Quality inspection method and system for cooling system of refrigerant direct-cooling laser

Abstract

The invention belongs to the technical field of laser equipment, and discloses a quality inspection method for a refrigerant direct cooling laser cooling system, which comprises the following steps: acquiring an environment temperature, setting a starting parameter according to the environment temperature, and starting a quality inspection system and a cooling system according to the starting parameter. After a quality inspection system and a cooling system are started, quality inspection data are obtained, and the quality inspection data comprise the cold plate temperature, the superheat degree and the condensing coil pipe temperature; and comparing whether the cold plate temperature, the superheat degree and the condensing coil temperature are consistent, if so, determining that the cooling system is qualified, and if not, determining that the cooling system is unqualified. According to the invention, the purposes of simple quality inspection process, time saving, low cost and full inspection can be achieved. The invention also discloses a quality inspection system for the cooling system of the refrigerant direct-cooling laser.

Description

Technical Field

[0001] The present invention belongs to the technical field of laser devices, and particularly relates to a quality inspection method and system for a cooling system of a refrigerant direct-cooled laser. Background Art

[0002] For a direct-cooled cooling system constructed by using copper pipe welding and refrigerant filling processes, the process consistency of its refrigeration efficiency directly affects the temperature control accuracy of the laser. Due to small deviations in process parameters such as the welding tightness of the refrigerant circulation path and the refrigerant filling amount, fluctuations in the system's refrigeration capacity will occur, which will directly cause temperature oscillations in the cooled device, and in severe cases, even lead to thermal runaway.

[0003] Currently, the industry generally uses the whole machine environmental simulation test method for quality control. This quality inspection method has the following technical defects: (1) It is necessary to build a high and low temperature test chamber and configure optical detection devices such as optical power meters, and the single quality inspection takes a long time; (2) Limited by the capacity of the detection equipment and the test cost, the actual quality inspection coverage rate is insufficient, so only sampling inspection can be carried out; (3) If an abnormality in the cooling system is found during the quality inspection process, it is necessary to reverse-disassemble the assembled optical module and electronic module. The disassembly process causes a high pollution rate of the optical mirror surface and a high repair damage rate of the circuit board. This defect tracing method for the subsequent process not only increases the processing cost of a single defective product, but also makes it difficult to effectively break through the overall production yield.

[0004] Therefore, the above technical pain points seriously restrict the mass production stability of the laser, and the existing quality inspection methods can no longer meet the process requirements. Summary of the Invention

[0005] In order to solve the above technical problems, the present invention discloses a quality inspection method for a cooling system of a refrigerant direct-cooled laser, which can meet the purposes of simple, time-saving, low-cost quality inspection process and full inspection. The present invention also discloses a quality inspection system for a cooling system of a refrigerant direct-cooled laser.

[0006] The specific technical solutions of the present invention are as follows:

[0007] A quality inspection method for a cooling system of a refrigerant direct-cooled laser, comprising:

[0008] Obtaining the ambient temperature, setting start parameters according to the ambient temperature, and turning on the quality inspection system and the cooling system according to the start parameters;

[0009] After turning on the quality inspection system and the cooling system, obtaining quality inspection data, where the quality inspection data includes cold plate temperature, superheat degree, and condensing coil temperature;

[0010] Comparing whether the cold plate temperature, superheat degree, and condensing coil temperature are consistent. If they are consistent, the cooling system is qualified; if they are not consistent, the cooling system is unqualified.

[0011] Preferably, the startup parameters include the compressor frequency, the fan air speed, the heating power of the heating block, the opening degree of the main valve, and the opening degree of the auxiliary valve.

[0012] Preferably, with the ambient temperature as a variable, simulate and calculate the refrigerating capacity of the compressor, and obtain the compressor frequency at the current ambient temperature according to the refrigerating capacity;

[0013] Simulate multiple times, linearly process the ambient temperature and the compressor frequency based on multiple simulation results, so as to obtain the compressor frequency at the current ambient temperature according to the actual ambient temperature.

[0014] Preferably, with the ambient temperature as a variable, simulate and calculate the heat power of the compressor;

[0015] Simulate multiple times, linearly process the ambient temperature and the heat power of the compressor based on multiple simulation results, so as to obtain the heat power of the compressor at the current ambient temperature according to the actual ambient temperature;

[0016] Obtain the heat power of the heating block, and obtain the total heat dissipation of the cooling system within a preset time according to the heat power of the compressor and the heat power of the heating block;

[0017] Obtain the fan speed according to the total heat dissipation.

