A heat dissipation system and method applied to an air switch cabinet

Abstract

The application discloses a heat dissipation system and method applied to an air switch cabinet, and particularly relates to the technical field of switch cabinet heat dissipation, and is used for solving the problem of local temperature rise fluctuation caused by unstable thermal resistance of the connecting interface between a radiator and a conductive element in a continuous ship vibration environment; the heat dissipation system is characterized in that the ship vibration of the installation position of the switch cabinet is monitored in real time to extract the main frequency band and the phase angle of the vibration, the dynamic compensation parameters are determined based on the frequency domain overlap factor and the phase lag angle amplitude of heat conduction, the direction-optimized elastic heat-conduction gasket is arranged between the radiator and the busbar, the axial pre-tightening force which is periodically adjusted with the phase angle is applied, the thermal resistance change rate of the phase angle positions of the wave crest and the wave trough is synchronously measured, and the compensation parameters are updated when the thermal resistance change rate exceeds the standard, so that the dynamic stability and adaptive control of the heat dissipation interface are realized.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of switch cabinet heat dissipation, more particularly, to a heat dissipation system and method applied to an air switch cabinet. BACKGROUND

[0002] Air-insulated switch cabinets are widely used in ship power distribution systems as core equipment for power distribution. Such switch cabinets are usually deployed in enclosed spaces such as engine rooms or power distribution rooms, and are subjected to low-frequency mechanical vibrations transmitted by the ship's main engine and propeller for a long time. To control the temperature rise of heat-generating components such as busbars and circuit breakers in the cabinet, the existing technology mainly relies on natural convection heat dissipation structures (such as rigid bolt connections of heat dissipation fins and busbars) or forced air cooling systems. Such designs have a mature engineering application basis in land-based fixed scenarios.

[0003] However, in a continuous ship vibration environment, the mechanical connection interface between the heat sink and the conductive element is prone to periodic micro-deformation, which significantly increases the instability of the contact heat conduction path. This uncontrollable mutation of the interface thermal resistance poses a risk of abnormal fluctuations in local temperature rise in critical heat-generating areas during operation. SUMMARY

[0004] To overcome the above-mentioned defects of the prior art, the present application provides a heat dissipation system and method applied to an air switch cabinet to solve the problems raised in the background art.

[0005] To achieve the above-mentioned purpose, the present application provides the following technical solutions:

[0006] A heat dissipation method applied to an air switch cabinet, comprising the following steps:

[0007] S1, real-time monitoring of ship vibration at the installation position of the switch cabinet, extraction of the main frequency band and phase angle of the vibration;

[0008] S2, based on the frequency domain overlap factor of the main frequency band and the natural frequency of the heat sink, and the amplitude of the thermal conduction phase lag angle, determining the dynamic compensation parameters of the connection interface between the heat sink and the busbar;

[0009] S3, an elastic heat-conducting gasket is arranged between the heat sink and the busbar, the elastic heat-conducting gasket is selected according to the compression and rebound characteristics index in the dynamic compensation parameters, and the long axis direction is perpendicular to the maximum displacement direction of the phase angle;

[0010] S4, an axial pre-tightening force is applied to the fastening bolt of the heat sink, which is generated according to the pre-tightening force adjustment coefficient in the dynamic compensation parameters, and the axial pre-tightening force is adjusted periodically according to the phase angle;

[0011] S5, synchronously measure the transient thermal resistance value of the interface between the heat sink and the busbar at the crest phase angle position and the trough phase angle position of the vibration main frequency band, and calculate the thermal resistance change rate from the adjacent crest phase angle position to the trough phase angle position;

[0012] S6, when the thermal resistance change rate exceeds the dynamic response tolerance threshold, update the pre-tightening force adjustment coefficient and the compression resilience characteristic index.

[0013] Further, the ship vibration at the switch cabinet installation position is monitored in real time, and the vibration main frequency band and the phase angle are extracted, including:

[0014] The ship vibration signal at the switch cabinet installation position is collected through a three-axis acceleration sensor;

[0015] The ship vibration signal is subjected to band-pass filtering processing, and the vibration components in the preset frequency band are retained;

[0016] Fast Fourier transform is performed on the filtered ship vibration signal, and the frequency component with an energy proportion exceeding a set threshold is extracted as the vibration main frequency band;

[0017] The instantaneous phase angle of the vibration main frequency band is calculated through Hilbert transform.

[0018] Further, based on the frequency domain overlap factor of the vibration main frequency band and the natural frequency of the heat sink, the dynamic compensation parameters of the interface between the heat sink and the busbar are determined in cooperation with the heat conduction phase lag angle amplitude, including:

[0019] The natural frequency of the heat sink is obtained based on the sweep frequency test;

[0020] The intersection bandwidth of the vibration main frequency band and the natural frequency of the heat sink accounts for the ratio of the total bandwidth of the vibration main frequency band as the frequency domain overlap factor;

[0021] The phase difference between the vibration displacement signal and the heat flow signal at the heat sink interface is calculated as the heat conduction phase lag angle amplitude through a phase-locked amplifier;

[0022] The frequency domain overlap factor and the heat conduction phase lag angle amplitude are input into a preset compensation parameter mapping table, and the compression resilience characteristic index and the pre-tightening force adjustment coefficient in the dynamic compensation parameters are output.

[0023] Further, the compensation parameter mapping table is constructed through orthogonal test:

[0024] The frequency domain overlap factor and the heat conduction phase lag angle amplitude are divided into gradient levels;

[0025] The heat resistance fluctuation value of the heat sink interface is measured under each level combination;

[0026] The compression resilience characteristic index and the pre-tightening force adjustment coefficient corresponding to the minimum heat resistance fluctuation value are selected as the mapping output.

[0027] Further, an elastic heat-conducting gasket is arranged between the heat sink and the busbar, the elastic heat-conducting gasket is selected according to the compression and rebound characteristic index in the dynamic compensation parameter, and the long axis direction is perpendicular to the maximum displacement direction of the phase angle, and the elastic heat-conducting gasket comprises:

[0028] According to the compression and rebound characteristic index in the dynamic compensation parameter, an elastic heat-conducting gasket that meets the dynamic compression rate and rebound delay requirements is matched from a pre-prepared elastic heat-conducting gasket library;

[0029] The maximum displacement direction of the phase angle is obtained through a vibration displacement sensor;

[0030] The long axis direction of the elastic heat-conducting gasket is calibrated by using a laser positioner, so as to ensure that the long axis direction forms a 90-degree perpendicular relationship with the maximum displacement direction;

[0031] The elastic heat-conducting gasket is installed after the heat-conducting silicone grease is coated on the contact interface between the heat sink and the busbar, and the fastening bolt is tightened to an initial pre-tightening force state.

