setting structural parameters and material attribute parameters of the main bearing, setting oil supply boundary conditions, setting physical parameters of engine oil, completing modular modeling of the main bearing, introducing parameterized design molded lines of the main bearing, and establishing an elastic liquid dynamic lubrication analysis model of the main bearing.
In some alternative embodiments, step S2 includes:
s2.1: analyzing the simulation result of the main bearing elastic hydrodynamic lubrication, and preliminarily judging the lubrication condition of the main bearing;
s2.2: determining a wear region of the main bearing by utilizing a finite difference grid based on an elastic hydrodynamic lubrication simulation analysis result of the main bearing;
s2.3: and setting the abrasion amount in an allowable range in the abrasion area of the main bearing according to the evaluation limit value requirement of the reliable durability of the main bearing based on the design profile of the main bearing, and establishing the abrasion profile of the main bearing.
In some alternative embodiments, step S2.2 comprises:
s2.21: uniformly differentiating on the basis of a main bearing finite element grid in an elastic fluid dynamic lubrication analysis model of a main bearing to obtain a main bearing finite difference grid with increased grid density and uniformly distributed, wherein the axial node number of the main bearing finite difference grid is n times of the main bearing finite element grid plus 1; similarly, the number of circumferential nodes of the main bearing finite element grid is ensured to be n times +1 of the main bearing finite element grid, and n is a natural number;
s2.22: acquiring the basic size and the node number of an axial grid of a main bearing finite difference grid, the node number of a circumferential grid and an angle corresponding to one circumferential basic grid;
s2.23: determining a circumferential angle range of the main bearing in which edge abrasion occurs by combining a peak value rough contact pressure distribution cloud picture of the main bearing, selecting an angle which is closest to a position in which the edge abrasion occurs and meets a target relationship in the circumferential angle range, and setting the angle as the circumferential abrasion position of the main bearing, wherein the target relationship is an angle multiplied by l corresponding to a circumferential basic grid, and l is a natural number;
s2.24: and setting a position in the axial direction to represent the position of the main bearing stopping wear, wherein the position must be overlapped with the axial node of the finite difference grid of the main bearing, setting the position as the axial stopping wear position of the main bearing, and taking the circumferential wear position and the axial stopping wear position of the main bearing as the wear area of the main bearing.
In some alternative embodiments, step S2.22 comprises:
from NAxialDetermining the axial node number N of the main bearing finite difference grid as 6N +1AxialFrom
Determining a base dimension L of an axial grid of a main bearing finite difference gridAxialFrom NCircleDetermining the number N of circumferential nodes of the main bearing finite difference gridCircleFrom
Determining an angle A corresponding to a base grid circumferential to a finite difference grid of a main bearingCircleN is a natural number, b is the width of the main bearing, and x is the circumferential grid number of the main bearing finite element grid.
In some alternative embodiments, step S2.24 comprises:
by X ═ LAxialM determining the position X of the main bearing at which the wear ceases in the axial direction, m being from 1 to NAxialIs an integer between.
According to another aspect of the present invention, there is provided a wear profile modification apparatus for an engine main bearing, comprising:
the model building module is used for building an elastic hydrodynamic lubrication analysis model of the main bearing and carrying out simulation analysis on the elastic hydrodynamic lubrication condition of the main bearing;
the correction module is used for correcting the design molded line of the main bearing by utilizing a finite difference grid based on the elastic hydrodynamic lubrication simulation analysis result of the main bearing and establishing a wear molded line of the main bearing so as to simulate a stable state achieved after the main bearing is in running-in;
and the optimization analysis module is used for performing optimization analysis on the elastic liquid dynamic lubrication analysis model of the main bearing by using the wear molded line of the main bearing.
According to another aspect of the invention, a computer-readable storage medium is provided, on which a computer program is stored which, when being executed by a processor, carries out the steps of the method of any of the above.
In general, compared with the prior art, the above technical solution contemplated by the present invention can achieve the following beneficial effects:
the invention provides an analysis idea of the engine main bearing elastic liquid dynamic lubrication simulation, and considers the running-in process between a main bearing and a main journal in the actual operation process of an engine. The wear profile of the main bearing is utilized to perform optimization analysis on the main bearing elastic liquid dynamic lubrication simulation model, the misjudgment rate of the main bearing on the reliable durability is reduced, the development efficiency of the main bearing is improved, the part cost is reduced, and the arrangement boundary of the main bearing is optimized.
The invention provides a wear profile correction method for elastic liquid dynamic lubrication simulation analysis of an engine main bearing.
