Friction clutch joint spline wear determination method, device, equipment, medium and product

Abstract

The invention discloses a friction clutch joint spline abrasion determination method and device, equipment, a medium and a product, and relates to the field of mechanical transmission. The method comprises the steps that engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters and spring parameters are obtained; according to the engine parameters, the clutch parameters, the load parameters, the lubricating oil parameters, the geometric parameters and the spring parameters, coupling iterative calculation is carried out by utilizing a joint process kinetic equation of a plurality of friction pairs of the clutch, and the time-varying friction torque and the time-varying slip speed of a joint spline are determined; and according to the time-varying friction torque and the time-varying slip speed, determining the abrasion loss of the tooth surface of the joint spline by utilizing a joint spline abrasion calculation model. According to the method, the accuracy of joint spline abrasion loss calculation can be improved.

Description

Technical Field

[0001] This application relates to the field of mechanical transmission, and in particular to a method, apparatus, equipment, medium, and product for determining the wear of spline engagement of a friction clutch. Background Technology

[0002] The engagement spline is a key component of the tail thrust clutch system in vertical takeoff and landing (VTOL) aircraft. It works in conjunction with the hydraulic system and friction pairs of the tail thrust clutch system to transmit the torque of the drive unit to the tail propeller. During the engagement process of the tail thrust clutch system, the engagement spline needs to undergo a relatively long sliding distance, inevitably resulting in sliding wear. Wear of the engagement spline increases the engagement impact of the tail drive system, reduces control accuracy, and thus affects the transmission performance of the entire system. Traditional calculation methods use a constant load torque to calculate the wear of the tail thrust clutch system; however, this method cannot consider the dynamic friction torque transmission process of multiple friction pairs in the tail thrust clutch system, and therefore cannot obtain accurate sliding wear and life prediction of the engagement spline. Therefore, a method that can accurately determine the wear of the engagement spline is needed. Summary of the Invention

[0003] The purpose of this application is to provide a method, apparatus, equipment, medium, and product for determining the wear of the spline of a friction clutch engagement, which can improve the accuracy of calculating the wear amount of the engagement spline.

[0004] To achieve the above objectives, this application provides the following solution:

[0005] In a first aspect, this application provides a method for determining the wear of the spline engagement of a friction clutch, including:

[0006] Obtain engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters;

[0007] Based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, coupled iterative calculations are performed using the dynamic equations of the engagement process of multiple friction pairs of the clutch to determine the time-varying friction torque and time-varying slip speed of the engagement spline.

[0008] The wear amount of the spline tooth surface is determined using the time-varying friction torque and the time-varying slip velocity through a spline wear calculation model.

[0009] In one embodiment, based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, coupled iterative calculations are performed using the dynamic equations of the engagement process of multiple friction pairs of the clutch to determine the time-varying friction torque and time-varying slip velocity of the engagement spline. Specifically, this includes:

[0010] Determine whether both the sliding displacement and angular displacement meet the accuracy threshold.

[0011] If so, based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, the n-degree-of-freedom axial dynamic equations and the 4-degree-of-freedom torsional vibration equations are simultaneously established. The Runge-Kutta method is used to perform coupled iterative calculations of sliding displacement and angular displacement to obtain the time-varying friction torque and time-varying slip velocity of the engaging spline. The dynamic equations for the engagement process of the multiple friction pairs of the clutch include the n-degree-of-freedom axial dynamic equations and the 4-degree-of-freedom torsional vibration equations.

[0012] If not, return "Get engine parameters, clutch parameters, load parameters, lubricant parameters, geometry parameters, and spring parameters".

[0013] In one embodiment, the wear amount of the spline tooth surface is determined using a spline wear calculation model based on the time-varying frictional torque and the time-varying slip velocity, specifically including:

[0014] Based on the time-varying friction torque, the time-varying normal contact load of the friction pair is obtained using the internal spline contact model of the friction plate and the external spline contact model of the dual steel plate.

[0015] The wear amount of the spline tooth surface is determined using a spline wear calculation model based on the time-varying normal contact load of the friction pair and the time-varying slip velocity.