[0018] Preferably, with the ambient temperature as a variable, simulate and calculate the refrigerant flow rate through the main valve;

[0019] Simulate multiple times, linearly process the ambient temperature and the refrigerant flow rate through the main valve based on multiple simulation results, so as to obtain the refrigerant flow rate through the main valve at the current ambient temperature according to the actual ambient temperature;

[0020] Obtain the refrigerant density, and obtain a first flow coefficient according to the refrigerant density and the refrigerant flow rate through the main valve at the current ambient temperature;

[0021] Obtain the condensation pressure at the current ambient temperature and the evaporation pressure of the cooling system, and obtain a first pressure difference between the two;

[0022] Obtain the opening degree of the main valve according to the above-mentioned first flow coefficient and first pressure difference.

[0023] Preferably, with the ambient temperature as a variable, simulate and calculate the refrigerating capacity of the compressor, and obtain the compressor frequency at the current ambient temperature according to the refrigerating capacity;

[0024] Simulate multiple times, linearly process the ambient temperature and the compressor frequency based on multiple simulation results, so as to obtain the compressor frequency at the current ambient temperature according to the actual ambient temperature;

[0025] With the ambient temperature as a variable, simulate and calculate the refrigerant flow rate through the main valve;

[0026] Perform multiple simulations, linearly process the ambient temperature and the refrigerant flow rate through the main valve based on multiple simulation results, so as to obtain the refrigerant flow rate through the main valve at the current ambient temperature according to the actual ambient temperature;

[0027] Obtain the compressor displacement;

[0028] According to the compressor displacement, as well as the compressor frequency and the refrigerant flow rate through the main valve at the current ambient temperature, obtain the refrigerant flow rate through the auxiliary valve at the current ambient temperature;

[0029] Obtain the refrigerant density, and according to the refrigerant density and the refrigerant flow rate through the auxiliary valve at the current ambient temperature, obtain the flow coefficient two;

[0030] Obtain the condensation pressure at the current ambient temperature and the evaporation pressure of the cooling system, and obtain the pressure difference two between the two;

[0031] According to the above-mentioned flow coefficient two and pressure difference two, obtain the opening degree of the auxiliary valve.

[0032] Preferably, when comparing whether the cold plate temperature, superheat degree, and condensation coil temperature are consistent, compensate for system errors and / or measurement errors.

[0033] Preferably, each item in the quality inspection data has a preset numerical range. Determine whether any item in the quality inspection data is within the preset numerical range. If so, the cooling system is qualified; if not, the cooling system is unqualified.

[0034] Preferably, it further includes:

[0035] Obtain the identification information on the cooling system and match the identification information to the quality inspection data.

[0036] A quality inspection system for a refrigerant direct-cooled laser cooling system, including:

[0037] A loading mechanism, which can drive the cooling system to switch between the loading position and the quality inspection position;

[0038] A fan, which is located above the quality inspection position and can switch between the working position one and the standby position one, and is used to dissipate heat from the condenser of the cooling system at the working position one;

[0039] A heating block, which is located on one side of the quality inspection position and can switch between the working position two and the standby position two, and is used to closely adhere to the cold plate of the cooling system at the working position two;

[0040] An ambient temperature sensor, which is used to detect the ambient temperature;

[0041] A sensor assembly, which is used to detect the temperature data of the cooling system at the quality inspection position;

[0042] A controller, which stores preset information. The controller controls the fan, heating block, and cooling system according to the ambient temperature and preset information. The controller also determines whether the cooling system is qualified based on the temperature data fed back by the sensor assembly.

[0043] Compared with the prior art, the present invention can achieve automated full inspection, effectively improve the quality inspection efficiency, and thus effectively improve the production efficiency and product yield. The present invention also incorporates the ambient temperature data, making the entire quality inspection more adaptable to the environment and thus improving the accuracy of quality inspection. BRIEF DESCRIPTION OF THE DRAWINGS

[0044] Figure 1 It is a schematic diagram of the quality inspection principle in an embodiment of the present invention;

[0045] Figure 2 It is a schematic diagram of the quality inspection system in an embodiment of the present invention;

[0046] Figure 3 It is another direction schematic diagram of the quality inspection system in an embodiment of the present invention.