Drawings
FIG. 1 is a schematic flow chart of a method for correcting a wear profile of an engine main bearing according to an embodiment of the present invention;
FIG. 2 is a schematic flow chart illustrating another method for modifying a wear profile of an engine main bearing according to an embodiment of the present invention;
FIG. 3 is a schematic diagram of a finite element mesh of a main bearing according to an embodiment of the present invention;
FIG. 4 is a schematic representation of a design profile of a main bearing provided by an embodiment of the present invention;
FIG. 5 is a schematic illustration of a peak asperity contact pressure variation profile of an optimized front main bearing provided by embodiments of the present invention;
FIG. 6 is a cloud representation of a peak asperity contact pressure distribution of an optimized front main bearing provided by embodiments of the present invention;
FIG. 7 is a cloud view illustrating the average heat load distribution of an optimized front main bearing according to an embodiment of the present invention;
FIG. 8 is a schematic view of a wear profile modification of a main bearing provided in accordance with an embodiment of the present invention;
FIG. 9 is a schematic comparison of peak asperity contact pressure profiles for an optimized front and rear main bearing provided by embodiments of the invention;
FIG. 10 is a comparative schematic illustration of a cloud of peak asperity contact pressure distributions for an optimized front and rear main bearing provided by embodiments of the present invention;
FIG. 11 is a comparative schematic illustration of a cloud profile of the mean heat load profile of an optimized front and rear main bearing provided by an embodiment of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention. In addition, the technical features involved in the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.
Fig. 1 is a schematic flow chart of a method for correcting a wear profile of an engine main bearing according to an embodiment of the present invention, including the following steps:
s1: establishing an elastic hydrodynamic lubrication analysis model of the main bearing, and carrying out simulation analysis on the elastic hydrodynamic lubrication condition of the main bearing;
s2: based on the elastic liquid dynamic lubrication simulation analysis result of the main bearing, correcting the design Profile of the main bearing by utilizing a finite difference grid, and establishing a wear Profile (work Profile) of the main bearing so as to simulate a stable state achieved after the main bearing is in running-in;
s3: and optimizing and analyzing the elastic hydrodynamic lubrication analysis model of the main bearing by using the wear molded line of the main bearing.
The implementation of each step is explained in detail by using a flow diagram of a wear profile correction method for the elastic hydrodynamic lubrication analysis of the engine crankshaft main bearing shown in fig. 2.
In the embodiment of the present invention, step S1 may be implemented as follows:
s1.1: establishing a finite element model of the power assembly, wherein the main bearing adopts a first-order hexahedral mesh, and a plurality of layers (such as 2-3 layers) of meshes are generally and uniformly arranged in the thickness direction; the circumferential grid nodes are uniformly distributed, and generally 40/60 grids are formed; the axial grid nodes are unevenly distributed and are centrosymmetric about the width direction of the main bearing, the grid lengths are sequentially decreased from the center of the main bearing to two sides, preferably, the grid lengths are b/4, b/6 and b/12 in sequence, wherein b is the width of the main bearing, as shown in fig. 3;
s1.2: based on a finite element model of the power assembly, completing modular modeling of the flexible body units, completing parametric modeling of the connecting units, completing dynamic global parameters and load boundary definition, and establishing a multi-body dynamic model of the power assembly by utilizing a reduced substructure;
s1.3: setting structural parameters such as the width, the diameter, the bearing clearance, an oil hole and an oil groove of a main bearing, material attribute parameters such as the surface roughness, the elastic modulus, the Poisson ratio and the like of the main bearing, setting oil supply boundary conditions, setting physical property parameters such as the viscosity, the density, the specific heat capacity and the like of engine oil, completing the modular modeling of the main bearing, introducing a parameterized design molded line of the main bearing, and establishing an elastic liquid dynamic lubrication analysis model of the main bearing;
in an embodiment of the present invention, further, the parameterized design profile of the main bearing in step S1.3 may be implemented by:
the modern engine widely adopts the axle bush of radial variable wall thickness to adapt to the axle journal and warp, increase the geometric clearance of axle bush in the bearing area, be favorable to engine oil distribution, avoid taking place marginal wear, guarantee that the main bearing has good lubricating property. The parameterized design line of the main bearing is a change curve of the angle-relative wall thickness of the circumferential section of the bearing bush calculated by using a curve linear difference method according to the wall thickness reduction of the bearing bush obtained by detecting main bearing parts, as shown in fig. 4. The design line of the main bearing does not consider the running-in process of the main bearing and the main journal in the actual operation process of the engine.