[0016] In one embodiment, the engine parameters include the engine's actual output torque, actual speed, moment of inertia, and damping coefficient; the clutch parameters include the friction plate mass, the mass of the mating steel plate, the wear coefficient, the friction plate damping coefficient, the steel plate damping coefficient, the friction plate elastic modulus, the steel plate elastic modulus, the friction plate Poisson's ratio, and the steel plate Poisson's ratio; the load parameters include the load speed, resistance torque, moment of inertia, and damping coefficient; the lubricating oil parameters include the lubricating oil's ambient viscosity and ambient density; the geometric parameters include the initial clearance of the friction pair; and the spring parameters include the return spring stiffness and the release spring stiffness.

[0017] In one embodiment, it further includes:

[0018] Determine whether the wear exceeds 0.2 mm of the hardened layer depth on the spline tooth surface;

[0019] If yes, the spline is determined to be faulty; otherwise, the spline is determined to be not faulty.

[0020] In one embodiment, it further includes:

[0021] When a spline is determined to be in failure, the corresponding number of clutch engagements is the service life of the clutch engagement spline.

[0022] Secondly, this application provides a device for determining the wear of the spline of a friction clutch engagement, comprising:

[0023] The acquisition module is used to acquire engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters;

[0024] The coupled iterative calculation module is used to perform coupled iterative calculations based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, using the dynamic equations of the engagement process of multiple friction pairs of the clutch, to determine the time-varying friction torque and time-varying slip speed of the engagement spline;

[0025] The wear determination module is used to determine the wear amount of the spline tooth surface based on the time-varying friction torque and the time-varying slip velocity using a spline wear calculation model.

[0026] Thirdly, this application provides a computer device, including: a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the method for determining the wear of the engagement spline of the friction clutch.

[0027] Fourthly, this application provides a computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the method for determining the wear of the spline of the friction clutch engagement.

[0028] Fifthly, this application provides a computer program product, including a computer program that, when executed by a processor, implements the method for determining the wear of the spline of the friction clutch engagement.

[0029] According to the specific embodiments provided in this application, the following technical effects are disclosed:

[0030] This application provides a method, apparatus, equipment, medium, and product for determining the wear of engagement splines in a friction clutch. Based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, coupled iterative calculations are performed using the dynamic equations of the engagement process of multiple friction pairs in the clutch to determine the time-varying friction torque and time-varying slip velocity of the engagement spline. Based on the time-varying friction torque and time-varying slip velocity, the wear amount of the engagement spline tooth surface is determined using an engagement spline wear calculation model. By utilizing the dynamic equations of the engagement process of multiple friction pairs in the clutch, the transmission process of dynamic friction torque of multiple friction pairs in the push-pull clutch system is considered, thereby improving the accuracy of wear calculation. Attached Figure Description

[0031] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0032] Figure 1 This is a schematic diagram of the spline structure for clutch engagement;

[0033] Figure 2 This is a schematic diagram of the axial motion of the clutch with n degrees of freedom.

[0034] Figure 3 Schematic diagram of a method for determining spline wear in a friction clutch engagement;

[0035] Figure 4 This is a speed diagram showing the clutch engagement process;

[0036] Figure 5 This is a diagram showing the friction torque during clutch engagement.

[0037] Figure 6 This is a diagram showing the slip distances of each friction element in the clutch.

[0038] Figure 7 A diagram showing the average sliding wear of the clutch spline;

[0039] Figure 8 This is a diagram showing the wear life of the clutch spline.

[0040] Figure 9 This is a flowchart illustrating a method for determining the wear of splines in a friction clutch engagement.

