Method and system for detecting and warning the phenomenon of friction pair dislocation of hydraulic viscous clutch

Abstract

The present invention belongs to the technical field of liquid viscous clutch, and specifically discloses a method and system for detecting and warning the phenomenon of belt-discharging in the friction pair of a liquid viscous clutch, the method comprising the following steps: S1, collecting the structural parameters of the groove friction pair; S2, dividing a plurality of micro-element rings on the groove friction pair to form a plurality of grids; S3, using the structural parameters of the groove friction pair, respectively calculating the radial groove belt-discharging torque and the boss area belt-discharging torque of the friction pair; S4, obtaining the total belt-discharging torque of a single friction pair; S5, calculating the sum of the belt-discharging torques of all friction pairs in the friction pair space area, and obtaining the total output torque of the belt-discharging considering the uneven gap; S6, comparing the total output torque of the belt-discharging with a preset value, judging the degree of the belt-discharging phenomenon, and outputting a warning signal according to the belt-discharging degree information. By adopting this technical solution, the total output torque of the belt-discharging can be accurately obtained, and the severity of the belt-discharging phenomenon can be judged to give a timely warning.

Description

Technical Field

[0001] The invention belongs to the technical field of liquid-viscous clutches, and relates to a method and system for detecting and warning the pull-out phenomenon of a friction pair of a liquid-viscous clutch. Background Art

[0002] As the core component of shift control, the hydroviscous clutch is composed of multiple ring-shaped dual plates and friction plates arranged alternately with each other. It is widely used in high-power fans, military heavy-duty vehicles, and engineering machinery transmission devices. When the hydroviscous clutch is in the separation process or separation state, there is a speed difference between the friction plate and the dual plate. Due to the viscosity of the cooling lubricating oil in the gap of the friction pair, the friction element cannot be completely separated, thus generating a pull-out torque. When the pull-out phenomenon is serious, not only the transmission component cannot operate normally, but it may even cause the friction pair of the hydroviscous clutch to heat up, burn black, warp and deform, and even lose its function.

[0003] In response to the phenomenon of liquid-viscous clutch belt-rowing, a variety of belt-row torque models have been proposed, such as radial grooves, radial annular grooves, square grooves and spiral grooves. The existing belt-row torque models of grooved friction pairs are all analytical expressions. The analytical formulas are difficult to derive and have low universality. They cannot provide early warning for friction plate belt-row failures, resulting in untimely maintenance of friction elements and delayed equipment operation or direct damage to the equipment. Summary of the invention

[0004] The object of the present invention is to provide a method and system for detecting and warning the pull-out phenomenon of the friction pair of a fluid-viscous clutch, accurately obtaining the total torque output by the pull-out, and judging the severity of the pull-out phenomenon so as to provide a timely warning.

[0005] In order to achieve the above object, the basic scheme of the present invention is: a method for detecting and warning the friction pair banding phenomenon of a fluid-viscous clutch, comprising the following steps:

[0006] S1, collect the structural parameters of the groove friction pair;

[0007] S2, based on the grooves and bosses on the groove friction pair, multiple micro-element rings are divided on the groove friction pair to form multiple grids;

[0008] S3, for the radial groove and boss area on the friction pair, using the structural parameters of the groove friction pair, calculate the radial groove belt torque and boss area belt torque of the friction pair respectively;

[0009] S4, integrating and calculating the radial groove row torque and the boss area row torque of the friction pair to obtain the total row torque of the single friction pair;

[0010] S5, using the uneven coefficients between multiple friction pairs to characterize the actual state of the gaps between multiple friction pairs, calculate the sum of the belt row torques of all friction pairs in the friction pair space area, and obtain the total belt row output torque considering the uneven gaps;

[0011] S6, comparing the total belt-displacement output torque with a preset value, determining the extent of the belt-displacement phenomenon, and outputting a warning signal according to the belt-displacement extent information.