In the embodiment of the present invention, step S2 may be implemented as follows:
s2.1: analyzing the simulation result of the main bearing elastic hydrodynamic lubrication, and preliminarily judging the lubrication condition of the main bearing;
s2.2: determining a wear region of the main bearing by using a finite difference grid based on an elastic hydrodynamic lubrication simulation analysis result of the main bearing;
s2.3: and setting the abrasion amount in an allowable range in the abrasion area of the main bearing according to the evaluation limit value requirement of the reliability of the main bearing based on the design profile of the main bearing, and establishing the abrasion profile of the main bearing.
In the embodiment of the present invention, step S2.1 may be implemented by:
the peak value rough contact pressure is an important parameter for evaluating whether the main bearing is excessively worn, and the average heat load is an important parameter for evaluating whether the main bearing is burnt and exploded. The evaluation limit of the main bearing elastic hydrodynamic lubrication simulation analysis result is shown in table 1.
TABLE 1 evaluation Limit values for Main bearing elastohydrodynamic lubrication simulation analysis results
Based on a main bearing elastic liquid dynamic lubrication simulation analysis model, taking the characteristic working condition rated rotating speed of a power assembly as an example, the main bearing elastic liquid dynamic lubrication of a certain in-line four-cylinder engine is subjected to simulation analysis. The simulation results of the peak asperity contact pressure variation curve (as shown in fig. 5) of the main bearing show that the peak asperity contact pressure of the main bearing is too high to exceed the evaluation limit. The simulation results of the cloud of the peak rough contact pressure distribution of the main bearings (as shown in fig. 6) show that the edges of the main bearings are worn seriously and the peak rough contact pressure exceeds the evaluation limit, wherein in fig. 6, (a) shows the cloud of the peak rough contact pressure distribution of the first main bearing, (b) shows the cloud of the peak rough contact pressure distribution of the second main bearing, (c) shows the cloud of the peak rough contact pressure distribution of the third main bearing, (d) shows the cloud of the peak rough contact pressure distribution of the fourth main bearing, and (e) shows the cloud of the peak rough contact pressure distribution of the fifth main bearing. As shown in fig. 7, the simulation result of the average heat load distribution cloud of the main bearing (see fig. 7) shows that the edge heat load of the main bearing is too high, and seizure easily occur, where in fig. 7, (a) shows the average heat load distribution cloud of the first main bearing, (b) shows the average heat load distribution cloud of the second main bearing, (c) shows the average heat load distribution cloud of the third main bearing, (d) shows the average heat load distribution cloud of the fourth main bearing, and (e) shows the average heat load distribution cloud of the fifth main bearing.
The simulation results shown in fig. 5, 6 and 7 show that the main bearing has poor lubrication condition, eccentric wear occurs, the peak value rough contact pressure and the average heat load exceed the evaluation limit value, and the main bearing has risks of excessive wear and tile burning, which will affect the reliable durability of the main bearing, shorten the service life of the main bearing, and require further optimization analysis.
In the embodiment of the present invention, step S2.2 may be implemented by:
s2.21: uniformly differentiating on the basis of a main bearing finite element grid in an elastic hydrodynamic lubrication analysis model of a main bearing to obtain a main bearing finite difference grid with increased grid density and uniformly distributed, wherein the axial node number of the main bearing finite difference grid is n times of the main bearing finite element grid plus 1; similarly, the number of circumferential nodes of the main bearing finite element grid is ensured to be n times +1 of the main bearing finite element grid so as to ensure the calculation precision, wherein n is a natural number;
s2.22: acquiring the basic size and the node number of an axial grid of a main bearing finite difference grid, the number of grid nodes in the circumferential direction and an angle corresponding to one basic grid in the circumferential direction;
further, from NAxialDetermining the axial node number N of the main bearing finite difference grid as 6N +1AxialFrom
Determining a base dimension L of an axial grid of a main bearing finite difference gridAxialFrom NCircleDetermining the number N of circumferential nodes of the main bearing finite difference gridCircleFrom
Determining an angle A corresponding to a base grid circumferential to a main bearing finite difference gridCircleN is a natural number, b is the width of the main bearing, and x is the circumferential grid number of the main bearing finite element grid;
s2.23: determining a circumferential angle range of the main bearings with edge wear by combining a peak value rough contact pressure distribution cloud chart of the main bearings (as shown in fig. 6, the first main bearing has edge wear in a range of 0-90 deg/180-225 deg/290-300 deg, the second main bearing has edge wear in a range of 110-225 deg, the third main bearing has edge wear in a range of 135-205 deg, the fourth main bearing has edge wear in a range of 135-225 deg, and the fifth main bearing has edge wear in a range of 135-205 deg), selecting an angle which is closest to a position where edge wear occurs and meets a target relation in the circumferential angle range, and setting the angle as a circumferential wear position, wherein the target relation is an angle x l corresponding to a circumferential basic grid, and l is a natural number;
s2.24: and setting a position in the axial direction to represent the position of the main bearing stopping wear, wherein the position must be overlapped with the axial node of the finite difference grid of the main bearing, setting the position as an axial wear position, and taking the circumferential wear position and the axial wear stopping position of the main bearing as the wear area of the main bearing.