[0041] Figure 10 A schematic diagram of the functional modules of a friction clutch engagement spline wear determination device;

[0042] Figure 11 This is a schematic diagram of the structure of a computer device. Detailed Implementation

[0043] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0044] To make the above-mentioned objectives, features and advantages of this application more apparent and understandable, the application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0045] In one exemplary embodiment, such as Figure 9 As shown, a method for determining the wear of splines in a friction clutch engagement is provided. This method is executed by a computer device, specifically a terminal or server, or both. In this embodiment, the method is described using a server as an example, and includes steps 901 to 903. Wherein:

[0046] Step 901: Obtain engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters;

[0047] Step 902: Based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, perform coupled iterative calculations using the dynamic equations of the engagement process of multiple friction pairs of the clutch to determine the time-varying friction torque and time-varying slip speed of the engagement spline;

[0048] Step 903: Determine the wear amount of the spline tooth surface using the spline wear calculation model based on the time-varying friction torque and the time-varying slip velocity.

[0049] By implementing steps 901 to 903 above, the dynamic friction torque transmission process of multiple friction pairs in the tail-push clutch system is considered using the dynamic equation of the engagement process of multiple friction pairs of the clutch, thereby improving the accuracy of wear calculation.

[0050] In an exemplary embodiment, based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, coupled iterative calculations are performed using the dynamic equations of the engagement process of multiple friction pairs of the clutch to determine the time-varying friction torque and time-varying slip speed of the engagement spline. Specifically, this includes:

[0051] Determine whether both the sliding displacement and angular displacement meet the accuracy threshold.

[0052] If so, based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, the n-degree-of-freedom axial dynamic equations and the 4-degree-of-freedom torsional vibration equations are simultaneously established. The Runge-Kutta method is used to perform coupled iterative calculations of sliding displacement and angular displacement to obtain the time-varying friction torque and time-varying slip velocity of the engaging spline. The dynamic equations for the engagement process of the multiple friction pairs of the clutch include the n-degree-of-freedom axial dynamic equations and the 4-degree-of-freedom torsional vibration equations.

[0053] If not, return "Get engine parameters, clutch parameters, load parameters, lubricant parameters, geometry parameters, and spring parameters".

[0054] In an exemplary embodiment, the wear amount of the spline tooth surface is determined using a spline wear calculation model based on the time-varying frictional torque and the time-varying slip velocity, specifically including:

[0055] Based on the time-varying friction torque, the time-varying normal contact load of the friction pair is obtained using the internal spline contact model of the friction plate and the external spline contact model of the dual steel plate; the time-varying normal contact load of the friction pair includes the normal contact load of the spline teeth of the dual steel plate and the normal contact load of the internal spline of the friction plate.

[0056] The wear amount of the spline tooth surface is determined using a spline wear calculation model based on the time-varying normal contact load and time-varying slip velocity of the friction pair. The wear amount of the spline tooth surface is the wear depth of the outer spline of the mating steel plate and the wear depth of the inner spline of the friction plate.

[0057] In an exemplary embodiment, the engine parameters include the engine's actual output torque, actual speed, moment of inertia, and damping coefficient; the clutch parameters include the friction plate mass, the mass of the mating steel plate, the wear coefficient, the friction plate damping coefficient, the steel plate damping coefficient, the friction plate elastic modulus, the steel plate elastic modulus, the friction plate Poisson's ratio, and the steel plate Poisson's ratio; the load parameters include the load speed, resistance torque, moment of inertia, and damping coefficient; the lubricating oil parameters include the lubricating oil's ambient viscosity and ambient density; the geometric parameters include the initial clearance of the friction pair; the spring parameters include the return spring stiffness and the release spring stiffness; the sliding displacement includes the sliding of the mating steel plate and the sliding displacement of the friction plate; the angular displacement includes the angular displacement of the mating steel plate and the angular displacement of the friction plate.

[0058] In one exemplary embodiment, the method for determining the wear of the spline engagement of a friction clutch further includes:

[0059] Determine whether the wear exceeds 0.2 mm of the hardened layer depth on the spline tooth surface;

[0060] If yes, the spline is determined to be faulty; otherwise, the spline is determined to be not faulty.

