Method and device for acquiring thickness of oil film of sliding bearing

Abstract

The invention provides a sliding bearing oil film thickness obtaining method and device, and the method comprises the steps: building a micro-contact roughness model of a sliding bearing, and obtaining the contact pressure and contact area of a shaft of the bearing and a bearing bush rough peak according to the micro-contact roughness model; establishing a wear model of the sliding bearing, and obtaining the wear depth hw of the sliding bearing according to the wear model, the contact pressure and the contact area; obtaining the elastic deformation hE of the sliding bearing; according to the included angle between the axis of the sliding bearing journal and the center line of the bearing and the included angle between the circle center connecting line of the front and rear end faces of the journal and the center connecting line of the bearing and the journal, the journal inclination h '0 is obtained; and obtaining the thickness h of the oil film of the sliding bearing according to hw, he and h '0. According to the method, the influence of factors such as abrasion, elastic deformation and journal inclination in the working process of the bearing on the oil film thickness is fully considered, the oil film thickness of the sliding bearing can be accurately calculated and monitored, a theoretical basis is provided for design of the sliding bearing, and reliable operation of the bearing is guaranteed.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of rotary machinery, in particular to a method for obtaining the oil film thickness of a sliding bearing and a device for obtaining the oil film thickness of a sliding bearing. BACKGROUND

[0002] In a sliding bearing, an oil film separates the shaft journal from the bearing surface, avoiding direct contact, which can significantly reduce the friction coefficient, energy loss, protect the contact surface, reduce wear, and thus prolong the service life of the bearing. The oil film thickness is a key parameter of the sliding bearing, which determines the lubrication state and performance of the bearing. Therefore, it is necessary to calculate and monitor the oil film thickness of the sliding bearing during the design and operation stages of the bearing.

[0003] In related technologies, the oil film thickness is generally measured directly using a microscope or a laser range finder, or inferred indirectly based on the properties of the lubricating oil. In the above two methods, the direct measurement method is only suitable for laboratory environments and is not suitable for online monitoring. Although the indirect measurement method is suitable for industrial applications, it does not consider the influence of actual environmental factors. The bearing will wear or deform to some extent during operation, which will also affect the oil film thickness. Therefore, the oil film thickness calculated by this method is not accurate enough. SUMMARY

[0004] To solve the above technical problems, the first purpose of the present application is to provide a method for obtaining the oil film thickness of a sliding bearing.

[0005] The second purpose of the present application is to provide a device for obtaining the oil film thickness of a sliding bearing.

[0006] The technical solutions adopted by the present application are as follows:

[0007] The embodiment of the present application provides a method for obtaining the oil film thickness of a sliding bearing, comprising the following steps: establishing a micro-contact roughness model of the sliding bearing, obtaining the contact pressure and contact area of the rough peaks of the shaft and the bearing shell of the bearing according to the micro-contact roughness model; establishing a wear model of the sliding bearing, obtaining the wear depth h w of the sliding bearing according to the wear model, the contact pressure and contact area; obtaining the elastic deformation amount h E of the sliding bearing; obtaining the angle between the axis of the journal and the center line of the bearing and the angle between the center line of the journal and the center line of the bearing and the journal, obtaining the inclination amount h′0 of the journal; obtaining the oil film thickness h of the sliding bearing according to the wear depth h w , the elastic deformation amount h e and the inclination amount h′0 of the journal.

[0008] The method for obtaining the oil film thickness of a sliding bearing proposed in this invention may also have the following additional technical features:

[0009] According to one embodiment of the present invention, the micro-contact roughness model is specifically established based on the following formula: Where η is the bearing roughness peak distribution density, a is the roughness peak curvature radius; σ is the Gaussian distribution variance, E′ is the comprehensive elastic modulus, and A n For nominal contact area, F n (I t ) is the probability distribution function of the rough peak height, I t p is the film thickness ratio c A represents the contact pressure between the roughness peaks of the shaft and the bearing bush. c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

[0010] According to one embodiment of the present invention, the wear depth h of the sliding bearing is obtained specifically according to the following formula. w :h w =kp c s / H b ; Among them, F c Where is the contact load, s is the sliding distance, and H is the contact load. b The bearing hardness is k; the wear coefficient is μ. b σ is the boundary friction coefficient, τ is the friction fatigue index, and σ is the friction fatigue coefficient. T For tensile strength, p c A represents the contact pressure between the roughness peaks of the shaft and the bearing bush. c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

[0011] According to one embodiment of the present invention, the elastic deformation h of the sliding bearing is obtained according to the following formula. E :

[0012]

[0013] Among them, h E E' is the elastic deformation, x is the comprehensive elastic modulus, y is the horizontal coordinate of the sliding bearing, x' is the additional coordinate of x, y' is the additional coordinate of y, Ω′ is the computational domain, and p is the distributed load of the sliding bearing.