[0012] The working principle and beneficial effects of this basic scheme are as follows: this scheme adopts the idea of ​​discrete integration, and according to the groove form, geometric parameters and structural parameters of the friction pair, the groove friction pair is discretized into micro-rings, and the deflection of the friction element, the oil film shrinkage under high speed difference and the uneven distribution of multiple friction pairs are considered. The deflection state of the friction pair under low speed difference, the oil film gap under high speed difference and the influence coefficient of the uneven gap of multiple friction pairs are calculated, and the friction pair belt torque of the liquid-viscous clutch considering the uneven gap is obtained. It is suitable for a variety of groove forms and can obtain a more accurate actual working state of the liquid-viscous clutch, so as to accurately judge the severity of the belt-displacement phenomenon for timely warning.

[0013] Furthermore, the structural parameters of the groove friction pair include the center o of the friction pair, the inner diameter r1 of the friction pair, the outer diameter r2 of the friction pair; the annular groove groove width a, the annular groove boss width b, the radial groove width c, the groove depth h c , the center angle θ1 corresponding to the radial groove and the center angle θ2 corresponding to the fan-shaped boss.

[0014] Obtain appropriate parameters for subsequent use.

[0015] Furthermore, taking the center o of the friction pair as the origin, a circular arc radial groove friction pair coordinate system is established, and the groove friction pair is meshed with step sizes a and b in the radial direction of the coordinate system.

[0016] Dividing the coordinate system facilitates subsequent positioning and calculation.

[0017] Furthermore, the method for calculating the radial groove strip torque in the grid area where the micro-ring is located is as follows:

[0018] Take a microelement ring at the oil film radius r and calculate the oil film gap h considering the influence of the deflection state under low speed difference according to the position of the grid area. b ;

[0019] h b =h0+rsinαcosγ

[0020] Among them, h0 is the initial oil film gap; r is the distance between the micro-ring and the center of the friction pair o; α is the deflection angle; γ is the position angle of the micro-ring;

[0021] According to the friction pair structure and flow parameters, calculate the friction pair oil film shrinkage gap h under high speed difference a :

[0022]

[0023] Then calculate the equivalent oil film outer diameter R of the friction pair s :

[0024]

[0025] Where ρ is the oil density; h0 is the initial oil film gap; h a Q is the shrinkage clearance of the friction pair oil film; a is the theoretical flow rate; Q is the actual flow rate; r1 is the inner diameter of the friction pair; r2 is the outer diameter of the friction pair;

[0026] Take a micro-circular area dA=rθ1d r at the radius r of the oil film in the θ1 region, and its shear stress is expressed as:

[0027]

[0028] Among them, θ1 is the central angle corresponding to the radial groove, μ is the dynamic viscosity of the lubricating oil; ω1 is the rotation speed of the friction pair; ω2 is the rotation speed of the dual plate; r is the distance between the micro-ring and the center o of the friction pair; δ1 is the initial oil film thickness at the radial groove and the circular groove;

[0029] The overall oil film transmission belt torque of the radial groove in the θ1 region is:

[0030]

[0031] Among them, M 1_c is the radial groove row torque; μ is the dynamic viscosity of the lubricating oil; ω s is the critical speed; δ1 is the initial oil film thickness at the radial groove and the arc groove; R s is the equivalent oil film radius; h c The groove depth.

[0032] The deflection state of the friction element under low speed difference and the oil film contraction characteristics under high speed difference are analyzed to better simulate the influence of the oil film gap between the friction pairs of the liquid-viscous clutch on the belt torque.

[0033] Furthermore, the method for calculating the belt torque of the boss area within the grid area where the micro-element ring is located is as follows:

[0034] Calculate the torque transmitted by the boss and groove at the angle θ2, and judge whether the equivalent oil film outer diameter is located at the boss or the groove. There are three cases;

[0035] Number of bosses: num_t = floor[(R s / 2-r1 / 2) / b];

[0036] Number of grooves: num_c = floor[(R s / 2-r1 / 2) / (b+a)];

[0037] Among them, R s is the equivalent oil film radius; θ2 is the central angle corresponding to the fan-shaped boss; r1 is the inner diameter of the friction pair; a is the width of the annular groove; b is the width of the annular groove boss;