[0061] In one exemplary embodiment, the method for determining the wear of the spline engagement of a friction clutch further includes:

[0062] When spline failure is determined, the corresponding number of clutch engagements is considered the service life of the clutch engagement spline. By substituting the time-varying normal contact load and time-varying slip velocity into the spline wear calculation model, the wear depth of the spline teeth under a single engagement condition can be obtained. This allows us to determine the wear depth of each tooth on the internal and external engagement splines under different engagement numbers. Under continuous clutch engagement, if the cumulative wear depth of the spline teeth exceeds 0.2 mm of the hardened layer depth, the spline is considered to have failed. Therefore, when spline failure is determined by the wear depth reaching the hardened layer depth, the number of clutch engagements is the service life of the clutch engagement spline.

[0063] See the schematic diagram of the clutch engagement spline structure. Figure 1 The clutch engagement splines consist of internal splines on the friction plates and external splines on the mating steel plates. The internal splines on the friction plates mate with the external splines on the output shaft to form friction pair 1, while the external splines on the mating steel plates mate with the internal splines on the input shaft to form friction pair 2. When the clutch is not engaged, there is an initial gap between the friction plates and the mating steel plates, and they do not contact each other. When the clutch is engaged, the piston pushes the friction plates and mating steel plates axially, reducing the gap until contact occurs. During this process, sliding wear occurs on the internal splines on the friction plates and the external splines on the mating steel plates in friction pair 1. Under frequent clutch operation cycles, this sliding wear on the internal splines on the friction plates and the external splines on the mating steel plates will affect the clutch transmission performance.

[0064] See the schematic diagram of the axial motion of clutch n-degree of freedom. Figure 2 . Figure 2 (a) is a schematic diagram of the initial state of the clutch. Figure 2 (b) is a schematic diagram of the clutch engagement state. In the initial state, a release spring is installed between the clutch mating steel plates to maintain a consistent clearance between each mating steel plate. A friction plate is installed between two adjacent mating steel plates. Assuming the friction plate is positioned at the center of the two steel plates, the clearance between each friction plate and the mating steel plate is equal, defined as h0. In the clutch engagement state, the piston pushes each mating steel plate and friction plate axially, reducing the clearance between each mating steel plate and friction plate, defined as h1, h2, h3, ..., h n .

[0065] The axial dynamic equation of the clutch with n degrees of freedom is:

[0066]

[0067] In the formula, m s The mass of the paired steel sheet is expressed in kg; m. f The mass of the friction plate is expressed in kg. This represents the axial slip acceleration of the clutch, in m / s². 2 k represents the spring stiffness, N / m; Fp The piston is subjected to a pressure load, N; n represents the number of friction elements, F. aj The total axial load between each pair of steel plates and friction plates, where j = 1, 2, 3, ..., n, can be calculated using the following formula:

[0068] F a =(1-ζ)F h +ζF c

[0069] In the formula, ζ represents the ratio of actual contact area; F h Represents the hydrodynamic load, N; F c This represents the contact load on the micro-protrusion, in N. F. h and F c They are represented as follows:

[0070]

[0071] In the formula, p h Represents fluid dynamic pressure, N / m 2 ;p c Indicates the contact pressure of the micro-convexity, N / m 2 p h and p c They are represented as follows:

[0072]

[0073] In the formula, some variables are represented by A, B, and C to simplify the formula: A = φ r h 3 +12md, A, B, and C are all intermediate variables. Among them, p... h R is the average hydrodynamic pressure, r is the radius, r i r is the inner diameter. o p is the outer diameter. c For the contact pressure of the micro-protrusion, N is the density of the micro-protrusion, β is the radius of the micro-protrusion, σ is the root mean square of the comprehensive surface roughness, E' is the comprehensive elastic modulus, and φ is the micro-protrusion contact pressure. r ρ is the pressure flow rate, m is the friction lining permeability, d is the friction lining thickness, ρ is the lubricating oil density, ω1 is the friction plate rotation speed, ω2 is the steel plate rotation speed, μ is the lubricating oil dynamic viscosity, and φ is the friction oil dynamic viscosity. c For contact factor, the intermediate variable F 52 (σ / h) is p c The expanded representation of a formula in an expression can be expressed as:

[0074]

[0075] The time-varying slip distance x of the i-th friction element (friction plate or steel plate) iand time-varying slip velocity v i It can be represented as

[0076]

[0077] In the formula, i = 1, 2, 3, ..., n.