[0014] According to an embodiment of the present invention, the journal tilt amount h′0 is obtained according to the following formula:

[0015]

[0016] Wherein, R is the inner radius of the bearing bush, r' is the rotor radius after the bearing is inclined according to the geometric relationship, z is the axial coordinate of any point on the journal center line, is the angle between the axis of the journal and the center line of the bearing, is the angle between the center line of the journal and the center line of the bearing and the journal, is the angle of the maximum oil film thickness of the sliding bearing, e is the distance from the bearing center O to the journal center O1, is the angle of the line O1O along the Y direction, is the angle of the line O1O along the X direction.

[0017] The second aspect embodiment of the present application provides a sliding bearing oil film thickness acquisition device, comprising: a first acquisition module, the first acquisition module is used for establishing a micro-contact roughness model of a sliding bearing, and acquiring the contact pressure and contact area of the rough peaks of the bearing and the bearing bush according to the micro-contact roughness model; a second acquisition module, the second acquisition module is used for establishing a wear model of the sliding bearing, and acquiring the wear depth h w of the sliding bearing according to the wear model, the contact pressure and the contact area; E a third acquisition module, the third acquisition module is used for acquiring the elastic deformation amount h e of the sliding bearing; w a fourth acquisition module, the fourth acquisition module is used for acquiring the angle between the axis of the journal and the center line of the bearing and the angle between the center line of the journal and the center line of the bearing and the journal, and acquiring the journal inclination amount h'0; e a fifth acquisition module, the fifth acquisition module is used for acquiring the sliding bearing oil film thickness h according to the wear depth h n , the elastic deformation amount h n and the journal inclination amount h'0.

[0018] The sliding bearing oil film thickness acquisition device of the present application has the following additional technical features:

[0019] According to one embodiment of the present application, the first acquisition module specifically establishes the micro-contact roughness model according to the following formula:

[0020]

[0021] Wherein, η is the rough peak distribution density of the bearing bush, a is the roughness peak curvature radius; σ is the Gaussian distribution variance, E' is the comprehensive elastic modulus, A n is the nominal contact area, F n (I t ) is the rough peak height probability distribution function, I t is the film thickness ratio, p c is the contact pressure of the shaft and the rough peak of the bearing bush, A c is the contact area of the shaft and the rough peak of the bearing bush.

[0022] According to one embodiment of the present application, the second obtaining module obtains the wear depth h of the sliding bearing according to the following formula w : h w = kp c s / H b ; wherein F c is the contact load, s is the sliding distance, H b is the bush hardness; k is the wear coefficient, μ b is the boundary friction coefficient, τ is the friction fatigue index, σ T is the tensile strength, p c is the contact pressure of the shaft and the bush rough peak, A c is the contact area of the shaft and the bush rough peak.

[0023] According to one embodiment of the present application, the third obtaining module obtains the elastic deformation amount h of the sliding bearing according to the following formula E : wherein h E is the elastic deformation amount, E' is the comprehensive elastic modulus, x is the horizontal coordinate of the sliding bearing, y is the vertical coordinate of the sliding bearing, x' is the additional coordinate of x, y' is the additional coordinate of y, Ω' is the calculation domain, and p is the distributed load of the sliding bearing.

[0024] According to one embodiment of the present application, the fourth obtaining module obtains the shaft journal inclination amount h'0 according to the following formula:

[0025]

[0026] wherein R is the inner radius of the bush, r' is the rotor radius corrected according to the geometric relationship after the bearing is inclined, z is the axial coordinate of any point on the shaft journal center line, α is the included angle between the axis of the sliding bearing journal and the bearing center line, β is the included angle between the center line of the front and rear end faces of the shaft journal and the center line of the bearing and the shaft journal, is the angle at the maximum oil film thickness of the sliding bearing, e is the distance from the bearing center O to the shaft journal center O1, ∠D is the angle along the Y direction in which the connecting line O1O of the shaft journal center O1 to the bearing center O is inclined, and ∠E is the included angle along the X direction.