[0038] The first case: if num_t = n, the equivalent oil film outer diameter is located at the boss; and num_t = num_c = 0, indicating that the equivalent oil film outer diameter is located on the first boss near the inner diameter r1. At this time:

[0039]

[0040] M 2_c =0

[0041] Among them, M 2_t M is the displacement torque at the boss; 2_c is the annular groove belt torque; μ is the dynamic viscosity of the lubricating oil; ω1 is the friction pair speed; ω2 is the dual plate speed; ω s is the critical speed; r is the distance between the microelement ring and the center o of the friction pair;

[0042] The second case: If num_t = num_c ≠ 0, it means that the equivalent oil film outer diameter is at least located at the second boss near the inner diameter. At this time:

[0043]

[0044]

[0045] Among them, M 2_t_yu is the boss row torque between the last boss starting boundary and the equivalent oil film radius; i is the number of bosses;

[0046] The third case: If num_t>num_c, it means that the equivalent oil film radius is located at the groove and contains at least one boss close to the inner diameter.

[0047]

[0048]

[0049]

[0050] Among them, M 2_c_yu It is the annular groove row torque from the last groove starting boundary to the equivalent oil film radius.

[0051] The belt torque in the boss area is calculated in a targeted manner, which can be adapted to various situations and is convenient for use.

[0052] Furthermore, the method for obtaining the total torque of a single friction pair is as follows:

[0053] In the first case, the total torque of a single friction pair is:

[0054] M sum =M 1_c +M 2_t

[0055] Among them, M sum M is the total torque of a single friction pair; 1_c M is the radial groove belt row torque; 2_t It is the displacement torque at the boss;

[0056] Second case:

[0057] M sum =M 1_c +M 2_t +M 2_t_yu +M 2_c

[0058] Among them, M 2_t_yu M is the boss row torque between the last boss starting boundary and the equivalent oil film radius; 2_c It is the annular groove belt row torque;

[0059] The third case:

[0060] M sum =M 1_c +M 2_t +M 2_c +M 2_c_yu

[0061] Among them, M 2_c_yu It is the annular groove row torque from the last groove starting boundary to the equivalent oil film radius.

[0062] According to different situations, the total torque of a single friction pair is calculated, which is simple to operate and easy to use.

[0063] Furthermore, the method for obtaining the total output torque of the belt row considering the uneven gap is:

[0064] For N friction pairs, calculate the unevenness coefficient ζ of each pair i Sum the torque M of multiple friction pairs. 总 for:

[0065]

[0066] M 总 =Nζ i M sum

[0067] Where h0 is the initial oil film gap; h a is the shrinkage clearance of the friction pair oil film; i is the number of bosses, j represents the jth friction pair; N is the total number of friction pairs; M sum It is the total torque of a single friction pair.

[0068] The calculation operation is simple and easy to use.

[0069] The present invention also provides a liquid-viscous clutch friction pair belt-displacement phenomenon detection and early warning system, comprising a data acquisition module, a processing module and an early warning module, wherein the data acquisition module is used to collect structural parameters of the groove friction pair, and the output end of the data acquisition module is connected to the processing module, and the processing module executes the method described in the present invention and outputs a belt-displacement phenomenon detection and early warning signal to the control end of the early warning module.

[0070] The system uses a processing module to obtain the total torque output by the belt in the friction pair space area in order to accurately understand the actual working state of the liquid-viscous clutch, thereby judging the severity of the belt phenomenon, so that the early warning module can issue an early warning signal in time for timely processing and maintenance. BRIEF DESCRIPTION OF THE DRAWINGS

[0071] Figure 1 It is a schematic flow chart of the method for detecting and warning the friction pair belt displacement phenomenon of the liquid-viscous clutch of the present invention;

[0072] Figure 2 It is a structural schematic diagram of the circular arc radial groove friction pair of the method for detecting and warning the belt-draining phenomenon of the friction pair of the liquid-viscous clutch of the present invention. DETAILED DESCRIPTION

[0073] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0074] In the description of the present invention, it is necessary to understand that the terms "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the present invention.