Further, by X ═ LAxialM determining the position X of the main bearing at which the wear ceases in the axial direction, m being from 1 to NAxialIs an integer between.
To this end, the setting of the wear area of the main bearing is completed.
In the embodiment of the present invention, step S2.3 may be implemented by:
s2.3: based on the design profile of the main bearing, referring to the evaluation limit requirement of the reliability of the main bearing, setting the wear amount in an allowable range in the wear area of the main bearing, namely increasing the thinning amount of the wall thickness of a bearing bush in the wear area, and establishing the wear profile of the main bearing according to the fact that the wear amount of the main bearing does not exceed 5 microns in principle, as shown in figure 8. In fig. 8, (a) shows a schematic diagram of a wear profile correction of the first main bearing, (b) shows a schematic diagram of a wear profile correction of the second main bearing, (c) shows a schematic diagram of a wear profile correction of the third main bearing, (d) shows a schematic diagram of a wear profile correction of the fourth main bearing, and (e) shows a schematic diagram of a wear profile correction of the fifth main bearing.
In the embodiment of the present invention, step S3 may be implemented as follows:
s3: and optimizing and analyzing the elastic hydrodynamic lubrication analysis model of the main bearing by using the wear molded line of the main bearing.
Fig. 9 is a comparison diagram of peak rough contact pressure variation curves of the front and rear main bearings before optimization according to an embodiment of the present invention, and in fig. 9(a) - (e), the left side illustrates simulation results before optimization, and the right side illustrates simulation results after optimization, where (a) illustrates comparison of peak rough contact pressures of the first main bearings before and after optimization, (b) illustrates comparison of peak rough contact pressures of the second main bearings before and after optimization, (c) illustrates comparison of peak rough contact pressures of the third main bearings before and after optimization, (d) illustrates comparison of peak rough contact pressures of the fourth main bearings before and after optimization, and (e) illustrates comparison of peak rough contact pressures of the fifth main bearings before and after optimization; fig. 10 shows a comparison of cloud images of peak rough contact pressure distribution of the front and rear main bearings before optimization, and in fig. 10(a) - (e), the left side shows a simulation result before optimization, and the right side shows a simulation result after optimization, where (a) shows a comparison of cloud images of peak rough contact pressure distribution of the first main bearing before optimization and the first main bearing after optimization, (b) shows a comparison of cloud images of peak rough contact pressure distribution of the second main bearing before optimization and the second main bearing after optimization, (c) shows a comparison of cloud images of peak rough contact pressure distribution of the third main bearing before optimization and the third main bearing after optimization, (d) shows a comparison of cloud images of peak rough contact pressure distribution of the fourth main bearing before optimization and the fourth main bearing after optimization, and (e) shows a comparison of cloud images of peak rough contact pressure distribution of the fifth main bearing before optimization and the fifth main bearing after optimization; as shown in fig. 11, the left side of the drawings shows the simulation result before the optimization, and the right side of the drawings shows the simulation result after the optimization, where (a) shows the comparison of the average heat load distribution clouds of the first main bearing before and after the optimization, (b) shows the comparison of the average heat load distribution clouds of the second main bearing before and after the optimization, (c) shows the comparison of the average heat load distribution clouds of the third main bearing before and after the optimization, (d) shows the comparison of the average heat load distribution clouds of the fourth main bearing before and after the optimization, and (e) shows the comparison of the average heat load distribution clouds of the fifth main bearing before and after the optimization. Fig. 9, 10, and 11 show the simulation results of the main bearing elastohydrodynamic lubrication based on the design profile before optimization, and show the simulation results of the main bearing elastohydrodynamic lubrication based on the wear profile after optimization.