[0027] Advantages of the present application:

[0028] The present application fully considers the influence of the factors such as wear, elastic deformation and shaft journal inclination on the oil film thickness during the working process of the bearing, can accurately calculate and monitor the oil film thickness of the sliding bearing, provides a theoretical basis for the design of the sliding bearing, and ensures the reliable operation of the bearing. BRIEF DESCRIPTION OF DRAWINGS

[0029] Figure 1is a flow chart of a method for obtaining a sliding bearing oil film thickness according to an embodiment of the present application;

[0030] Figure 2 is a curve of a relationship between a journal tilt angle and an oil film thickness according to an embodiment of the present application;

[0031] Figure 3 is a schematic diagram of a geometric relationship between a sliding bearing journal and a bearing center line according to an embodiment of the present application;

[0032] Figure 4 is a block schematic diagram of a device for obtaining a sliding bearing oil film thickness according to an embodiment of the present application. DETAILED DESCRIPTION

[0033] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only some of the embodiments of the present application, but not all the embodiments of the present application. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0034] The present application is made by the inventors based on research and recognition of the following problems:

[0035] Sliding bearings are widely used in actual production activities, and the bearing system of heavy equipment is often in a mixed lubrication state due to high load work. At this time, the bushing will appear elastic deformation, the rough peak surface of the shaft and the bushing will be in contact, the friction will increase and wear will be caused, which will affect the lubrication characteristics of the bearing and the safe operation of the mechanical equipment. At the same time, due to the reasons such as unbalanced load and installation error, the journal will have a certain tilt, and these factors will significantly affect the tribological properties of the bearing.

[0036] Figure 1 is a flow chart of a method for obtaining a sliding bearing oil film thickness according to an embodiment of the present application, as shown in Figure 1 the method comprises the following steps:

[0037] S1, a micro-contact roughness model of a sliding bearing is established, and the contact pressure and the contact area of the rough peak of the shaft and the bushing of the bearing are obtained according to the micro-contact roughness model.

[0038] In one specific embodiment of the present application, the micro-contact roughness model is established according to the following formula:

[0039]

[0040] wherein η is the rough peak distribution density of the bushing, a is the rough peak curvature radius; σ is the Gaussian distribution variance, E' is the comprehensive elastic modulus, A nFor nominal contact area, F n (I t Let be the probability distribution function of the rough peak height, representing (S-λ). n The mathematical expectation (where S is the standardized rough peak height coordinate, and n in the above formula is respectively) and 2), I t p is the film thickness ratio c A represents the contact pressure between the roughness peaks of the shaft and the bearing bush. c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

[0041] ηaσ is usually taken as 0.02 to 0.10; We obtain E1 as the elastic modulus of the bearing, ν1 as the Poisson's ratio of the bearing, E2 as the elastic modulus of the shaft, and ν2 as the Poisson's ratio of the shaft.

[0042] S2. Establish a wear model for the sliding bearing, and obtain the wear depth h of the sliding bearing based on the wear model, contact pressure, and contact area. w .

[0043] Specifically, the wear volume V of the bearing under steady-state operating conditions w and wear depth h w It can be obtained from the following wear model, namely

[0044]

[0045] Among them, F c Where is the contact load, s is the sliding distance, and H is the contact load. b For the bearing hardness, p c Let k be the contact pressure between the rough peaks of the shaft and the bearing bush, and k be the wear coefficient. k is related to parameters such as the contact area and boundary friction coefficient at different times. Specifically, the wear coefficient k can be obtained from the following formula:

[0046]

[0047] Where, μ b σ is the boundary friction coefficient, τ is the friction fatigue index, and σ is the friction fatigue coefficient. T For tensile strength A c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

[0048] Assume the wear volume of the bearing during time t is V. w Then the wear rate ω w Defined as: ω w =V w / t.

[0049] S3, Obtain the elastic deformation h of the sliding bearing. E .