[0075] In the description of the present invention, unless otherwise specified and limited, it should be noted that the terms "installed", "connected" and "connected" should be understood in a broad sense. For example, it can be a mechanical connection or an electrical connection, or it can be the internal connection between two components. It can be a direct connection or an indirect connection through an intermediate medium. For ordinary technicians in this field, the specific meanings of the above terms can be understood according to the specific circumstances.

[0076] The present invention discloses a method for detecting and warning the phenomenon of friction pair stripping in a fluid-viscous clutch, which takes into account the deflection of friction elements under low speed difference, the shrinkage of oil film under high speed difference, and the uneven distribution of multiple pairs of friction plates, and can simultaneously meet the requirements of friction pair stripping torque detection under different groove forms or structural parameters. Figure 1 As shown, this method includes the following steps:

[0077] S1, collects the structural parameters of the groove friction pair; for example, the arc radial groove friction pair, such as Figure 2 As shown, the structural parameters of the groove friction pair include the center o of the friction pair, the inner diameter r1 of the friction pair, the outer diameter r2 of the friction pair; the width a of the annular groove, the width b of the annular groove boss, the width c of the radial groove, and the groove depth h c , the central angle θ1 corresponding to the radial groove and the central angle θ2 corresponding to the fan-shaped boss. With the center o of the friction pair as the origin, the arc radial groove friction pair coordinate system is established, and the groove friction pair is meshed with steps a and b in the radial direction of the coordinate system. The finer the meshing, the higher the solution accuracy.

[0078] S2, based on the grooves and bosses on the groove friction pair, multiple micro-rings are divided on the groove friction pair to form multiple grids; the idea of ​​differential discrete integral is adopted to discretize the friction pairs with different groove forms into micro-rings;

[0079] S3, for the radial groove and boss areas on the friction pair, the structural parameters of the groove friction pair are used to calculate the radial groove belt torque and boss area belt torque of the friction pair respectively; based on Newton's internal friction law, considering the influence of the clearance reduction caused by the deflection and oil film shrinkage, the output torque of each microelement ring belt row of the friction pair is calculated;

[0080] S4, integrating and calculating the radial groove row torque and the boss area row torque of the friction pair to obtain the total row torque of the single friction pair;

[0081] S5, using the uneven coefficients between multiple friction pairs to characterize the actual state of the gaps between multiple friction pairs, calculate the sum of the belt row torques of all friction pairs in the friction pair space area, and obtain the total belt row output torque considering the uneven gaps;

[0082] S6, compare the total torque output by the belt arrangement with the preset value, judge the degree of the belt displacement phenomenon, and output a warning signal according to the belt displacement degree information. Compare the total torque output by the belt arrangement with the preset value to judge whether the belt arrangement is abnormal. If the total torque output by the belt arrangement exceeds 1.5 times the preset value, it means that the belt arrangement is abnormal.

[0083] In a preferred embodiment of the present invention, the method for calculating the torque of the radial groove strip in the grid area where the micro-element ring is located is as follows:

[0084] Take a microelement ring at the oil film radius r and calculate the oil film gap h considering the influence of the deflection state under low speed difference according to the position of the grid area. b ;

[0085] h b =h0+rsinαcosγ

[0086] Among them, h0 is the initial oil film gap, in m; r is the distance between the micro-ring and the center o of the friction pair, in m; α is the deflection angle, in °; γ is the position angle of the micro-ring, in °;

[0087] According to the friction pair structure and flow parameters, calculate the friction pair oil film shrinkage gap h under high speed difference a :

[0088]

[0089] Then calculate the equivalent oil film outer diameter R of the friction pair s :

[0090]

[0091] Where ρ is the oil density; h0 is the initial oil film gap; h a is the shrinkage clearance of the friction pair oil film, in m; Q a is the theoretical flow rate, in L / min; Q is the actual flow rate, in L / min; r1 is the inner diameter of the friction pair, in m; r2 is the outer diameter of the friction pair, in m;

[0092] Take a micro-circular area at the radius r of the oil film in the θ1 region The shear stress is expressed as:

[0093]

[0094] Among them, θ1 is the central angle corresponding to the radial groove, μ is the dynamic viscosity of the lubricating oil (Pa·s); ω1 is the rotation speed of the friction pair, in r / min; ω2 is the rotation speed of the dual plate, in r / min; r is the distance between the micro-ring and the center o of the friction pair, in m; δ1 is the initial oil film thickness at the radial groove and the circular groove, in m;

[0095] The overall oil film transmission belt torque of the radial groove in the θ1 region is:

[0096]

[0097] Among them, M 1_c is the radial groove row torque, in N·m; μ is the dynamic viscosity of the lubricating oil, in Pa·s; ω s is the critical speed, in r / min; δ1 is the initial oil film thickness at the radial groove and arc groove, in m; R s is the equivalent oil film radius, in m; h c is the groove depth, in m.

[0098] In a preferred embodiment of the present invention, the method for calculating the row torque of the boss area within the grid area where the micro-element ring is located is as follows:

[0099] Once the friction pair structure and groove parameters are determined, the position coordinates of the groove and boss are determined. When calculating the torque transmitted by the boss and groove within the θ2 angle, it is necessary to determine whether the equivalent oil film outer diameter is located at the boss or the groove. There are three situations:

[0100] Number of bosses: num_t = floor[(R s / 2-r1 / 2) / b];

[0101] Number of grooves: num_c = floor[(R s / 2-r1 / 2) / (b+a)];

[0102] Among them, R s is the equivalent oil film radius, in m; θ2 is the central angle corresponding to the fan-shaped boss; r1 is the inner diameter of the friction pair, in m; a is the width of the annular groove, in m; b is the width of the annular groove boss, in m;

[0103] The first case: if num_t = n, the equivalent oil film outer diameter is located at the boss; and num_t = num_c = 0, indicating that the equivalent oil film outer diameter is located on the first boss near the inner diameter r1. At this time:

[0104]

[0105] M 2_c =0

[0106] Among them, M 2_t is the displacement torque at the boss, in N·m; M 2_c is the annular groove belt torque, in N·m; μ is the dynamic viscosity of the lubricating oil, in Pa·s; ω1 is the friction pair speed; ω2 is the dual plate speed; ωs is the critical speed, generally 1000r / min; r is the distance between the micro-ring and the center o of the friction pair, in m;

[0107] The second case: If num_t = num_c ≠ 0, it means that the equivalent oil film outer diameter is at least located at the second boss near the inner diameter. At this time:

[0108]

[0109]

[0110]

[0111] Among them, M 2_t_yu is the boss row torque between the last boss starting boundary and the equivalent oil film radius, in N·m; i is the number of bosses; ω s is the critical speed, generally 4500r / min;

[0112] The third case: If num_t>num_c, it means that the equivalent oil film radius is located at the groove and contains at least one boss close to the inner diameter.

[0113]

[0114]

[0115]

[0116] Among them, M 2_c_yu is the annular groove row torque from the last groove starting boundary to the equivalent oil film radius, in N·m; ω s It is the critical speed, generally 1000r / min.

[0117] More preferably, the method for obtaining the total torque of a single friction pair is as follows:

[0118] In the first case, the total torque of a single friction pair is:

[0119] M sum =M 1_c +M 2_t

[0120] Among them, M sum is the total torque of a single friction pair, in N·m; M 1_c is the radial groove belt row torque, in N·m; M 2_t is the displacement torque at the boss, in N·m;

[0121] Second case:

[0122] M sum =M 1_c +M 2_t +M 2_t_yu +M 2_c

[0123] Among them, M 2_t_yu M is the boss row torque between the last boss starting boundary and the equivalent oil film radius, in N·m; 2_c is the annular groove belt row torque, in N·m;

[0124] The third case:

[0125] M sum =M 1_c +M 2_t +M 2_c +M 2_c_yu

[0126] Among them, M 2_c_yu It is the annular groove row torque from the last groove starting boundary to the equivalent oil film radius, in N·m.