[0078] The torsional vibration equation of a 4-DOF clutch was established, written as:

[0079]

[0080] Where, I e , I i , I o , I L These represent the moments of inertia of the engine, the driving end of the clutch, the driven end of the clutch, and the load, respectively, in kg.m. 2 c e c i c o c L The damping values ​​are for the engine, the clutch driving end, the clutch driven end, and the load, respectively, in Ns / m; θ e ,θ i ,θ o ,θ L ω represents the angular displacement of the engine, clutch driving end, clutch driven end, and load, respectively, in rad; k1 and k2 are the torsional stiffness of drive shaft 1 and drive shaft 2, respectively, in Nm / rad; T e For driving torque, Nm; T c Friction torque, Nm; T L The load torque is Nm.

[0081] By combining equations (1) and (2), the time-varying friction torque and time-varying slip velocity of the spline can be obtained.

[0082] Based on spline contact analysis, the normal contact load F of the external spline teeth of the mating steel sheet is... s It can be written as:

[0083]

[0084] In the formula, Z s The number of external spline teeth for the paired steel sheet; r s The mean diameter of the outer spline of the paired steel sheet is m; α s The contact angle of the external spline of the paired steel sheet is °.

[0085] Friction plate internal spline normal contact load F f It can be written as:

[0086]

[0087] In the formula, Z f The number of external spline teeth for the paired steel sheet; r f The mean diameter of the outer spline of the paired steel sheet is m; α f The contact angle of the external spline of the paired steel sheet is °.

[0088] For the sliding friction condition of the spline, the Archard model is modified to determine the wear depth h of the tooth surface of the external spline of the mating steel sheet within the time range [t1, t2]. s for:

[0089]

[0090] In the formula, t is time (s); K is the wear coefficient; H is the tooth surface hardness; v is the sliding velocity (m / s); and A0 is the tooth surface contact area (m²). 2 The Archard wear model is specifically defined as dV / ds = K × F / H, where V is the wear volume, s is the slip distance, K is the wear coefficient, and H is the tooth surface hardness.

[0091] For the sliding friction condition of the spline, the Archard model is modified to determine the wear depth h of the spline tooth surface within the time range [t1, t2]. f for:

[0092]

[0093] In the formula, t is time (s); K is the wear coefficient; H is the tooth surface hardness; v is the sliding velocity (m / s); and A0 is the tooth surface contact area (m²). 2 .

[0094] The modified Archard wear model described above is used to calculate the tooth surface wear depth of each individual spline tooth on each friction plate or steel plate within a single engagement time. This allows for the determination of the tooth surface wear depth of each tooth on the internal and external engaging splines under different engagement cycles. If the wear exceeds 0.2 mm of the hardened layer depth on the spline tooth surface, the spline is considered to have failed. Finally, the clutch engagement spline life can be evaluated based on the number of engagements required to reach the hardened layer depth.

[0095] like Figure 3 As shown, this application also provides a method for determining the wear of the spline engagement of a friction clutch. The specific process in practical applications is as follows:

[0096] Step 1: Through analysis of the structure, materials, manufacturing process, and service environment of the tail-end clutch system, obtain engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters. Engine parameters include actual engine output torque, actual speed, moment of inertia, and damping coefficient; clutch parameters include friction plate mass, mating steel plate mass, wear coefficient, friction plate damping coefficient, steel plate damping coefficient, friction plate elastic modulus, steel plate elastic modulus, friction plate Poisson's ratio, and steel plate Poisson's ratio; load parameters include load speed, resistance torque, moment of inertia, and damping coefficient; lubricating oil parameters include ambient viscosity and ambient density; geometric parameters include initial clearance of the friction pair; and spring parameters include return spring stiffness and release spring stiffness.

[0097] Step 2: Based on the engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, establish the dynamic equations for the engagement process of multiple friction pairs of the clutch, including the n-degree-of-freedom axial dynamic equation and the 4-degree-of-freedom torsional vibration equation. Solve the n-degree-of-freedom axial dynamic equation and the 4-degree-of-freedom torsional vibration equation simultaneously using the Runge-Kutta method to obtain the time-varying friction torque and time-varying slip velocity of the engagement spline.