[0050] Specifically, the classic lubrication theory usually considers that the lubrication surfaces of the journal and the bearing bush are rigid, which is reasonable in light load conditions. However, in heavy load conditions, the local pressure of the bearing is large, and the elastic deformation of the bearing bush surface is large and cannot be ignored. The displacement equation is derived by adopting the elastic semi-infinite space subjected to force.

[0051] The oil film thickness expression without considering the elastic deformation is:

[0052]

[0053] Wherein, h0 is the oil film thickness without considering the elastic deformation, c is the radius gap of the bearing, and ε is the eccentricity; is the angle at the maximum oil film.

[0054] The elastic deformation amount h of the sliding bearing E :

[0055]

[0056] Wherein, h E is the elastic deformation amount, E' is the comprehensive elastic modulus, x is the horizontal coordinate of the sliding bearing, y is the vertical coordinate of the sliding bearing, x' is the additional coordinate of x, y' is the additional coordinate of y, Ω' is the calculation domain, and p is the distributed load of the sliding bearing.

[0057] S4, the angle between the axis of the journal of the sliding bearing and the center line of the bearing and the angle between the center line of the front and rear end faces of the journal and the center line of the bearing and the journal are obtained to obtain the inclination amount h'0 of the journal.

[0058] Specifically, the inventor finds through relevant tests that, as shown in Figure 2 , after the journal is inclined, with the increase of the inclination angle α, the maximum film thickness (oil film thickness h) of the bearing increases, and the minimum film thickness becomes smaller and smaller. With the increase of the inclination angle, the rough peak surfaces of the shaft and the bearing bush are in contact and in a mixed lubrication state, and at this time, the friction increases to cause the wear of the bearing.

[0059] After the journal is inclined, the oil film gap is no longer symmetrically distributed along the axial direction, and the oil film thickness of each section is also different, and at this time, the geometric relationship becomes more complex. After the journal is inclined, the film thickness in the axial direction changes (that is, the change of the eccentric distance), and the deflection angle also needs to be corrected. Two angles are needed to determine the inclined position of the journal, that is, the angle α between the axis of the sliding bearing journal after being inclined and the center line of the bearing or the angle α between the axis before being inclined, and the angle β between the center line of the front and rear end faces of the inclined journal and the center line of the bearing and the journal. α can determine the degree of inclination, and β can determine the position of the inclination.

[0060] As shown in Figure 3If O is the bearing center, O1 is the journal center, O2 is the front end face, O3 is the rear end face, O' is an arbitrary point on the journal center line, and the axial coordinate of O' is z (the vertical distance to the middle section of the bearing), then the distance between any point on the axis and the position of the un-inclined axis of the journal is z tan α, and the triangular relationship in the plane can be projected as O' O1 = z tan α, OO1 = e. The eccentricity e' of the section in the arbitrary inclined plane can be obtained by the cosine theorem:

[0061] where z is the axial coordinate of an arbitrary point on the journal center line, e is the distance from the bearing center O to the journal center O1, α is the angle between the axis of the journal of the sliding bearing and the center line of the bearing, and β is the angle between the center line of the front and rear end faces of the journal and the center line of the bearing and the journal.

[0062] The definition of the offset angle θ is the angle between the center line of the journal and the vertical direction of the bearing. After the inclination, the offset angle of each section is no longer the same, that is, the angle between OO' and the vertical direction of the bearing, and the variable of the angle between OO' and the vertical direction of the bearing after the inclination is θ'.

[0063] In the triangle OO1O', according to the sine theorem, we can obtain:

[0064] Simplifying, we obtain: where e' is the eccentricity of the section in the arbitrary inclined plane.

[0065] The offset angle θ of the arbitrary inclined plane is θ = θ0 + θ', θ0 is the angle between the center line of the journal and the vertical direction of the bearing when the journal is not inclined, and θ' is the angle between the center line of the journal and the vertical direction of the bearing after the inclination.

[0066] The initial angle at the arbitrary section is which is calculated from the maximum film thickness: which is the angle at the maximum oil film of the sliding bearing.