[0032] Further, an axial pre-tightening force generated according to a pre-tightening force adjustment coefficient in the dynamic compensation parameter is applied to the heat sink fastening bolt, and the axial pre-tightening force is adjusted periodically according to the phase angle, and the method comprises the steps of:

[0033] The pre-tightening force adjustment coefficient is extracted from the dynamic compensation parameter;

[0034] The pre-tightening force change period is determined according to the fundamental frequency of the vibration main frequency band;

[0035] The instantaneous angle value of the phase angle is obtained in real time;

[0036] Based on the instantaneous angle value of the phase angle and the pre-tightening force adjustment coefficient, an axial pre-tightening force target value corresponding to the vibration period is generated;

[0037] The bolt loading device is driven by a hydraulic actuator to apply a mechanical load corresponding to the axial pre-tightening force target value to the heat sink fastening bolt.

[0038] Further, the transient thermal resistance value of the heat sink and busbar connection interface is synchronously measured at the wave peak phase angle position and the wave trough phase angle position of the vibration main frequency band, and the thermal resistance change rate from the adjacent wave peak phase angle position to the wave trough phase angle position is calculated, and the method comprises the steps of:

[0039] The wave peak phase angle position and the wave trough phase angle position are determined;

[0040] When the ship vibration reaches the wave peak phase angle position, the first transient thermal resistance value of the heat sink and busbar connection interface is synchronously collected by the thermocouple array;

[0041] When the ship vibration reaches the wave trough phase angle position, the second transient thermal resistance value of the heat sink and busbar connection interface is synchronously collected by the thermocouple array;

[0042] The difference between the first transient thermal resistance value and the second transient thermal resistance value is divided by the first transient thermal resistance value to obtain a thermal resistance change rate.

[0043] Further, the wave peak phase angle position is determined according to the maximum displacement direction of the phase angle, and the wave trough phase angle position is determined according to the minimum displacement direction of the phase angle.

[0044] Further, when the thermal resistance change rate exceeds the dynamic response tolerance threshold, the pre-tightening force adjustment coefficient and the compression resilience characteristic index are updated, including:

[0045] The thermal resistance change rate is compared with the preset dynamic response tolerance threshold;

[0046] When the thermal resistance change rate exceeds the dynamic response tolerance threshold, the pre-tightening force adjustment coefficient is adjusted based on the thermal resistance change rate exceeding amplitude;

[0047] The minimum compression rate required for the radiator and the busbar connecting interface is reversely deduced according to the adjusted pre-tightening force adjustment coefficient;

[0048] The elastic heat-conducting gasket meeting the compression resilience characteristic index is re-matched from the elastic heat-conducting gasket library according to the minimum compression rate;

[0049] The original dynamic compensation parameter is covered with the updated pre-tightening force adjustment coefficient and the compression resilience characteristic index.

[0050] On the other hand, the application provides a heat dissipation system applied to an air switch cabinet, including the following modules:

[0051] A vibration monitoring module is used to monitor the ship vibration of the installation position of the switch cabinet in real time, extract the vibration main frequency band and phase angle;

[0052] A parameter decision module is used to determine the dynamic compensation parameter of the radiator and the busbar connecting interface based on the frequency domain overlap factor of the vibration main frequency band and the inherent frequency of the radiator, and the heat conduction phase lag angle amplitude;

[0053] A gasket installation module is used to set an elastic heat-conducting gasket between the radiator and the busbar, the elastic heat-conducting gasket is selected according to the compression resilience characteristic index in the dynamic compensation parameter, and the long axis direction is perpendicular to the maximum displacement direction of the phase angle;

[0054] A pre-tightening control module is used to apply an axial pre-tightening force generated according to the pre-tightening force adjustment coefficient in the dynamic compensation parameter to the radiator fastening bolt, and the axial pre-tightening force is adjusted periodically with the phase angle;

[0055] A thermal resistance monitoring module is configured to synchronously measure transient thermal resistance values of a heat sink and a busbar connecting interface at a wave crest phase angle position and a wave trough phase angle position in a vibration main frequency band, and to calculate a thermal resistance change rate from the wave crest phase angle position to the wave trough phase angle position.

[0056] A parameter updating module is configured to update a pre-tightening force adjustment coefficient and a compression resilience characteristic index when the thermal resistance change rate exceeds a dynamic response tolerance threshold.

[0057] Compared with the prior art, the application has the following beneficial effects:

[0058] 1. The vibration of the ship is monitored in real time, and the vibration main frequency band and the phase angle are extracted, so that the dynamic influence of the vibration on the heat dissipation interface is accurately captured, and data basis is provided for subsequent compensation. Based on frequency domain analysis of the vibration characteristics and the inherent frequency of the heat sink, and in combination with the phase lag angle amplitude of heat conduction, the compensation parameters are dynamically determined, and the response capability of the heat sink and the busbar connecting interface is directly optimized. The elastic heat-conducting gasket is selected according to the compression resilience characteristic index and is perpendicular to the maximum displacement, effectively absorbs the vibration energy and maintains the stability of the heat conduction path. Periodic adjustment of the pre-tightening force specifically offsets the interface loosening caused by the vibration, and ensures uniform distribution of the contact pressure. These technical features work together to significantly suppress the mutation of the interface thermal resistance, avoid abnormal fluctuations in local temperature rise, and thus improve the heat dissipation efficiency and equipment reliability.

[0059] 2. The thermal resistance change rate is monitored in a closed loop, and the parameters are updated when the thermal resistance change rate exceeds the threshold, so that the self-adaptive optimization of the heat dissipation system is realized. Through transient thermal resistance measurement of the wave crest and wave trough phase positions, the change of the interface thermal performance is fed back in real time. When the thermal resistance change rate exceeds the threshold, the pre-tightening force coefficient and the compression resilience index are immediately adjusted, the elastic gasket is re-matched, and the compensation parameters are covered. This dynamic adjustment mechanism continuously adapts to changes in the vibration environment, ensures the long-term stability of the heat dissipation interface from the root, prevents temperature rise from getting out of control, and enhances the durability and safe operation capability of the switch cabinet under the vibration working condition of the ship. BRIEF DESCRIPTION OF DRAWINGS

[0060] Figure 1 A flowchart of a heat dissipation method applied to an air switch cabinet according to the application;

[0061] Figure 2 A structural schematic diagram of a heat dissipation system applied to an air switch cabinet according to the application. DETAILED DESCRIPTION

[0062] The technical solutions in the embodiments of the application will be clearly and completely described below with reference to the drawings in the embodiments of the application. Obviously, the described embodiments are only part of the embodiments of the application, rather than all the embodiments of the application. Based on the embodiments in the application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the application.