[0098] Specifically, based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, fluid mechanics and rough surface contact theory are used to solve for the clutch friction fluid dynamic pressure and micro-protrusion contact force. Then, based on the clutch friction fluid dynamic pressure and micro-protrusion contact force, the dynamic equations of the clutch's multiple friction pairs engagement process are constructed.

[0099] Step 3: Substitute the time-varying friction torque into the internal spline contact model of the friction plate as shown in formula (3) and the external spline contact model of the dual steel plate as shown in formula (4) to obtain the time-varying normal contact load of the friction pair.

[0100] Step 4: Substitute the time-varying normal contact load and time-varying slip velocity into the spline wear calculation model to obtain the wear amount of the spline tooth surface. This allows us to obtain the wear depth of each tooth of the spline under different engagement cycles. If the wear exceeds 0.2 mm of the hardened layer depth on the spline tooth surface, the spline is considered to have failed. Finally, based on the number of engagement cycles required to reach the hardened layer depth on the spline tooth surface, the life of the clutch engagement spline can be evaluated.

[0101] This application considers the transmission process of dynamic friction torque of multiple friction pairs in the tail-end clutch system. By using the axial engagement dynamic equation of multiple friction pairs and the torsional vibration equations of the engine, clutch drive end, clutch driven end, and load, the clutch slip displacement and angular displacement are coupled and iteratively calculated to obtain the time-varying friction torque of the engagement spline that conforms to the actual working conditions. Substituting the time-varying friction torque into the engagement spline wear model, the sliding wear of the engagement spline is obtained, which improves the accuracy of the calculation and can provide more accurate technical parameters for engagement spline parameter design and life estimation. Among them, the torsional vibration equations of the engine, clutch drive end, clutch driven end, and load refer to the 4-DOF clutch torsional vibration equation set, as shown in formula (2). This equation set considers the engine, clutch drive end, clutch driven end, and load.

[0102] This application provides a calculation example of slip wear on the spline of a clutch engagement. The geometric and material parameters of the clutch friction pair are shown in Table 1, and the lubricating oil parameters are shown in Table 2.

[0103] Table 1 Geometric and material parameters of the clutch friction pair

[0104]

[0105]

[0106] Table 2 Lubricating Oil Parameters

[0107] Dynamic viscosity at 40℃ (Pa.s) <![CDATA[Density (kg / m 3 )]]> lubricating oil 0.029 993

[0108] The speed and friction torque during clutch engagement are shown in the figure. Figure 4 , Figure 5 The speeds of the clutch's driving and driven ends reach the same level at 0.3843s and continue to accelerate to the target speed. The total clutch torque consists of fluid viscous torque and micro-cam contact torque. The total torque first increases linearly, then increases parabolically, finally exhibits oscillation, and finally decreases to zero.

[0109] The slip distance between the clutch mating steel plates and friction plates is shown in the figure. Figure 6 Spline sliding wear amount see Figure 7 Spline wear life see Figure 8 It can be seen that the lifespan of the mating steel plate 4 is the longest, and the lifespan of the friction plate 4 is the longest.

[0110] Based on the same inventive concept, this application also provides a friction clutch engagement spline wear determination device for implementing the above-described method for determining friction clutch engagement spline wear. The solution provided by this device is similar to the solution described in the above method; therefore, the specific limitations of one or more embodiments of the friction clutch engagement spline wear determination device provided below can be found in the limitations of the friction clutch engagement spline wear determination method described above, and will not be repeated here.

[0111] In one exemplary embodiment, such as Figure 10 As shown, a device for determining the wear of a friction clutch engagement spline includes:

[0112] The acquisition module 101 is used to acquire engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters;

[0113] The coupled iterative calculation module 102 is used to perform coupled iterative calculations based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters and spring parameters using the dynamic equations of the engagement process of multiple friction pairs of the clutch, to determine the time-varying friction torque and time-varying slip speed of the engagement spline;

[0114] Wear determination module 103 is used to determine the wear amount of the spline tooth surface based on the time-varying friction torque and the time-varying slip velocity using a spline wear calculation model.