[0067] After the inclination of the journal, any section of the journal projects as an ellipse on the bearing end face, and the corresponding geometric relationship of the two inclination angles α and β is transformed into the coordinate system XOY. In the coordinate system XOY, the distance of an arbitrary point O projected on OY is z tan α cos β, and the distance projected on OX is z tan α sin β. Therefore, the angle of O1O along the Y direction in space is ∠D, and the angle of O1O along the X direction is ∠E. According to the geometric relationship, we can obtain:

[0068]

[0069] Let the coordinates of an arbitrary point F on the journal in the coordinate system XOY be (x, y) when the journal is not inclined. The position of the inclined F point changes to F, and the coordinates of F are The distance r' from the center of the journal to the projection plane after the inclination is:

[0070] r is the rotor radius.

[0071] In triangle OO1A, A is the intersection of the line O1O2 on the rotor inner radius, according to the cosine theorem and substituting the above relationship, the journal inclination h'0 can be obtained by simplifying:

[0072]

[0073] wherein, wherein, R is the inner radius of the bearing bush, r' is the rotor radius after the bearing inclination is corrected according to the geometric relationship, is the angle at the maximum thickness of the oil film of the sliding bearing, θ' is the angle variable of the line connecting the center of the journal and the center of the bearing with the vertical direction of the bearing after the journal inclination, and e' is the eccentricity of the section in the arbitrary inclined plane.

[0074] S5, the sliding bearing oil film thickness h is obtained according to the wear depth h w , the elastic deformation amount h e and the journal inclination h'0.

[0075] Specifically, the sliding bearing oil film thickness h is obtained by coupling the wear depth h w , the elastic deformation amount h e and the journal inclination h'0: h = h0' + h w + h E .

[0076] In summary, according to the method for obtaining the sliding bearing oil film thickness of the embodiment of the present application, a micro-contact roughness model of the sliding bearing is first established, the contact pressure and contact area of the rough peaks of the bearing shaft and bearing bush are obtained according to the micro-contact roughness model, then a wear model of the sliding bearing is established, the wear depth h w of the sliding bearing is obtained according to the wear model, the contact pressure and the contact area, the elastic deformation amount h E of the sliding bearing is obtained, the angle between the axis of the journal and the center line of the bearing and the angle between the center line of the front and rear end faces of the journal and the center line of the bearing and the journal are obtained to obtain the journal inclination h'0, and finally, the sliding bearing oil film thickness h is obtained according to the wear depth h w , the elastic deformation amount h e and the journal inclination h'0. Thus, the present application fully considers the influence of factors such as wear, elastic deformation and journal inclination on the oil film thickness during the operation of the bearing, and can accurately calculate and monitor the oil film thickness of the sliding bearing, providing a theoretical basis for the design of the sliding bearing and ensuring the reliable operation of the bearing.

[0077] Corresponding to the above-mentioned method for obtaining the oil film thickness of the sliding bearing, the present application further provides an apparatus for obtaining the oil film thickness of the sliding bearing. Since the apparatus embodiment of the present application corresponds to the above-mentioned method embodiment, the details not disclosed in the apparatus embodiment can be referred to the above-mentioned method embodiment, which will not be described herein again.

[0078] Figure 4 is a block schematic diagram of the apparatus for obtaining the oil film thickness of the sliding bearing according to an embodiment of the present application. As shown in Figure 4 , the apparatus comprises a first obtaining module 1, a second obtaining module 2, a third obtaining module 3, a fourth obtaining module 4 and a fifth obtaining module 5.

[0079] The first obtaining module 1 is configured to establish a micro-contact roughness model of the sliding bearing, and obtain the contact pressure and the contact area of the rough peaks of the shaft and the bearing bush of the bearing according to the micro-contact roughness model; the second obtaining module 2 is configured to establish a wear model of the sliding bearing, and obtain the wear depth h w of the sliding bearing according to the wear model, the contact pressure and the contact area; the third obtaining module 3 is configured to obtain the elastic deformation amount h E of the sliding bearing; the fourth obtaining module 4 is configured to obtain the included angle between the axis of the journal and the center line of the bearing and the included angle between the center line of the journal and the center line of the bearing and the journal to obtain the journal inclination amount h′0; and the fifth obtaining module 5 is configured to obtain the oil film thickness h of the sliding bearing according to the wear depth h w , the elastic deformation amount h e and the journal inclination amount h′0.