[0063] Embodiment 1: Figure 1 A heat dissipation method applied to an air switch cabinet is given, which comprises the following steps:

[0064] S1, real-time monitoring of ship vibration at the installation position of the switch cabinet, extraction of the main frequency band and phase angle of the vibration;

[0065] S2, based on the frequency domain overlap factor of the main frequency band of the vibration and the natural frequency of the radiator, the dynamic compensation parameters of the radiator and the busbar connection interface are determined in cooperation with the phase lag angle amplitude of heat conduction;

[0066] S3, an elastic heat-conducting gasket is arranged between the radiator and the busbar, the elastic heat-conducting gasket is selected according to the compression and rebound characteristic index in the dynamic compensation parameters, and the long axis direction is perpendicular to the maximum displacement direction of the phase angle;

[0067] S4, an axial pre-tightening force generated according to the pre-tightening force adjustment coefficient in the dynamic compensation parameters is applied to the fastening bolt of the radiator, and the axial pre-tightening force is adjusted periodically according to the phase angle;

[0068] S5, at the wave peak phase angle position and the wave trough phase angle position of the main frequency band, the transient thermal resistance value of the radiator and the busbar connection interface is measured synchronously, and the thermal resistance change rate from the adjacent wave peak phase angle position to the wave trough phase angle position is calculated;

[0069] S6, when the thermal resistance change rate exceeds the dynamic response tolerance threshold, the pre-tightening force adjustment coefficient and the compression and rebound characteristic index are updated.

[0070] S1, real-time monitoring of ship vibration at the installation position of the switch cabinet, extraction of the main frequency band and phase angle, implementation is:

[0071] The ship vibration signal at the installation position of the switch cabinet is collected by a three-axis acceleration sensor, the three-axis acceleration sensor adopts a piezoelectric sensing principle, the core piezoelectric ceramic element of which deforms under the action of the inertial force generated by the ship vibration, and outputs an electric charge signal proportional to the acceleration. The sensor is installed at the center position of the metal flange surface rigidly connected between the switch cabinet base and the ship body main structure, and high-strength bolts are used during installation to cooperate with the lock washer to ensure that there is no gap between the sensor shell and the installation surface., in order to accurately transmit the mechanical vibration caused by the main engine and propeller shaft system of the ship. The three-axis direction of the sensor is calibrated according to the ship coordinate system: the X-axis is parallel to the centerline of the bow and stern of the ship and points to the bow direction, the Y-axis is perpendicular to the X-axis and points to the right side direction, and the Z-axis is perpendicular to the deck plane and upward. During signal acquisition, the built-in charge amplifier in the sensor converts the weak charge signal into a voltage signal, and transmits it to the data acquisition unit through a twisted shield cable. The cable shield layer is grounded at both the sensor end and the data acquisition end to suppress electromagnetic interference generated by the ship's electrical system.

[0072] The ship vibration signal is band-pass filtered to retain the vibration components within a preset frequency band. The low cutoff frequency is set to 50% of the fundamental frequency corresponding to the lowest operating speed of the ship's main engine, to filter out the ultra-low frequency components caused by sea wave sway. The high cutoff frequency is set to twice the maximum value of the blade passing frequency of the propeller, to eliminate high-frequency electrical noise. The filtering process is implemented using a cascade of analog active filters and digital filters: the analog filters first filter out high-intensity impact components that exceed the sensor's range, protecting the subsequent circuit; the digital filter uses a finite-length unit impulse response filter design, whose linear phase characteristics ensure that the filtering process does not distort the time-domain characteristics of the vibration waveform. The filtered signal retains the low-frequency vibration components caused by the reciprocating inertia force of the ship's main engine and the medium-frequency vibration components caused by the torsional vibration of the propeller shaft system, while effectively suppressing the high-frequency vibration components caused by the electromagnetic force of the ship's generator winding.

[0073] The filtered ship vibration signal is subjected to fast Fourier transform to extract the frequency components with energy proportion exceeding a set threshold as the main vibration band. The number of points for fast Fourier transform is dynamically adjusted according to the width of the ship vibration energy concentration band: when the vibration energy distribution band is wide, the number of points is increased to improve the frequency resolution, and when the energy distribution is concentrated, the number of points is reduced to reduce the operation delay. The energy proportion threshold is set according to the ship vibration environment level: for the conventional machinery cabin environment of merchant ships, it is 60% to 70% of the total vibration energy, and for the high-vibration-risk propulsion cabin of warships, it is increased to 75% to 85%. The specific extraction logic is: calculate the amplitude square of all discrete frequency components in the preset frequency band and arrange them in descending order, and sequentially accumulate the energy of each component until the cumulative value first exceeds the product of the total energy of the frequency band and the set threshold, at which point all continuous frequency components participating in the accumulation constitute the main vibration band. This design ensures that the extracted main frequency band covers the energy dominant band that has the most significant impact on the switchgear structure in the ship vibration environment.

[0074] The instantaneous phase angle of the main vibration band is calculated by Hilbert transform, which includes: first, the main vibration band time-domain signal is subjected to quadrature demodulation processing, and the analytic signal expression form of the original signal is constructed using Hilbert transform. The imaginary part of the analytic signal is generated by the original signal through a ninety-degree phase shift network, and the real part is the original signal itself, which together constitutes a rotating vector in the complex plane. The instantaneous phase angle is obtained by calculating the angle between this vector and the positive direction of the real axis, and the phase unwrapping algorithm is used to eliminate the two-pi radian discontinuity points caused by circular jump. The phase angle zero point reference is set to the top dead center position of the ship's main engine crankshaft angle, which is synchronized and calibrated by the pulse signal provided by the reference marker sensor installed on the main engine flywheel. To verify the phase measurement accuracy, a comparative test is conducted on a standard vibration source with known phase relationship: a sinusoidal vibration signal with constant amplitude and linear frequency change is input, and the deviation between the measured instantaneous phase angle and the theoretical value is controlled within 0.005 radians.

[0075] S2, determine the dynamic compensation parameters of the heat sink and busbar connection interface based on the frequency domain overlap factor of the vibration main frequency band and the natural frequency of the heat sink, and the amplitude of the heat conduction phase lag angle, and implement as:

[0076] The natural frequency of the heat sink is obtained based on the sweep test, and the specific implementation process is as follows: the heat sink sample is fixed on the electromagnetic vibration table through a rigid clamp, and the center axis of the vibration table moving coil is perpendicular to the plane of the heat sink base plate. The sweep signal is generated by a function generator to produce a sine waveform, and the frequency range covers 20% of the upper limit to 20% of the lower limit of the main frequency band of the ship vibration, and the sweep rate is set to 1 / 3 octave per minute to ensure the quasi-static response. A piezoelectric acceleration sensor is installed at the center of the top of the heat sink fin, and its output signal is converted into a voltage signal by a charge amplifier and the amplitude is recorded. When the sweep frequency reaches a certain frequency point, the amplitude of the heat sink increases to more than 3 times the background noise level, and the phase difference suddenly changes to nearly 180 degrees relative to the excitation force, then the frequency point is determined as the natural frequency. In the test, the surface temperature distribution of the heat sink is monitored in real time by an infrared thermal imager, and the sweep is paused when the local temperature rise exceeds 5°C to prevent overheating damage, and the test continues after cooling.