[0115] In one exemplary embodiment, a computer device is provided, which may be a server or a terminal, and its internal structure diagram may be as follows. Figure 11 As shown, the computer device includes a processor, memory, input / output (I / O) interfaces, and a communication interface. The processor, memory, and I / O interfaces are connected via a system bus, and the communication interface is also connected to the system bus via the I / O interfaces. The processor provides computational and control capabilities. The memory includes non-volatile storage media and internal memory. The non-volatile storage media stores the operating system, computer programs, and a database. The internal memory provides the environment for the operation of the operating system and computer programs stored in the non-volatile storage media. The database stores data on the wear determination of friction clutch engagement splines. The I / O interfaces are used for information exchange between the processor and external devices. The communication interface is used for communication with external terminals via a network connection. When executed by the processor, the computer program implements a method for determining the wear of friction clutch engagement splines.

[0116] Those skilled in the art will understand that Figure 11The structures shown are merely block diagrams of some structures related to the present application and do not constitute a limitation on the computer device to which the present application is applied. Specific computer devices may include more or fewer components than shown in the figures, or combine certain components, or have different component arrangements. In an exemplary embodiment, a computer device is provided, including a memory and a processor. The memory stores a computer program, and the processor executes the computer program to implement the above-described method embodiments.

[0117] In one exemplary embodiment, a computer-readable storage medium is provided storing a computer program that, when executed by a processor, implements the above-described method embodiments.

[0118] In one exemplary embodiment, a computer program product is provided, including a computer program that, when executed by a processor, implements the above-described method embodiments.

[0119] It should be noted that the user information (including but not limited to user device information, user personal information, etc.) and data (including but not limited to data used for analysis, data stored, data displayed, etc.) involved in this application are all information and data authorized by the user or fully authorized by all parties, and the collection, use and processing of the relevant data must comply with relevant regulations.

[0120] In this application, all actions to acquire signals, information, or data are carried out in compliance with the relevant data protection laws and policies of the country where the location is situated, and with the authorization granted by the owner of the relevant device.

[0121] Those skilled in the art will understand that all or part of the processes in the methods of the above embodiments can be implemented by a computer program instructing related hardware. The computer program can be stored in a non-volatile computer-readable storage medium, and when executed, it can include the processes of the embodiments of the above methods. Any references to memory, databases, or other media used in the embodiments provided in this application can include at least one of non-volatile and volatile memory. Non-volatile memory can include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetic random access memory (MRAM), ferroelectric random access memory (FRAM), phase change memory (PCM), graphene memory, etc. Volatile memory can include random access memory (RAM) or external cache memory, etc. By way of illustration and not limitation, RAM can take many forms, such as Static Random Access Memory (SRAM) or Dynamic Random Access Memory (DRAM).

[0122] The databases involved in the embodiments provided in this application may include at least one type of relational database and non-relational database. Non-relational databases may include, but are not limited to, blockchain-based distributed databases. The processors involved in the embodiments provided in this application may be general-purpose processors, central processing units, graphics processing units, digital signal processors, programmable logic devices, quantum computing-based data processing logic devices, etc., and are not limited to these.

[0123] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0124] This document uses specific examples to illustrate the principles and implementation methods of this application. The descriptions of the above embodiments are only for the purpose of helping to understand the methods and core ideas of this application. Furthermore, those skilled in the art will recognize that, based on the ideas of this application, there will be changes in the specific implementation methods and application scope. Therefore, the content of this specification should not be construed as a limitation of this application.

Claims

1. A method for determining the wear of the spline engagement of a friction clutch, characterized in that, The method for determining the wear of the spline engagement of the friction clutch includes: Obtain engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters; Based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, coupled iterative calculations are performed using the dynamic equations of the engagement process of multiple friction pairs of the clutch to determine the time-varying friction torque and time-varying slip speed of the engagement spline. The wear amount of the spline tooth surface is determined using the time-varying friction torque and the time-varying slip velocity through a spline wear calculation model.