[0047] In the figure: 100 - cooling system; 200 - quality inspection system; 1 - compressor; 2 - condenser; 3 - cold plate; 4 - main valve; 5 - auxiliary valve; 6 - fan; 7 - heating block; 8 - ambient temperature sensor; 9 - controller; 10 - feeding mechanism; 11 - pushing mechanism one; 12 - pushing mechanism two; 13 - temperature sensor one; 14 - temperature sensor two; 15 - temperature sensor three; 16 - temperature sensor four; 17 - scanner; 18 - clamping mechanism; 19 - position sensor. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0048] In order to enable those skilled in the art to better understand the technical solutions of the present invention, the present invention will be further described in detail below in conjunction with the specific embodiments.

[0049] As Figure 1As shown, in this embodiment, the cooling system 100 includes a compressor 1, a condenser 2, a cold plate 3, a main valve 4, an auxiliary valve 5, and a copper tube assembly. The quality inspection system 200 includes a fan 6, a heating block 7, an ambient temperature sensor 8, a sensor assembly, and a controller 9. Specifically, a heating block 7 is installed on the cold plate 3, and the heat of the heating block 7 is transferred to the cold plate 3. The cold plate 3 is embedded with a copper tube. The liquid refrigerant in the copper tube evaporates and takes away the heat transferred by the heating block 7. It evaporates into a gaseous refrigerant and enters the compressor 1. The compressor 1 compresses the evaporated gaseous refrigerant into a high-temperature and high-pressure gaseous refrigerant. The high-temperature and high-pressure refrigerant is condensed into a liquid refrigerant in the condenser 2. The condensed liquid refrigerant is throttled by the main valve 4 and becomes a low-temperature liquid refrigerant. It then re-enters the cold plate 3 to form a heat cycle. The high-temperature and high-pressure gaseous refrigerant passes through the auxiliary valve 5 and mixes with the liquid refrigerant to enter the cold plate 3, and a cycle is also formed at the same time. In this embodiment, the auxiliary valve 5 can adjust the evaporation pressure in the cold plate 3.

[0050] In this embodiment, the controller 9 is connected to the cooling system 100 and the quality inspection system 200 through a communication line, and can send data and instructions. The controller 9 sends instructions to adjust the compressor 1, the fan 6, the main valve 4, and the auxiliary valve 5 through the communication line, and reads the temperature of the cold plate 3, the evaporator inlet temperature, the evaporator outlet temperature, the condensing coil temperature, and the ambient temperature through the controller 9 to determine whether the cooling system 100 is qualified. The condensing coil temperature is the temperature at the condenser 2. The evaporator inlet temperature and the evaporator outlet temperature are the temperatures at both ends of the cold plate 3.

[0051] Generally, for the same cooling system 100, if at a certain ambient temperature, the compressor 1 frequency is the same, the fan 6 wind speed is the same, the heating power of the heating block 7 is the same, the main valve 4 opening is the same, and the auxiliary valve 5 opening is the same, then ideally, the cold plate 3 temperature, condensation temperature, and superheat should be the same. Considering the system error and measurement error, the cold plate 3 temperature, condensation temperature, and superheat should be qualified within a certain range. It should be noted that the superheat is the difference between the evaporator outlet temperature and the evaporator inlet temperature.

[0052] Since the ambient temperature may change during the use of the quality inspection system 200 , if the ambient temperature is not introduced into the control of the quality inspection system 200 and the cooling system 100 , the final quality inspection result may be affected.

[0053] Therefore, in this embodiment, a quality inspection method for a refrigerant direct-cooling laser cooling system 100 includes:

[0054] S100, obtaining the ambient temperature, setting the startup parameters according to the ambient temperature, and starting the quality inspection system 200 and the cooling system 100 according to the startup parameters;

[0055] After starting the quality inspection system 200 and the cooling system 100, obtain quality inspection data, where the quality inspection data includes the temperature of the cold plate 3, the superheat degree, and the temperature of the condensation coil.

[0056] S300. Compare whether the temperature of the cold plate 3, the superheat degree, and the temperature of the condensation coil are consistent. If they are consistent, the cooling system 100 is qualified; if not, the cooling system 100 is unqualified.

[0057] Furthermore, the starting parameters include the frequency of the compressor 1, the wind speed of the fan 6, the heating power of the heating block 7, the opening degree of the main valve 4, and the opening degree of the auxiliary valve 5.

[0058] In this embodiment, the method for obtaining the frequency of the compressor 1 is as follows:

[0059] S111. Taking the ambient temperature as a variable, simulate and calculate the refrigerating capacity of the compressor 1, and obtain the frequency of the compressor 1 at the current ambient temperature according to the refrigerating capacity.