[0077] The ratio of the intersection bandwidth of the vibration main frequency band and the natural frequency of the heat sink to the total bandwidth of the vibration main frequency band is calculated as the frequency domain overlap factor. The vibration main frequency band is composed of the discrete frequency point set output by S1 step, and the natural frequency of the heat sink is the multiple resonance frequency points identified by the sweep test. The intersection bandwidth calculation logic is: taking the lowest frequency of the vibration main frequency band as the starting point and the highest frequency as the ending point to form a continuous frequency band, and counting the number of heat sink natural frequency points located in the frequency band; merging the sections between adjacent natural frequency points with a spacing less than 5% of the center frequency into a continuous frequency band; and accumulating the widths of all continuous frequency bands to obtain the intersection bandwidth value. The frequency domain overlap factor is finally expressed in the form of percentage of the intersection bandwidth divided by the total bandwidth of the vibration main frequency band. For example, the vibration main frequency band is 15Hz to 45Hz (bandwidth 30Hz) under certain working conditions, and the natural frequencies of the heat sink are 20Hz and 40Hz, which are located in the frequency band. The interval between the two frequencies is 20Hz, which is greater than 5% (1.5Hz) of the center frequency 30Hz, so the intersection bandwidth is the width of the two independent frequency points and 0.2Hz (according to the frequency resolution), and the frequency domain overlap factor is (0.2 / 30) x 100% ≈ 0.67%.

[0078] The phase difference value between the vibration displacement signal and the heat flow signal at the interface of the heat sink is calculated as the phase lag angle amplitude of heat conduction. The vibration displacement signal is obtained by installing a laser displacement sensor at the center point of the heat sink substrate, with the measurement direction perpendicular to the busbar mounting plane, and the sampling rate being consistent with that in step S1, i.e. 512 Hz. The heat flow signal is obtained by embedding a thin film heat flow probe with a diameter of 0.5 mm at the contact surface between the heat sink and the busbar, with a 25 μm thick insulating ceramic layer covering the surface of the probe, and the spatial resolution satisfying 1 / 10 of the minimum feature size of the contact area. The phase-sensitive detection is performed on the heat flow signal by setting the fundamental component of the vibration displacement signal as the reference signal, and the instantaneous phase difference value of the two signals at the reference frequency is directly output. The phase lag angle amplitude is the arithmetic average of the absolute values of the phase difference in 10 consecutive vibration periods, and the unit is radian.

[0079] The frequency domain overlap factor and the phase lag angle amplitude of heat conduction are input into a preset compensation parameter mapping table to output the compression and rebound characteristic index and the pre-tightening force adjustment coefficient in the dynamic compensation parameter. The compensation parameter mapping table is constructed by orthogonal test, and the construction process includes three levels: the first level is parameter gradient division, the frequency domain overlap factor is divided into 0%-100% at an interval of 10%, and the phase lag angle amplitude of heat conduction is divided into 0-1.5 rad at an interval of 0.1 rad; the second level is test execution, each level combination condition is simulated on a vibration-temperature comprehensive test bench, and the target parameter combination is accurately reproduced by controlling the vibration frequency, amplitude and heat sink base temperature; the third level is data acquisition, the heat resistance value of the heat sink is recorded every 5 seconds during the stable operation of each parameter combination for 30 minutes, and the relative change amount of the maximum and minimum values of the heat resistance is taken as the heat resistance fluctuation value.

[0080] In the data processing stage of the orthogonal test, the arithmetic mean of the 12 groups of heat resistance fluctuation values measured under each parameter combination is taken after removing the outliers, and a three-dimensional response surface model is established. The mapping rules of the compression and rebound characteristic index and the pre-tightening force adjustment coefficient are as follows: under the same frequency domain overlap factor and phase lag angle amplitude of heat conduction, the median of the compression and rebound characteristic index of the first 10 test results with the smallest heat resistance fluctuation value is taken as the output value; the pre-tightening force adjustment coefficient is the average of the first 10 results. The finally formed mapping table is stored in the non-volatile memory, and the bilinear interpolation algorithm is used to realize accurate matching under continuous parameter input. To verify the effectiveness of the mapping table, the deviation between the predicted compensation parameters and the actual optimal parameters is compared in the independent verification group data, the matching error of the compression and rebound characteristic index is controlled within ±5%, and the deviation of the pre-tightening force adjustment coefficient is less than 0.05.

[0081] S3, an elastic heat-conductive gasket is arranged between the heat sink and the busbar, the elastic heat-conductive gasket is selected according to the compression and rebound characteristic index in the dynamic compensation parameter, and the long axis direction is perpendicular to the maximum displacement direction of the phase angle, and is implemented as:

[0082] According to the compression and rebound characteristic index in the dynamic compensation parameter, an elastic heat-conductive gasket satisfying the dynamic compression rate and rebound delay requirements is matched from a pre-prepared elastic heat-conductive gasket library. The elastic heat-conductive gasket library is constructed through a material accelerated aging test: each candidate gasket is subjected to a sinusoidal wave compression load on a hydraulic fatigue testing machine, the load amplitude corresponds to the interface pressure generated by the maximum acceleration of ship vibration, and the frequency covers the main frequency range of vibration. The dynamic compression rate is defined as the percentage of the change in gasket thickness to the initial thickness, which is measured after 10,000 consecutive compression cycles; the rebound delay is recorded by a high-speed camera to measure the time required for the gasket thickness to recover to 95% of the initial value during unloading. The compression and rebound characteristic index includes a tolerance band of ±3% of the dynamic compression rate and an upper limit value of the rebound delay, and when matching, the gasket type that meets both requirements is selected. For example, a certain dynamic compensation parameter requires a dynamic compression rate of 30%±3% and a rebound delay of less than 0.05 seconds, then a silicone rubber-based composite gasket with a calibrated value of dynamic compression rate of 29.5% to 31.5% and rebound delay of 0.03 to 0.04 seconds is selected from the library.

[0083] The maximum displacement direction of the phase angle is obtained by a vibration displacement sensor, and a non-contact laser Doppler vibration meter is specifically used. A reflective marker point is pasted on the surface of the heat sink substrate, and the marker point position coincides with the mounting point of the three-axis acceleration sensor in the S1 step. The vibration meter emits a laser beam to irradiate the marker point, and a Doppler frequency shift signal of the reflected light is received and a three-dimensional vibration vector is calculated. The maximum displacement direction of the phase angle extraction logic is: in a complete working cycle period of the ship main engine, the real-time direction angle of the vibration displacement vector is recorded; the lengths of the displacement vectors of each sampling point are compared, and the direction angle corresponding to the maximum length is defined as the maximum displacement direction of the phase angle. The direction angle data is taken as a reference in the ship coordinate system, and the output format is the horizontal angle deviating from the bow-stern center line and the pitch angle deviating from the horizontal plane. Random interference is eliminated by three repeated acquisitions during the measurement process, and the final result is taken as the median value.