[0127] In a preferred embodiment of the present invention, a method for obtaining the total output torque of the belt row taking into account uneven gaps is as follows:

[0128] For N friction pairs, calculate the unevenness coefficient ζ of each pair i Sum the torque M of multiple friction pairs. 总 for:

[0129]

[0130] M 总 =Nζ i M sum

[0131] Where h0 is the initial oil film gap; h a is the shrinkage clearance of the friction pair oil film, in m; i is the number of bosses, j represents the jth friction pair; N is the total number of friction pairs; M sum It is the total torque of a single friction pair, in N·m.

[0132] The present invention also provides a liquid-viscous clutch friction pair belt-displacement phenomenon detection and early warning system, comprising a data acquisition module, a processing module and an early warning module, wherein the data acquisition module is used to collect structural parameters of the groove friction pair, and the output end of the data acquisition module is connected to the processing module, and the processing module executes the method described in the present invention and outputs a belt-displacement phenomenon detection and early warning signal to the control end of the early warning module.

[0133] The system uses a processing module to obtain the total torque output by the belt in the friction pair space area in order to accurately understand the actual working state of the liquid-viscous clutch, thereby judging the severity of the belt phenomenon, so that the early warning module can issue an early warning signal in time for timely processing and maintenance.

[0134] In the description of this specification, the description with reference to the terms "one embodiment", "some embodiments", "examples", "specific examples", or "some examples" means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0135] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A method for detecting and warning the phenomenon of friction pair displacement of a fluid-viscous clutch, characterized in that: The steps include: S1, collect the structural parameters of the groove friction pair; S2, based on the grooves and bosses on the groove friction pair, multiple micro-element rings are divided on the groove friction pair to form multiple grids; S3, for the radial groove and boss area on the friction pair, using the structural parameters of the groove friction pair, calculate the radial groove belt torque and boss area belt torque of the friction pair respectively; S4, integrating and calculating the radial groove row torque and the boss area row torque of the friction pair to obtain the total row torque of the single friction pair; S5, using the uneven coefficients between multiple friction pairs to characterize the actual state of the gaps between multiple friction pairs, calculate the sum of the belt row torques of all friction pairs in the friction pair space area, and obtain the total belt row output torque considering the uneven gaps; S6, comparing the total torque output by the belt displacement with a preset value, determining the degree of the belt displacement phenomenon, and outputting a warning signal according to the belt displacement degree information; The structural parameters of the groove friction pair include the center o of the friction pair, the inner diameter r1 of the friction pair, the outer diameter r2 of the friction pair; the width a of the annular groove, the width b of the annular groove boss, the width c of the radial groove, and the groove depth h. c , the central angle θ1 corresponding to the radial groove and the central angle θ2 corresponding to the fan-shaped boss; Taking the center o of the friction pair as the origin, establish the arc radial groove friction pair coordinate system, and mesh the groove friction pair with step sizes a and b in the radial direction of the coordinate system; The method for calculating the radial groove strip torque in the grid area where the micro-element ring is located is as follows: Take a microelement ring at the oil film radius r and calculate the oil film gap h considering the influence of the deflection state under low speed difference according to the position of the grid area. b ; h b =h0+r sinαcosγ Among them, h0 is the initial oil film gap; r is the distance between the micro-ring and the center of the friction pair o; α is the deflection angle; γ is the position angle of the micro-ring; According to the friction pair structure and flow parameters, calculate the friction pair oil film shrinkage gap h under high speed difference a : Then calculate the equivalent oil film outer diameter R of the friction pair s : Where ρ is the oil density; h0 is the initial oil film gap; h a Q is the shrinkage clearance of the friction pair oil film; a is the theoretical flow rate; Q is the actual flow rate; r1 is the inner diameter of the friction pair; r2 is the outer diameter of the friction pair; Take a micro-circular area at the radius r of the oil film in the θ1 region The shear stress is expressed as: Among them, θ1 is the central angle corresponding to the radial groove, μ is the dynamic viscosity of the lubricating oil; ω1 is the rotation speed of the friction pair; ω2 is the rotation speed of the dual plate; r is the distance between the micro-ring and the center o of the friction pair; δ1 is the initial oil film thickness at the radial groove and the circular groove; The overall oil film transmission belt torque of the radial groove in the θ1 region is: Among them, M 1_c is the radial groove row torque; μ is the dynamic viscosity of the lubricating oil; ω s is the critical speed; δ1 is the initial oil film thickness at the radial groove and the arc groove; R s is the equivalent oil film radius; h c The groove depth.