2. The method for determining the wear of the spline engagement of a friction clutch according to claim 1, characterized in that, Based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, coupled iterative calculations are performed using the dynamic equations of the clutch's multiple friction pairs engagement process to determine the time-varying friction torque and time-varying slip velocity of the engagement spline. Specifically, this includes: Determine whether both the sliding displacement and angular displacement meet the accuracy threshold. If so, based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, the n-degree-of-freedom axial dynamic equations and the 4-degree-of-freedom torsional vibration equations are simultaneously established. The Runge-Kutta method is used to perform coupled iterative calculations of sliding displacement and angular displacement to obtain the time-varying friction torque and time-varying slip velocity of the engaging spline. The dynamic equations for the engagement process of the multiple friction pairs of the clutch include the n-degree-of-freedom axial dynamic equations and the 4-degree-of-freedom torsional vibration equations. If not, return "Get engine parameters, clutch parameters, load parameters, lubricant parameters, geometry parameters, and spring parameters".

3. The method for determining the wear of the spline engagement of a friction clutch according to claim 1, characterized in that, The wear amount of the spline tooth surface is determined using a spline wear calculation model based on the time-varying friction torque and the time-varying slip velocity, specifically including: Based on the time-varying friction torque, the time-varying normal contact load of the friction pair is obtained using the internal spline contact model of the friction plate and the external spline contact model of the dual steel plate. The wear amount of the spline tooth surface is determined using a spline wear calculation model based on the time-varying normal contact load of the friction pair and the time-varying slip velocity.

4. The method for determining the wear of the spline engagement of a friction clutch according to claim 1, characterized in that, The engine parameters include the engine's actual output torque, actual speed, moment of inertia, and damping coefficient; the clutch parameters include the friction plate mass, the mass of the mating steel plate, the wear coefficient, the friction plate damping coefficient, the steel plate damping coefficient, the friction plate elastic modulus, the steel plate elastic modulus, the friction plate Poisson's ratio, and the steel plate Poisson's ratio; the load parameters include the load speed, resistance torque, moment of inertia, and damping coefficient; the lubricating oil parameters include the lubricating oil's ambient viscosity and ambient density; the geometric parameters include the initial clearance of the friction pair; and the spring parameters include the return spring stiffness and the release spring stiffness.

5. The method for determining the wear of the spline engagement of a friction clutch according to claim 1, characterized in that, Also includes: Determine whether the wear exceeds 0.2 mm of the hardened layer depth on the spline tooth surface; If yes, the spline is determined to be faulty; otherwise, the spline is determined to be not faulty.

6. The method for determining the wear of the spline engagement of a friction clutch according to claim 5, characterized in that, Also includes: When a spline is determined to be in failure, the corresponding number of clutch engagements is the service life of the clutch engagement spline.

7. A device for determining the wear of the spline engagement of a friction clutch, characterized in that, The friction clutch engagement spline wear determination device includes: The acquisition module is used to acquire engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters; The coupled iterative calculation module is used to perform coupled iterative calculations based on engine parameters, clutch parameters, load parameters, lubricating oil parameters, geometric parameters, and spring parameters, using the dynamic equations of the engagement process of multiple friction pairs of the clutch, to determine the time-varying friction torque and time-varying slip speed of the engagement spline; The wear determination module is used to determine the wear amount of the spline tooth surface based on the time-varying friction torque and the time-varying slip velocity using a spline wear calculation model.

8. A computer device, comprising: A memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that the processor executes the computer program to implement the method for determining the wear of the spline of the friction clutch engagement as described in any one of claims 1-6.

9. A computer-readable storage medium having a computer program stored thereon, characterized in that, When executed by a processor, the computer program implements the method for determining the wear of the spline of the friction clutch engagement as described in any one of claims 1-6.

10. A computer program product, comprising a computer program, characterized in that, When executed by a processor, the computer program implements the method for determining the wear of the spline of the friction clutch engagement as described in any one of claims 1-6.

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