[0084] The long axis direction of the elastic heat-conducting pad is calibrated by a laser positioning instrument to ensure that the long axis direction is perpendicular to the maximum displacement direction. The laser positioning instrument establishes a cross reference line on the heat sink mounting plane: the horizontal laser beam is parallel to the bow-stern centerline of the ship, and the vertical laser beam is orthogonal to the horizontal plane. The calibration operation includes two levels: first, place the elastic heat-conducting pad in the center of the heat sink mounting area, and adjust the orientation of the pad so that the long axis projection coincides with the vertical laser beam; then, rotate the pad according to the angle value of the maximum displacement direction, and the rotation angle is equal to the complementary angle of the angle between the maximum displacement direction and the vertical laser beam. For example, if the maximum displacement direction is 30 degrees clockwise in the bow-stern direction, then rotate the long axis of the pad 60 degrees counterclockwise from the vertical reference, so that the long axis forms a 90-degree intersection angle with the maximum displacement direction. After calibration, use a precision protractor to verify the perpendicularity, with an allowable tolerance of ±0.5 degrees.

[0085] After coating the heat-conducting silicone grease on the contact interface between the heat sink and the bus bar, install the elastic heat-conducting pad and tighten the bolts to the initial pre-tightening state. The heat-conducting silicone grease is selected from silver powder filled silicone materials. Before coating, clean the contact surface of the heat sink and the bus bar with a solvent to remove oil stains. During coating, use a scraper to evenly apply the silicone grease to form a 0.1mm thick continuous film layer. When installing the elastic heat-conducting pad, keep the long axis direction consistent with the calibration reference, and the deviation of the pad edge from the heat sink boundary is less than 1mm. Tighten the bolts in three stages using the torque control method: the first stage applies 30% of the target pre-tightening force to eliminate assembly gaps, the second stage loads to 60% to preliminarily compress the pad, and the third stage loads to the initial pre-tightening target value and maintains for 30 seconds to release stress. The initial pre-tightening target value is calculated based on the bolt specification and material yield strength to ensure that the bolt stress does not exceed 70% of the yield strength.

[0086] S4, apply an axial pre-tightening force to the heat sink tightening bolt according to the pre-tightening force adjustment coefficient in the dynamic compensation parameter, and the axial pre-tightening force is adjusted periodically according to the phase angle, which is implemented as:

[0087] The pre-tightening force adjustment coefficient is extracted from the dynamic compensation parameter, which is implemented as follows: identify the floating point parameter value labeled "pre-tightening force adjustment coefficient" in the dynamic compensation parameter data packet, and normalize the value range to between 0 and 1. The extraction operation is realized through a data analysis protocol: first, verify the data packet checksum to confirm integrity, then locate the parameter storage address offset, and finally decode the binary data in IEEE 754 single-precision floating point number format. If there are multiple sets of dynamic compensation parameters (such as multiple heat sink parallel connection scenarios), establish a parameter mapping relationship according to the physical number order of the heat sinks.

[0088] The pre-tightening force change period is determined according to the fundamental frequency of the vibration main frequency band, and the fundamental frequency refers to the frequency component with the highest energy proportion in the vibration main frequency band. The period calculation adopts the reciprocal principle of the fundamental frequency: the basic period length is obtained by dividing 1 by the fundamental frequency value, and then multiplied by the number of phase angle complete change periods. For example, the fundamental frequency of a certain working condition is 25 Hz, and the phase angle change period is 1 (i.e. 0 to 360 degrees complete a cycle), then the pre-tightening force change period is equal to 1 / 25=0.04 seconds. When the vibration main frequency band contains multiple dominant frequencies, the geometric mean frequency is taken as the calculation reference of the fundamental frequency.

[0089] The instantaneous angle value of the phase angle is obtained in real time, which is realized through the phase angle data stream interface established in step S1. The data stream is updated at a rate of 512 Hz, and each read operation obtains the angle value corresponding to the latest timestamp. The angle value is represented in floating-point number form, with a range of 0 to 360 degrees continuously changing. In order to eliminate the influence of signal jitter, moving average filtering is used: the angle values of the current time and the previous two sampling points (a total of 3 points) are taken as the arithmetic mean, and the filtering window width corresponds to 5.86 milliseconds (3 / 512 seconds), which meets the phase tracking accuracy requirements under the maximum angular acceleration of ship vibration.

[0090] Based on the instantaneous angle value of the phase angle and the pre-tightening force adjustment coefficient, the axial pre-tightening force target value corresponding to the vibration period is generated. The generation logic includes three calculation levels: the first level converts the instantaneous angle value into a phase proportion factor, the formula is instantaneous angle value divided by 360; the second level defines the load change amplitude through the pre-tightening force adjustment coefficient, the formula is initial pre-tightening force multiplied by pre-tightening force adjustment coefficient; the third level calculates the target value, the formula is initial pre-tightening force plus phase proportion factor multiplied by load change amplitude. For example, when the initial pre-tightening force is 10000 Newton, the pre-tightening force adjustment coefficient is 0.3, and the instantaneous angle is 180 degrees: phase proportion factor = 180 / 360 = 0.5, load change amplitude = 10000 x 0.3 = 3000 Newton, target value = 10000 + 0.5 x 3000 = 11500 Newton.

[0091] The bolt loading device is driven by a hydraulic actuator to apply a mechanical load corresponding to the axial pre-tightening force target value to the radiator fastening bolt. The hydraulic system adopts three closed-loop control: position loop controls piston displacement, pressure loop monitors oil pressure value, and force loop ensures output load accuracy. The execution process is divided into three steps: the first step is to convert the target value into the hydraulic cylinder pressure set value by the servo controller, and the conversion is based on the relationship between the piston effective area and the load; the second step is to adjust the oil flow by the proportional valve, so that the actual value measured by the pressure sensor reaches the set value within 200 milliseconds; the third step is to transfer the axial load to the bolt through the ball hinge type pull and pressure head, and the load holding time is greater than 50 milliseconds to ensure sufficient stress transfer. The system monitors the load error in real time, and when the deviation continuously exceeds 5% of the target value, the fault protection program is triggered.

[0092] S5, synchronously measure the transient thermal resistance value of the interface between the heat sink and the busbar at the peak phase angle position and the valley phase angle position in the vibration frequency band, calculate the thermal resistance change rate from the adjacent peak phase angle position to the valley phase angle position, and implement as follows:

[0093] Determine the peak phase angle position and the valley phase angle position: based on the phase angle data stream output in S1, identify the displacement extreme points in the continuous vibration period. The peak phase angle position is defined as the position point in the 5-degree tolerance interval of the maximum displacement direction corresponding angle value of the phase angle, which needs to meet the conditions that the displacement vector module length reaches the local maximum value and the second derivative is negative; the valley phase angle position is defined as the position point in the 5-degree tolerance interval of the minimum displacement direction corresponding angle value of the phase angle, which has the local minimum value of the displacement vector module length and the positive second derivative. The identification algorithm uses a sliding window extreme value detection: the window width covers 1 / 4 of the vibration period, and when the displacement module length of the window center point is greater than the maximum value in the front and rear 1 / 4 window width, it is determined as a peak; otherwise, it is determined as a valley.