2. The method for detecting and warning the friction pair displacement phenomenon of a fluid-viscous clutch as claimed in claim 1, characterized in that: The method for calculating the row torque of the boss area within the grid area where the microelement ring is located is as follows: Calculate the torque transmitted by the boss and groove at the angle θ2, and judge whether the equivalent oil film outer diameter is located at the boss or the groove. There are three cases; Number of bosses: num_t = floor[(R s / 2-r1 / 2) / b]; Number of grooves: num_c = floor[(R s / 2-r1 / 2) / (b+a)]; Among them, R s is the equivalent oil film radius; θ2 is the central angle corresponding to the fan-shaped boss; r1 is the inner diameter of the friction pair; a is the width of the annular groove; b is the width of the annular groove boss; The first case: if num_t = num_c, the equivalent oil film outer diameter is located at the boss; and num_t = num_c = 0, indicating that the equivalent oil film outer diameter is located on the first boss near the inner diameter r1. At this time: M2_c=0 Among them, M 2_t M is the displacement torque at the boss; 2_c is the annular groove belt torque; μ is the dynamic viscosity of the lubricating oil; ω1 is the friction pair speed; ω2 is the dual plate speed; ω s is the critical speed; r is the distance between the microelement ring and the center o of the friction pair; The second case: If num_t = num_c ≠ 0, it means that the equivalent oil film outer diameter is at least located at the second boss near the inner diameter. At this time: Among them, M 2_t_yu is the boss row torque between the last boss starting boundary and the equivalent oil film radius; i is the number of bosses; The third case: If num_t>num_c, it means that the equivalent oil film radius is located at the groove and contains at least one boss close to the inner diameter. Among them, M 2_c_yu It is the annular groove row torque from the last groove starting boundary to the equivalent oil film radius.

3. The method for detecting and warning the friction pair displacement phenomenon of a fluid-viscous clutch as claimed in claim 2, characterized in that: The method to obtain the total torque of a single friction pair is as follows: In the first case, the total torque of a single friction pair is: M sum =M 1_c +M 2_t Among them, M sum M is the total torque of a single friction pair; 1_c M is the radial groove belt row torque; 2_t It is the belt displacement torque at the boss; Second case: M sum =M 1_c +M 2_t +M 2_t_yu +M 2_c Among them, M 2_t_yu M is the boss row torque between the last boss starting boundary and the equivalent oil film radius; 2_c It is the annular groove belt row torque; The third case: M sum =M 1_c +M 2_t +M 2_c +M 2_c_yu Among them, M 2_c_yu It is the annular groove row torque from the last groove starting boundary to the equivalent oil film radius.

4. The method for detecting and warning the friction pair displacement phenomenon of a fluid-viscous clutch as claimed in claim 1, characterized in that: The method to obtain the total output torque of the belt row considering uneven gap is: For N friction pairs, calculate the unevenness coefficient ζ of each pair i Sum the torque M of multiple friction pairs. 总 for: M 总 =Nζ i M sum Where h0 is the initial oil film gap; h a is the shrinkage clearance of the friction pair oil film; i is the number of bosses, j represents the jth friction pair; N is the total number of friction pairs; M sum It is the total torque of a single friction pair.

5. A hydraulic clutch friction pair belt displacement phenomenon detection and early warning system, characterized in that: It includes a data acquisition module, a processing module and an early warning module. The data acquisition module is used to collect structural parameters of the groove friction pair. The output end of the data acquisition module is connected to the processing module. The processing module executes the method described in one of claims 1-4 and outputs a belt-row phenomenon detection early warning signal to the control end of the early warning module.

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