[0080] According to an embodiment of the present application, the first obtaining module 1 specifically establishes the micro-contact roughness model according to the following formula:

[0081]

[0082] wherein η is the distribution density of the rough peaks of the bearing bush, a is the curvature radius of the rough peaks, σ is the variance of the Gaussian distribution, E′ is the comprehensive elastic modulus, A n is the nominal contact area, F n (I t ) is the probability distribution function of the rough peak height, I t is the film thickness ratio, p c is the contact pressure of the shaft and the rough peaks of the bearing bush, and A c is the contact area of the shaft and the rough peaks of the bearing bush.

[0083] According to an embodiment of the present application, the second obtaining module 2 specifically obtains the wear depth h w of the sliding bearing according to the following formula: h w =kpc s / H b ; Among them, F c Where is the contact load, s is the sliding distance, and H is the contact load. b The bearing hardness is k; the wear coefficient is μ. b σ is the boundary friction coefficient, τ is the friction fatigue index, and σ is the friction fatigue coefficient. T For tensile strength, p c A represents the contact pressure between the roughness peaks of the shaft and the bearing bush. c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

[0084] According to one embodiment of the present invention, the third acquisition module 3 specifically acquires the elastic deformation h of the sliding bearing according to the following formula. E : Among them, h E E′ is the elastic deformation, x is the comprehensive elastic modulus, y is the horizontal coordinate of the sliding bearing, x′ is the additional coordinate of x, y′ is the additional coordinate of y, Ω′ is the computational domain, and p is the distributed load of the sliding bearing.

[0085] According to one embodiment of the present invention, the fourth acquisition module 4 acquires the journal tilt amount h′0 according to the following formula:

[0086]

[0087] Where R is the inner radius of the bearing bush, r′ is the rotor radius corrected according to geometric relationships after the bearing tilts, z is the axial coordinate of any point on the journal centerline, α is the angle between the axis of the sliding bearing journal and the bearing centerline, and β is the angle between the line connecting the centers of the front and rear end faces of the journal and the line connecting the bearing and the journal centerlines. Let be the angle at the point where the oil film thickness of the sliding bearing is maximum, e be the distance from the bearing center O to the journal center O1, ∠D be the angle of inclination of the line O1O connecting the journal center O1 to the bearing center O along the Y direction, and ∠E be the angle between O1O and the X direction.

[0088] In summary, the sliding bearing oil film thickness acquisition device according to an embodiment of the present invention establishes a micro-contact roughness model of the sliding bearing through a first acquisition module, and obtains the contact pressure and contact area of ​​the roughness peaks between the shaft and the bearing bush based on the micro-contact roughness model; the second acquisition module establishes a wear model of the sliding bearing, and obtains the wear depth h of the sliding bearing based on the wear model, the contact pressure, and the contact area. w The third acquisition module acquires the elastic deformation h of the sliding bearing. EThe fourth acquisition module acquires the angle between the axis of the sliding bearing journal and the bearing centerline, and the angle between the line connecting the centers of the front and rear ends of the journal and the line connecting the bearing and the journal centerline, to obtain the journal inclination h′0. The fifth acquisition module acquires the journal inclination h′0 based on the wear depth h. w The elastic deformation amount h e The oil film thickness h of the sliding bearing is obtained by taking into account the journal tilt amount h'0. Therefore, by fully considering the influence of factors such as wear, elastic deformation, and journal tilt on the oil film thickness during bearing operation, the oil film thickness of the sliding bearing can be accurately calculated and monitored, providing a theoretical basis for the design of sliding bearings and ensuring their reliable operation.

[0089] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., indicate that a specific feature, structure, material, or characteristic described in connection with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, the illustrative expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0090] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0091] Any process or method description in the flowchart or otherwise herein can be understood as representing a module, segment, or portion of code comprising one or more executable instructions for implementing custom logic functions or processes, and the scope of preferred embodiments of the invention includes additional implementations in which functions may be performed not in the order shown or discussed, including substantially simultaneously or in reverse order depending on the functions involved, as should be understood by those skilled in the art to which embodiments of the invention pertain.