[0094] When the ship vibration reaches the peak phase angle position, the first transient thermal resistance value of the interface between the heat sink and the busbar is synchronously collected by the thermocouple array. The thermocouple array is composed of 9 T-type thermocouples arranged in a 3x3 grid, and the node spacing is 1 / 10 of the short side length of the heat sink contact surface. The collection trigger mechanism is that when the real-time phase angle output in S1 enters the peak phase angle position tolerance interval, a hardware trigger signal is sent to the data collection unit. All thermocouple channels are synchronously started to sample within 100 microseconds after the trigger, with a sampling frequency of 10 kHz for 10 milliseconds, and the arithmetic mean of the temperature readings in this period is taken as the steady-state temperature value. The thermal resistance value is calculated using Fourier heat conduction law: the thermal resistance value is equal to the temperature difference divided by the heat flux density, wherein the temperature difference is the difference between the average values of the thermocouples on the heat sink side and the busbar side, and the heat flux density is directly provided by the heat flow sensor embedded in the interface.

[0095] When the ship vibration reaches the valley phase angle position, the second transient thermal resistance value of the interface between the heat sink and the busbar is synchronously collected by the thermocouple array. The valley trigger logic is symmetrical to the peak trigger: when the real-time phase angle enters the valley phase angle position tolerance interval, a trigger signal is generated. The thermocouple uses the same 10 millisecond sampling window, but adds temperature drift compensation: the ambient temperature is collected as a reference 1 millisecond before the trigger, and the linear temperature drift component is deducted from the measured value. When calculating the thermal resistance, the temperature difference is subjected to nonlinear correction: when the temperature difference is less than 10K, the standard formula is used; when the temperature difference is greater than 10K, a Seebeck effect compensation term is introduced, and the compensation coefficient is pre-calibrated through material pairing tests.

[0096] The difference between the first transient thermal resistance value and the second transient thermal resistance value is divided by the first transient thermal resistance value to obtain a thermal resistance change rate. The calculation process includes data validity verification: if the first transient thermal resistance value is less than 0.01 K / W or greater than 1 K / W, it is determined that the sensor is faulty and the data is discarded; if the time interval between the two thermal resistance value collection times exceeds 20% of the vibration period, it is determined that there is an asynchronous error and re-measurement is required. The thermal resistance change rate is expressed in percentage form, and the calculation formula is: thermal resistance change rate = (second transient thermal resistance value - first transient thermal resistance value) ÷ first transient thermal resistance value × 100%. The thermal resistance change rate is continuously calculated for three vibration periods, and the median value is taken as the final output.

[0097] Implementation element description: thermocouple installation structure: the thermocouple junction is embedded in an alumina ceramic insulating sleeve, the sleeve has an outer diameter of 0.8 mm, and the space between the heat sink / busbar is filled with heat-conducting epoxy resin; peak-to-valley tolerance interval: set according to the maximum ship vibration angular velocity to ensure coverage of the phase jitter range; synchronous acquisition mechanism: uses a daisy chain type cascade sampling and holding circuit, with a delay of less than 10 nanoseconds between channels; temperature drift compensation: based on the drift characteristic curve modeling of the thermocouple in a static constant temperature field; data validity threshold: determined according to the thermal resistance design specification for ship power equipment.

[0098] Error control measures include: periodic calibration of thermocouples: calibration at 0°C ice water mixture and 100°C boiling water reference points every 24 hours; contact pressure monitoring: automatically triggers a data invalidity flag when the interface pressure fluctuation exceeds the initial value by 15%; electromagnetic shielding: thermocouple signal lines use twisted pair shielding lines with single-point grounding of the shielding layer; thermal inertia compensation: corrects transient temperature readings based on the thermal diffusivity of the material; vibration interference suppression: deducts additional potential caused by thermocouple junction inertia force in thermal resistance calculation.

[0099] Implementation description: for example, in a certain measurement, the first transient thermal resistance value collected at the peak phase angle position is 0.28 K / W, and the second transient thermal resistance value collected at the valley phase angle position is 0.35 K / W. After passing the validity check, the thermal resistance change rate is calculated as (0.35-0.28) / 0.28×100%=25%. This result is consistent with the trend of interface contact thermal spot distribution observed by the infrared thermal imager, verifying the reliability of the measurement. All data records are synchronized with the ship main engine speed, load rate, and environmental temperature and humidity parameters for subsequent analysis.

[0100] S6、When the thermal resistance change rate exceeds the dynamic response tolerance threshold, update the pre-tightening force adjustment coefficient and the compression and rebound characteristic index, and implement as follows:

[0101] The thermal resistance change rate is compared with a preset dynamic response tolerance threshold, which is set according to the heat dissipation performance safety specification of the ship switch cabinet. The threshold setting logic is: first, the thermal conductivity and thermal expansion coefficient of the radiator base plate material are obtained, combined with the maximum allowed temperature rise limit of the busbar, the critical value of the interface thermal resistance fluctuation is calculated through the thermoelastic mechanics model; then multiply the safety factor 1.2 as the final threshold. The comparison operation is executed after the measurement of three consecutive vibration periods is completed: if the arithmetic mean of the thermal resistance change rate of the three periods is greater than the threshold, it is judged as an out-of-tolerance event; if a single measurement value exceeds 150% of the threshold, the update program is triggered immediately without waiting for the period to complete.

[0102] When the thermal resistance change rate exceeds the dynamic response tolerance threshold, the pretightening force adjustment coefficient is adjusted based on the exceeding amplitude of the thermal resistance change rate. The adjustment algorithm adopts a proportional-integral control mode: the exceeding amplitude is defined as the difference between the measured thermal resistance change rate and the dynamic response tolerance threshold; the proportional term correction amount is the exceeding amplitude multiplied by the proportional gain coefficient 0.1; the integral term correction amount is the cumulative value of the historical exceeding amplitude multiplied by the integral gain coefficient 0.01. The updated value of the pretightening force adjustment coefficient is equal to the original coefficient plus the sum of the proportional term and the integral term. For example, the original coefficient is 0.4, the threshold is 15%, and the measured change rate is 21%: exceeding amplitude = 21%-15% = 6%, proportional term = 6% x 0.1 = 0.006, integral term (assuming historical cumulative 30%) = 30% x 0.01 = 0.003, new coefficient = 0.4 + 0.006 + 0.003 = 0.409. The coefficient range is limited to 0.2 to 0.8 to prevent overloading.

[0103] The minimum compression rate required for the connection interface between the radiator and the busbar is reversely deduced according to the adjusted pretightening force adjustment coefficient. The derivation process is based on the Hertz contact theory to establish a mathematical model: the axial pretightening force of the bolt is converted into the interface contact pressure, which is equal to the pretightening force divided by the effective contact area of the radiator and the busbar; the relationship between the minimum compression rate and the contact pressure is determined by the material compression test calibration curve. The specific implementation is: the target pretightening force is obtained by querying the product of the pretightening force adjustment coefficient and the initial pretightening force; the target contact pressure is calculated through the contact area; in the gasket material stress-strain curve, find the minimum compression rate value required to produce the contact pressure. The curve data is stored in an embedded database, and a cubic spline interpolation is used to realize continuous query.