[0060] S112. Conduct multiple simulations, linearly process the ambient temperature and the frequency of the compressor 1 based on multiple simulation results, so as to obtain the frequency of the compressor 1 at the current ambient temperature according to the actual ambient temperature.

[0061] Specifically, on the premise of ensuring that the refrigerating capacity is basically the same at different ambient temperatures, according to the results of multiple simulations, the following Table 1 is formed.

[0062] Relationship Table 1 of Ambient Temperature and Compressor Frequency

[0063] Serial number Ambient temperature / °C Compressor frequency / Hz Cooling capacity / W 1 5 30 4011 2 10 32 4016 3 15 34 4000 4 20 36 4020 5 25 38 4013 6 30 40 4029

[0064] Perform linear processing on the ambient temperature and the frequency of the compressor 1 to obtain Formula 1:

[0065] H = 0.4×T + 28 (Formula 1)

[0066] Wherein, H is the frequency of the compressor 1, with the unit of Hz; T is the ambient temperature, with the unit of °C.

[0067] Thus, through Formula 1, the application frequency of the compressor 1 can be directly calculated according to the ambient temperature.

[0068] In this embodiment, the method for obtaining the rotational speed of the fan 6 is as follows:

[0069] S121. Taking the ambient temperature as a variable, simulate and calculate the heat power of the compressor 1.

[0070] S122. Conduct multiple simulations, linearly process the ambient temperature and the heat power of the compressor 1 based on multiple simulation results, so as to obtain the heat power of the compressor 1 at the current ambient temperature according to the actual ambient temperature.

[0071] S123. Obtain the thermal power of the heating block 7, and obtain the total heat dissipation of the cooling system 100 within a preset time according to the thermal power of the compressor 1 and the thermal power of the heating block 7;

[0072] S124. Obtain the rotational speed of the fan 6 according to the total heat dissipation.

[0073] Specifically, according to the results of multiple simulations, Table 2 below is formed.

[0074] Table 2 Relationship between ambient temperature and compressor thermal power

[0075] Serial number Ambient temperature / °C Compressor thermal power / W 1 5 221 2 10 333 3 15 452 4 20 585 5 25 727 6 30 877

[0076] Perform linear processing on the ambient temperature and the thermal power of the compressor 1 to obtain Formula 2:

[0077] Q 压缩机 =26×T + 80 (Formula 2)

[0078] Wherein, Q 压缩机 is the thermal power of the compressor, in W; T is the ambient temperature, in °C.

[0079] Thus, through Formula 2, the thermal power of the compressor 1 can be directly calculated according to the ambient temperature.

[0080] After determining the model of the heating block 7, its thermal power is constant. Therefore, the heat dissipation that the compressor 1 needs to achieve can be obtained through the following Formula 3.

[0081] W = Q 加热块 t1 + Q 压缩机 t1 (Formula 3)

[0082] Wherein, W is the total heat, in J; Q 压缩机 is the thermal power of the compressor, in W; Q 加热块 is the thermal power of the heating block, in W; t1 is the working time of the heating block 7 and the compressor 1, in s.

[0083] It can be known that the heat dissipation that the compressor 1 needs to achieve is related to the specific heat capacity of air, the mass of air flowing through the condenser 2, and the temperature difference between the outlet air and the inlet air, that is, Formula 4.

[0084] W = c×m×ΔT (Formula 4)

[0085] Wherein, W is the total heat, in J; c is the specific heat capacity of air, in J / (kg·°C); m is the mass of air flowing through the condenser 2, in kg; ΔT is the temperature difference between the outlet air and the inlet air, generally taking 10°C to 15°C, and 15°C is selected for the system in this embodiment.

[0086] The air quality flowing through the condenser 2 can be obtained by the following Formula Five. After determining the model of the fan 6, the dimensional parameters of the fan 6 become fixed values.

[0087] m = S × V × t2 × ρ1 (Formula Five)

[0088] Where, m is the air quality flowing through the condenser 2, in kg; S is the flow area of the fan 6, in m 2 ; V is the wind speed of the fan 6, in m / s; t2 is the running time of the fan 6, in s; ρ1 is the air density, in kg / m 3 ; π is the pi.

[0089] Thus, after obtaining the wind speed blown by the fan 6, the rotational speed of the fan 6 can be obtained through the following Formula Six.