[0092] The logic and / or steps represented in the flowchart or otherwise described herein, for example, can be considered as a sequenced list of executable instructions for implementing logical functions, and can be embodied in any computer-readable medium for use by, or in conjunction with, an instruction execution system, apparatus, or device (such as a computer-based system, a processor-included system, or other system that can fetch and execute instructions from, an instruction execution system, apparatus, or device). For the purposes of this specification, "computer-readable medium" can be any means that can contain, store, communicate, propagate, or transmit programs for use by, or in conjunction with, an instruction execution system, apparatus, or device. More specific examples (a non-exhaustive list) of computer-readable media include: an electrical connection having one or more wires (electronic device), a portable computer disk drive (magnetic device), random access memory (RAM), read-only memory (ROM), erasable and editable read-only memory (EPROM or flash memory), fiber optic devices, and portable optical disc read-only memory (CDROM). Alternatively, the computer-readable medium may be paper or other suitable media on which the program can be printed, since the program can be obtained electronically, for example, by optically scanning the paper or other medium, followed by editing, interpreting, or otherwise processing as necessary, and then stored in a computer memory.

[0093] It should be understood that various parts of the present invention can be implemented in hardware, software, firmware, or a combination thereof. In the above embodiments, multiple steps or methods can be implemented in software or firmware stored in memory and executed by a suitable instruction execution system. For example, if implemented in hardware as in another embodiment, it can be implemented using any of the following techniques known in the art, or a combination thereof: discrete logic circuits having logic gates for implementing logical functions on data signals, application-specific integrated circuits (ASICs) having suitable combinational logic gates, programmable gate arrays (PGAs), field-programmable gate arrays (FPGAs), etc.

[0094] Those skilled in the art will understand that all or part of the steps of the methods in the above embodiments can be implemented by a program instructing related hardware. The program can be stored in a computer-readable storage medium, and when executed, the program includes one or a combination of the steps of the method embodiments.

[0095] Furthermore, the functional units in the various embodiments of the present invention can be integrated into a processing module, or each unit can exist physically separately, or two or more units can be integrated into a module. The integrated module can be implemented in hardware or as a software functional module. If the integrated module is implemented as a software functional module and sold or used as an independent product, it can also be stored in a computer-readable storage medium.

[0096] The storage medium mentioned above can be a read-only memory, a disk, or an optical disk, etc. Although embodiments of the present invention have been shown and described above, it is to be understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Those skilled in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A method for obtaining the oil film thickness of a sliding bearing, characterized in that, Includes the following steps: A micro-contact roughness model of a sliding bearing is established, and the contact pressure and contact area of ​​the roughness peaks between the shaft and the bearing bush are obtained based on the micro-contact roughness model. A wear model for the sliding bearing is established, and the wear depth h of the sliding bearing is obtained based on the wear model, the contact pressure, and the contact area. w ; Obtain the elastic deformation h of the sliding bearing E ; Obtain the angle between the axis of the sliding bearing journal and the bearing centerline, and the angle between the line connecting the centers of the front and rear ends of the journal and the line connecting the bearing and the centerline of the journal to obtain the journal inclination h′0. According to the wear depth h w The elastic deformation amount h e The thickness h of the oil film in the sliding bearing is obtained by measuring the journal tilt h′0.

2. The method for obtaining the oil film thickness of a sliding bearing according to claim 1, characterized in that, Specifically, the micro-contact roughness model is established based on the following formula: Where η is the bearing roughness peak distribution density, a is the roughness peak curvature radius; σ is the Gaussian distribution variance, E′ is the comprehensive elastic modulus, and A n For nominal contact area, F n (I t ) is the probability distribution function of the rough peak height, I t p is the film thickness ratio c A represents the contact pressure between the roughness peaks of the shaft and the bearing bush. c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

3. The method for obtaining the thickness of the sliding bearing oil film according to claim 1, characterized in that, The wear depth h of the sliding bearing is specifically obtained using the following formula. w : Among them, F c Where is the contact load, s is the sliding distance, and H is the contact load. b The bearing hardness is k; the wear coefficient is μ. b σ is the boundary friction coefficient, τ is the friction fatigue index, and σ is the friction fatigue coefficient. T For tensile strength, p c A represents the contact pressure between the roughness peaks of the shaft and the bearing bush. c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

4. The method for obtaining the oil film thickness of a sliding bearing according to claim 1, characterized in that, The elastic deformation h of the sliding bearing is obtained according to the following formula. E : Among them, h E E′ is the elastic deformation, x is the horizontal coordinate of the sliding bearing, y is the vertical coordinate of the sliding bearing, x′ is the additional coordinate of x, y′ is the additional coordinate of y, Ω′ is the calculation domain, and p is the oil film pressure.