[0104] Re-matching elastic heat-conducting gaskets from the gasket library according to the minimum compression rate to meet the compression and rebound characteristics index. The matching process includes double screening: the first level screening compression performance, selecting the gasket type whose nominal dynamic compression rate is greater than or equal to the minimum compression rate and less than or equal to the minimum compression rate plus 5%; the second level screening dynamic characteristics, selecting the gasket whose rebound delay is less than 0.1 second from the preliminary selection result. When multiple gaskets meet the conditions, the type with the highest thermal conductivity coefficient is preferentially selected. The matching result outputs the unique code of the gasket in the material library, and automatically checks the inventory status.

[0105] The original dynamic compensation parameters are covered by the updated preload adjustment coefficient and the compression and rebound characteristics index. The covering mechanism adopts version management: a new parameter partition is created in the non-volatile memory, the updated preload adjustment coefficient value and the compression and rebound characteristics index value corresponding to the new gasket are written, the parameter pointer is modified to point to the new partition address, and the original parameter partition is converted into a historical backup. After the covering is completed, a parameter ready signal is sent to the control system to trigger the following linkage operations: sending the new preload adjustment coefficient to the hydraulic actuator of S4 step; sending the new gasket code to the gasket installation station of S3 step; updating the dynamic response tolerance threshold value of S5 step (the new threshold value is recalculated according to 120% of the expected performance of the updated parameters).

[0106] Key implementation element description: safety factor determination basis: statistical distribution of interface pressure fluctuation amplitude under ship tilting and swinging working condition; PID gain coefficient setting: optimization through step response test, so that the system regulation time is less than 10 vibration periods; Hertz contact model simplification: rough surface contact is simplified as equivalent smooth surface contact; gasket screening tolerance band: considering the compression rate attenuation characteristics caused by material aging; parameter storage architecture: adopting double bank flash memory design to support atomic write operation.

[0107] Fault protection measures include: coefficient out-of-bound protection: triggering a warning when the updated coefficient approaches the 0.2 or 0.8 boundary; gasket matching failure processing: starting the standby manual selection mode and alarming; data integrity check: performing CRC check after parameter writing; rollback mechanism: automatically restoring the old parameters when the thermal resistance change rate worsens by more than 20% in the first period after applying the new parameters; operation log recording: storing the timestamp, operator and parameter change details in the secure storage area.

[0108] Embodiment 2: Figure 2 A structure diagram of a heat dissipation system applied to an air switch cabinet is given, and the heat dissipation system applied to the air switch cabinet comprises the following modules:

[0109] A vibration monitoring module is used for monitoring the ship vibration of the installation position of the switch cabinet in real time, and extracting the vibration main frequency band and phase angle.

[0110] The parameter decision module is configured to determine a dynamic compensation parameter of the interface between the heat sink and the busbar based on a frequency domain overlap factor of the vibration main frequency band and the inherent frequency of the heat sink and a phase lag angle amplitude of heat conduction;

[0111] The gasket installation module is configured to install an elastic heat-conducting gasket between the heat sink and the busbar, the elastic heat-conducting gasket being selected according to a compression and rebound characteristic index in the dynamic compensation parameter, and a long axis direction of the elastic heat-conducting gasket being perpendicular to a maximum displacement direction of the phase angle;

[0112] The pre-tightening control module is configured to apply an axial pre-tightening force generated according to a pre-tightening force adjustment coefficient in the dynamic compensation parameter to the fastening bolt of the heat sink, and the axial pre-tightening force is adjusted periodically according to the phase angle.

[0113] The thermal resistance monitoring module is configured to measure a transient thermal resistance value of the interface between the heat sink and the busbar at a wave peak phase angle position and a wave trough phase angle position of the vibration main frequency band, and calculate a thermal resistance change rate from an adjacent wave peak phase angle position to a wave trough phase angle position.

[0114] The parameter updating module is configured to update the pre-tightening force adjustment coefficient and the compression and rebound characteristic index when the thermal resistance change rate exceeds a dynamic response tolerance threshold.

[0115] The preset parameters and the thresholds in the calculation are set by a person skilled in the art according to actual conditions.

[0116] The above embodiments can be realized wholly or partially by software, hardware, firmware or any combination thereof. When realized by software, the above embodiments can be realized in the form of a computer program product wholly or partially.

[0117] Those skilled in the art can realize that the modules and algorithm steps of the examples described in combination with the embodiments disclosed herein can be realized by electronic hardware or a combination of computer software and electronic hardware. Whether the functions are realized by hardware or software depends on the specific application and the constraints of the technical solution. A person skilled in the art can use different methods to realize the described functions for each specific application, but such implementation should not be considered beyond the scope of the present application.

[0118] In addition, the functional modules in each embodiment of the present application can be integrated in one processing module, or each module can exist physically independently, or two or more modules can be integrated in one module.

[0119] In several embodiments provided in the present application, it should be understood that the disclosed system, device and method can be implemented in other manners. For example, the division of the above-described device embodiment is only a logical function division, and there can be another division manner for actual implementation, for example, multiple devices or components can be combined or integrated into another system, or some features can be ignored or not executed. In addition, the displayed or discussed mutual couplings or direct couplings or communication connections between different parts can be indirect couplings or communication connections through some interfaces, devices or modules, and can be in electrical, mechanical or other forms.

[0120] The above describes only the specific embodiments of the present application, but the protection scope of the present application is not limited thereto, and any modification or replacement within the technical range disclosed by the present application can be easily thought by those skilled in the art, and should be included in the protection scope of the present application. Therefore, the protection scope of the present application should be subject to the protection scope of the claims.

[0121] Finally: the above described is only the preferred embodiment of the present application, and is not used to limit the present application, any modification, equivalent replacement, improvement, etc. within the spirit and principle of the present application should be included in the protection scope of the present application.