As can be seen from the simulation results before optimization in fig. 9, 10, and 11, the lubrication condition of the main bearing before optimization is poor, eccentric wear occurs, the peak value rough contact pressure and the average heat load exceed the evaluation limit, the main bearing has risks of excessive wear and tile burning, and the design and development target is not satisfied. However, in the actual operation process of the engine, a running-in process exists between the main bearing and the main journal, and in the running-in process, the main bearing generates a certain abrasion loss, and the abrasion loss does not influence the reliable durability of the main bearing in an allowable range. Therefore, the designed profile of the main bearing is corrected, the wear profile of the main bearing is established, the wear profile of the main bearing is utilized to perform optimization analysis on the main bearing elastic liquid dynamic lubrication analysis model, and the optimized simulation results in fig. 9, 10 and 11 show that the lubrication condition of the main bearing is obvious after optimization, the peak value rough contact pressure and the average heat load both meet the evaluation limit value, the risks of excessive wear and tile burning do not exist, and the design and development target is met. Therefore, the elastic liquid lubrication analysis model of the main bearing is optimized and contrastively analyzed by utilizing the abrasion profile line, the misjudgment rate of the reliable durability of the main bearing is reduced, and the simulation analysis precision of the elastic liquid dynamic lubrication of the main bearing is improved.
The application also provides a wear profile correction device of engine main bearing, includes:
the model building module is used for building an elastic hydrodynamic lubrication analysis model of the main bearing and carrying out simulation analysis on the elastic hydrodynamic lubrication condition of the main bearing;
the correction module is used for correcting the design molded line of the main bearing by utilizing a finite difference grid based on the elastic hydrodynamic lubrication simulation analysis result of the main bearing and establishing a wear molded line of the main bearing so as to simulate a stable state achieved after the main bearing is in running-in;
and the optimization analysis module is used for performing optimization analysis on the elastic liquid dynamic lubrication analysis model of the main bearing by using the wear molded line of the main bearing.
The specific implementation of each module may refer to the description of the above method embodiment, and the embodiment of the present invention will not be repeated.
The present application also provides a computer readable storage medium having stored thereon a computer program which, when executed by a processor, implements a method of wear profile correction of an engine main bearing in method embodiments.
According to the scheme, the running-in process of the main bearing and the main journal in the actual operation process of the engine is considered, the design molded line of the main bearing is corrected by combining the elastic liquid dynamic lubrication simulation analysis result of the main bearing, the abrasion molded line of the main bearing is established, the elastic liquid dynamic lubrication analysis model of the main bearing is optimized and analyzed by utilizing the abrasion molded line of the main bearing, the misjudgment rate of the reliable durability of the main bearing is reduced, the development efficiency of the main bearing is improved, the part cost is reduced, and the arrangement boundary of the main bearing is optimized. The method combines the results of the elastic dynamic lubrication simulation analysis, utilizes the finite difference grids to determine the wear area of the main bearing, sets the wear amount in an allowable range in the wear area of the main bearing according to the evaluation limit value requirement of the reliability of the main bearing, and establishes the wear profile of the main bearing. Based on the elastic hydrodynamic lubrication simulation analysis of the wear profile of the main bearing, a stable state achieved after the main bearing is in running-in is simulated, the actual working state of the main bearing is better met, and the simulation precision of the elastic hydrodynamic lubrication analysis of the main bearing is improved.
It should be noted that, according to the implementation requirement, each step/component described in the present application can be divided into more steps/components, and two or more steps/components or partial operations of the steps/components can be combined into new steps/components to achieve the purpose of the present invention.
It will be understood by those skilled in the art that the foregoing is only a preferred embodiment of the present invention, and is not intended to limit the invention, and that any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the scope of the present invention.