5. The method for obtaining the thickness of the sliding bearing oil film according to claim 1, characterized in that, The journal tilt amount h′0 is obtained according to the following formula: Where R is the inner radius of the bearing bush, r′ is the rotor radius corrected according to geometric relationships after the bearing tilts, z is the axial coordinate of any point on the journal centerline, α is the angle between the axis of the sliding bearing journal and the bearing centerline, and β is the angle between the line connecting the centers of the front and rear end faces of the journal and the line connecting the bearing and the journal centerlines. Let be the angle at the point where the oil film thickness of the sliding bearing is maximum, e be the distance from the bearing center O to the journal center O1, ∠D be the angle of inclination of the line O1O connecting the journal center O1 to the bearing center O along the Y direction, and ∠E be the angle between O1O and the X direction.

6. A device for obtaining the thickness of an oil film in a sliding bearing, characterized in that, include: The first acquisition module is used to establish a micro-contact roughness model of the sliding bearing and to acquire the contact pressure and contact area of ​​the roughness peaks between the shaft and the bearing bush according to the micro-contact roughness model. The second acquisition module is used to establish a wear model of the sliding bearing and obtain the wear depth h of the sliding bearing based on the wear model, the contact pressure, and the contact area. w ; The third acquisition module is used to acquire the elastic deformation h of the sliding bearing. E ; The fourth acquisition module is used to acquire the angle between the axis of the sliding bearing journal and the bearing center line and the angle between the line connecting the centers of the front and rear ends of the journal and the line connecting the bearing and the center of the journal to acquire the journal tilt amount h′0. The fifth acquisition module is used to obtain information based on the wear depth h. w The elastic deformation amount h e The thickness h of the oil film in the sliding bearing is obtained by measuring the journal tilt h′0.

7. The device for obtaining the thickness of the sliding bearing oil film according to claim 6, characterized in that, The first acquisition module establishes the micro-contact roughness model based on the following formula: Where η is the bearing roughness peak distribution density, a is the roughness peak curvature radius; σ is the Gaussian distribution variance, E′ is the comprehensive elastic modulus, and A n For nominal contact area, F n (I t ) is the probability distribution function of the rough peak height, I t p is the film thickness ratio c A represents the contact pressure between the roughness peaks of the shaft and the bearing bush. c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

8. The device for obtaining the oil film thickness of a sliding bearing according to claim 6, characterized in that, The second acquisition module specifically obtains the wear depth h of the sliding bearing according to the following formula. w : Among them, F c Where is the contact load, s is the sliding distance, and H is the contact load. b The bearing hardness is k; the wear coefficient is μ. b σ is the boundary friction coefficient, τ is the friction fatigue index, and σ is the friction fatigue coefficient. T For tensile strength, p c A represents the contact pressure between the roughness peaks of the shaft and the bearing bush. c This represents the contact area between the roughness peaks of the shaft and the bearing bush.

9. The device for obtaining the thickness of the sliding bearing oil film according to claim 6, characterized in that, The third acquisition module specifically obtains the elastic deformation h of the sliding bearing according to the following formula. E : Among them, h E E′ is the elastic deformation, x is the comprehensive elastic modulus, y is the horizontal coordinate of the sliding bearing, x′ is the additional coordinate of x, y′ is the additional coordinate of y, Ω′ is the computational domain, and p is the distributed load of the sliding bearing.

10. The apparatus for obtaining the thickness of the sliding bearing oil film according to claim 6, characterized in that, The fourth acquisition module obtains the journal tilt h′0 according to the following formula: Where R is the inner radius of the bearing bush, r′ is the rotor radius corrected according to geometric relationships after the bearing tilts, z is the axial coordinate of any point on the journal centerline, α is the angle between the axis of the sliding bearing journal and the bearing centerline, and β is the angle between the line connecting the centers of the front and rear end faces of the journal and the line connecting the bearing and the journal centerlines. Let be the angle at the point where the oil film thickness of the sliding bearing is maximum, e be the distance from the bearing center O to the journal center O1, ∠D be the angle of inclination of the line O1O connecting the journal center O1 to the bearing center O along the Y direction, and ∠E be the angle between O1O and the X direction.

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