Claims

1. A heat dissipation method applied to an air switch cabinet, characterized in that: The steps include: S1. Real-time monitoring of ship vibration at the switchgear installation location, extracting the main vibration frequency band and phase angle; S2. Based on the frequency domain overlap factor of the main vibration frequency band and the natural frequency of the radiator, and in conjunction with the amplitude of the heat conduction phase lag angle, determine the dynamic compensation parameters of the connection interface between the radiator and the busbar; S3. Install an elastic thermally conductive gasket between the heat sink and the busbar. The elastic thermally conductive gasket is selected based on the compression-rebound characteristic index in the dynamic compensation parameter, and its long axis direction is perpendicular to the maximum displacement direction of the phase angle. S4. Applying an axial preload force generated by a preload force adjustment coefficient in the dynamic compensation parameter to the radiator fastening bolts, wherein the axial preload force is periodically adjusted with the phase angle; S5. At the peak phase angle position and the trough phase angle position of the main vibration frequency band, synchronously measure the transient thermal resistance value of the connection interface between the heat sink and the busbar, and calculate the thermal resistance change rate from the adjacent peak phase angle position to the trough phase angle position; S6. When the thermal resistance change rate exceeds the dynamic response tolerance threshold, the preload adjustment coefficient and the compression rebound characteristic index are updated; Based on the frequency domain overlap factor of the main vibration frequency band and the natural frequency of the radiator, and in conjunction with the heat conduction phase lag angle amplitude, the dynamic compensation parameters of the connection interface between the radiator and the busbar are determined, including: Obtain the natural frequency of the radiator based on the swept frequency test; The ratio of the intersection bandwidth of the main vibration frequency band and the natural frequency of the radiator to the total bandwidth of the main vibration frequency band is calculated as the frequency domain overlap factor; The vibration displacement signal and the heat flow signal of the radiator interface are synchronously collected by a lock-in amplifier, and the phase difference between the two is calculated as the heat conduction phase lag angle amplitude. Input the frequency domain overlap factor and the heat conduction phase lag angle amplitude into a preset compensation parameter mapping table, and output the compression-rebound characteristic index and preload adjustment coefficient in the dynamic compensation parameters; The compensation parameter mapping table is constructed through orthogonal experiments: The frequency domain overlap factor and the heat conduction phase lag angle amplitude are divided into gradient levels; The fluctuation value of thermal resistance of the heat sink interface was measured under each level combination; The compression-rebound characteristic index and preload adjustment coefficient corresponding to the minimum thermal resistance fluctuation value are selected as mapping output.

2. The heat dissipation method for an air switch cabinet according to claim 1, characterized in that: Real-time monitoring of ship vibration at the switchgear installation location, extraction of the main vibration frequency band and phase angle, including: The ship vibration signal at the switchgear installation location is collected through a three-axis acceleration sensor; Perform bandpass filtering on the ship vibration signal to retain the vibration components within the preset frequency band; Perform fast Fourier transform on the filtered ship vibration signal and extract the frequency component whose energy percentage exceeds the set threshold as the main vibration frequency band; The instantaneous phase angle of the main frequency band of vibration is calculated by Hilbert transform.

3. The heat dissipation method for an air switch cabinet according to claim 2, characterized in that: An elastic thermal pad is set between the radiator and the busbar. The elastic thermal pad is selected based on the compression-rebound characteristic index in the dynamic compensation parameters, and the long axis direction is perpendicular to the maximum displacement direction of the phase angle, including: According to the compression-rebound characteristic index in the dynamic compensation parameter, an elastic thermally conductive gasket that meets the dynamic compression rate and rebound delay requirements is matched from a prefabricated elastic thermally conductive gasket library; The maximum displacement direction of the phase angle is obtained by a vibration displacement sensor; Use a laser locator to calibrate the long axis direction of the elastic thermal pad to ensure that the long axis direction forms a 90-degree perpendicular relationship with the maximum displacement direction; After applying thermal grease on the contact interface between the radiator and the busbar, install the elastic thermal gasket and tighten the bolts to the initial pre-tightening state.

4. The heat dissipation method for an air switch cabinet according to claim 3, characterized in that: An axial preload force generated by the preload force adjustment coefficient in the dynamic compensation parameter is applied to the radiator fastening bolts. The axial preload force is periodically adjusted with the phase angle, including: Extracting preload adjustment coefficient from dynamic compensation parameters; Determine the preload force variation period based on the fundamental frequency of the main vibration frequency band; Get the instantaneous angle value of the phase angle in real time; Based on the instantaneous angle value of the phase angle and the preload adjustment coefficient, the axial preload target value corresponding to the vibration period is generated; The bolt loading device is driven by a hydraulic actuator to apply a mechanical load corresponding to the target value of the axial preload force to the radiator fastening bolts.

5. The heat dissipation method for an air switch cabinet according to claim 4, characterized in that: At the peak phase angle position and trough phase angle position of the main vibration frequency band, the transient thermal resistance value of the connection interface between the heat sink and the busbar is synchronously measured, and the thermal resistance change rate from the adjacent peak phase angle position to the trough phase angle position is calculated, including: Determine the peak phase angle position and the trough phase angle position; When the ship vibration reaches the peak phase angle position, the first transient thermal resistance value of the connection interface between the radiator and the busbar is synchronously collected through the thermocouple array; When the ship vibration reaches the trough phase angle position, the second transient thermal resistance value of the connection interface between the radiator and the busbar is synchronously collected through the thermocouple array; The thermal resistance change rate is obtained by dividing the difference between the first transient thermal resistance value and the second transient thermal resistance value by the first transient thermal resistance value.

6. The heat dissipation method for an air switch cabinet according to claim 5, characterized in that: The peak phase angle position is determined according to the maximum displacement direction of the phase angle, and the trough phase angle position is determined according to the minimum displacement direction of the phase angle.

7. The heat dissipation method for an air switch cabinet according to claim 5, characterized in that: When the thermal resistance change rate exceeds the dynamic response tolerance threshold, the preload adjustment coefficient and compression rebound characteristic indicators are updated, including: comparing the thermal resistance change rate with a preset dynamic response tolerance threshold; When the thermal resistance change rate exceeds the dynamic response tolerance threshold, the preload adjustment coefficient is adjusted based on the excess amplitude of the thermal resistance change rate; The minimum compression rate required for the connection interface between the radiator and the busbar is reversely deduced based on the adjusted preload adjustment coefficient; Re-matching an elastic thermally conductive gasket that meets the compression-rebound characteristic index from the elastic thermally conductive gasket library based on the minimum compression ratio; The original dynamic compensation parameters are covered by the updated preload adjustment coefficient and compression-rebound characteristic indicators.

8. A heat dissipation system for an air switch cabinet, used to implement the heat dissipation method for an air switch cabinet according to any one of claims 1 to 7, characterized in that: Includes the following modules: Vibration monitoring module, used to monitor the ship vibration at the switchgear installation location in real time and extract the main vibration frequency band and phase angle; The parameter decision module is used to determine the dynamic compensation parameters of the connection interface between the radiator and the busbar based on the frequency domain overlap factor of the main vibration frequency band and the natural frequency of the radiator, and the amplitude of the heat conduction phase lag angle; The gasket installation module is used to set an elastic thermal conductive gasket between the radiator and the busbar. The elastic thermal conductive gasket is selected based on the compression-rebound characteristic index in the dynamic compensation parameter, and the long axis direction is perpendicular to the maximum displacement direction of the phase angle; A preload control module is used to apply an axial preload force generated by a preload force adjustment coefficient in a dynamic compensation parameter to the radiator fastening bolts, wherein the axial preload force is periodically adjusted with the phase angle; Thermal resistance monitoring module, used to synchronously measure the transient thermal resistance value of the connection interface between the heat sink and the busbar at the peak phase angle position and the trough phase angle position of the main vibration frequency band, and calculate the thermal resistance change rate from the adjacent peak phase angle position to the trough phase angle position; The parameter update module is used to update the preload adjustment coefficient and the compression rebound characteristic index when the thermal resistance change rate exceeds the dynamic response tolerance threshold.

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