Claims (5)
1. A method of modifying a wear profile of an engine main bearing, comprising:
s1: establishing an elastic hydrodynamic lubrication analysis model of the main bearing, and carrying out simulation analysis on the elastic hydrodynamic lubrication condition of the main bearing;
s2: based on the elastic liquid dynamic lubrication simulation analysis result of the main bearing, correcting the design molded line of the main bearing by utilizing a finite difference grid, and establishing a wear molded line of the main bearing so as to simulate a stable state achieved after the main bearing is in running-in;
s3: optimizing and analyzing an elastic hydrodynamic lubrication analysis model of the main bearing by using the wear molded line of the main bearing;
step S1 includes:
s1.1: establishing a finite element model of the power assembly, wherein the main bearing adopts a first-order hexahedral mesh, and a plurality of layers of meshes are uniformly arranged in the thickness direction; the circumferential grid nodes are uniformly distributed; the axial grid nodes are unevenly distributed and are centrosymmetric about the width direction of the main bearing, and the grid lengths are sequentially decreased from the center of the main bearing to two sides;
s1.2: based on a finite element model of the power assembly, completing modular modeling of the flexible body units, completing parametric modeling of the connecting units, completing the definition of dynamic global parameters and load boundary conditions, and establishing a multi-body dynamic model of the power assembly by utilizing a reduced substructure;
s1.3: setting structural parameters and material attribute parameters of a main bearing, setting oil supply boundary conditions, setting physical property parameters of engine oil, completing modular modeling of the main bearing, introducing parameterized design molded lines of the main bearing, and establishing an elastic liquid dynamic lubrication analysis model of the main bearing based on a multi-body dynamic model of a power assembly;
step S2 includes:
s2.1: analyzing the simulation result of the main bearing elastic hydrodynamic lubrication, and preliminarily judging the lubrication condition of the main bearing;
s2.2: determining a wear region of the main bearing by utilizing a finite difference grid based on an elastic hydrodynamic lubrication simulation analysis result of the main bearing;
s2.3: setting the abrasion loss in an allowable range in an abrasion area of the main bearing according to the evaluation limit value requirement of the reliable durability of the main bearing based on the design profile of the main bearing, and establishing the abrasion profile of the main bearing;
step S2.2 comprises:
s2.21: uniformly differentiating on the basis of a main bearing finite element grid in an elastic hydrodynamic lubrication analysis model of a main bearing to obtain a main bearing finite difference grid with increased grid density and uniformly distributed, wherein the axial node number of the main bearing finite difference grid is n times of the main bearing finite element grid plus 1; similarly, the number of circumferential nodes of the main bearing finite element grid is ensured to be n times +1 of the main bearing finite element grid, and n is a natural number;
s2.22: obtaining the basic size and the node number of an axial grid of a main bearing finite difference grid, the node number of a circumferential grid and an angle corresponding to one circumferential basic grid;
s2.23: determining a circumferential angle range of the main bearing in which edge abrasion occurs by combining a peak value rough contact pressure distribution cloud picture of the main bearing, selecting an angle which is closest to a position in which the edge abrasion occurs and meets a target relationship in the circumferential angle range, and setting the angle as the circumferential abrasion position of the main bearing, wherein the target relationship is an angle multiplied by l corresponding to a circumferential basic grid, and l is a natural number;
s2.24: and setting a position in the axial direction to represent the position of the main bearing stopping wear, wherein the position must be overlapped with the axial node of the finite difference grid of the main bearing, setting the position as the axial stopping wear position of the main bearing, and taking the circumferential wear position and the axial stopping wear position of the main bearing as the wear area of the main bearing.
2. The method of wear profile modification of claim 1, wherein step S2.22 includes:
from NAxialDetermining the axial node number N of the main bearing finite difference grid as 6N +1AxialFrom
Determining a base dimension L of an axial grid of a main bearing finite difference gridAxialFrom NCircleDetermining the number N of circumferential nodes of the main bearing finite difference gridCircleFrom
Determining an angle A corresponding to a base grid circumferential to a finite difference grid of a main bearingCircleN is a natural number, b is the width of the main bearing, and x is the circumferential grid number of the main bearing finite element grid.
3. The wear profile modification method of claim 2, wherein step S2.24 comprises:
by X ═ LAxialM determining the position X of the main bearing at which the wear ceases in the axial direction, m being from 1 to NAxialIs an integer between.
4. A wear profile modification apparatus for an engine main bearing for implementing the wear profile modification method according to claims 1 to 3, comprising:
the model building module is used for building an elastic hydrodynamic lubrication analysis model of the main bearing and carrying out simulation analysis on the elastic hydrodynamic lubrication condition of the main bearing;
the correction module is used for correcting the design molded line of the main bearing by utilizing a finite difference grid based on the elastic hydrodynamic lubrication simulation analysis result of the main bearing and establishing a wear molded line of the main bearing so as to simulate a stable state achieved after the main bearing is in running-in;
and the optimization analysis module is used for performing optimization analysis on the elastic liquid dynamic lubrication analysis model of the main bearing by using the wear molded line of the main bearing.
5. A computer-readable storage medium, on which a computer program is stored, which, when being executed by a processor, carries out the steps of the method of any one of claims 1 to 3.
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