[0090]

[0091] Where, V is the wind speed of the fan 6, in m / s; D is the diameter of the fan blade of the fan 6, in m; n is the rotational speed of the fan 6, in r / min; K is an empirical coefficient.

[0092] Thus, through Formulas Two to Six, Formula Seven is obtained by arrangement:

[0093]

[0094] Where, n is the rotational speed of the fan 6, in r / min; Q_compressor1 is the heat power of the compressor 1, in W; T is the ambient temperature, in °C; c is the specific heat capacity of air, in J / (kg·°C); S is the flow area of the fan 6, in m 2 ; K is an empirical coefficient; π is the pi; D is the diameter of the fan blade of the fan 6, in m; ρ1 is the air density, in kg / m 3 ; ΔT is the temperature difference between the outlet air and the inlet air, generally taking 10°C to 15°C, and 15°C is selected for the system in this embodiment.

[0095] Thus, through Formula Seven, the rotational speed of the fan 6 can be calculated according to the ambient temperature.

[0096] In this embodiment, the method for obtaining the opening degree of the main valve 4 is as follows:

[0097] S131. Taking the ambient temperature as a variable, simulating and calculating the refrigerant flow rate passing through the main valve 4;

[0098] S132. Simulating multiple times, linearly processing the ambient temperature and the refrigerant flow rate passing through the main valve 4 based on multiple simulation results, so as to obtain the refrigerant flow rate passing through the main valve 4 at the current ambient temperature according to the actual ambient temperature;

[0099] S133. Obtain the refrigerant density, and based on the refrigerant density and the refrigerant flow rate through the main valve 4 at the current ambient temperature, obtain the first flow coefficient;

[0100] S134. Obtain the condensation pressure at the current ambient temperature and the evaporation pressure of the cooling system 100, and obtain the first pressure difference;

[0101] S135. Based on the above first flow coefficient and first pressure difference, obtain the opening degree of the main valve 4.

[0102] Specifically, according to the results of multiple simulations, form Table 3 and Table 4 below.

[0103] Table 3 of the relationship between ambient temperature and refrigerant flow rate

[0104] Serial number Ambient temperature / °C Refrigerant flow rate / g / s 1 5 19.955 2 10 20.792 3 15 21.726 4 20 22.779 5 25 23.982 6 30 25.377

[0105] Table 4 of the relationship between ambient temperature and condensation pressure

[0106] Serial number Ambient temperature / °C Condensing temperature / °C Condensing pressure / MPa 1 5 20 1.4476 2 10 25 1.6574 3 15 30 1.8893 4 20 35 2.1449 5 25 40 2.4256 6 30 45 2.7335

[0107] Perform a linear treatment on the ambient temperature and the refrigerant flow rate to obtain Formula VIII:

[0108] m1 = 0.2×T + 19 (Formula VIII)

[0109] Where, m1 is the main valve flow rate, unit g / s; T is the ambient temperature, unit °C.

[0110] According to the selection of the refrigerant, its flow coefficient can be obtained, such as Formula IX:

[0111]

[0112] Where, K D is the flow coefficient; ρ2 is the density of the refrigerant, unit kg / m 3 .

[0113] Based on this, the flow area of the main valve at this time can be obtained through Formula X:

[0114]

[0115] Where, m1 is the flow rate of the main valve 4, unit g / s; KD is the flow coefficient; A is the flow area of the main valve 4; ρ2 is the density of the refrigerant, unit kg / m 3 ; P1 is the condensation pressure, unit MPa; P2 is the evaporation pressure, unit MPa.

[0116] It should be noted that the condensation pressure P1 is related to the ambient temperature and increases with the increase of the ambient temperature, which can be obtained by referring to Table 4; after the components of the entire cooling system 100 are determined, the evaporation temperature range and the refrigerant type are known, and thus the evaporation pressure P2 can be known by referring to the thermodynamic property table of the refrigerant.

[0117] After the main valve 4 is fully opened, the shape of the medium passing through the main valve 4 is circular. Therefore, after the main valve 4 is fully opened, the maximum flow area of the main valve 4 is circular. At this time, the step number of the main valve 4 reaching the corresponding opening can be obtained through the proportional relationship. See Formula Eleven:

[0118]

[0119] Wherein, A is the current flow area of the main valve 4, with the unit of m 2 ; A max is the maximum flow area of the main valve 4, with the unit of m 2 ; h1 is the current calculation step number of the main valve 4; h2 is the step number when the main valve 4 reaches the maximum flow area.

[0120] In the above formula, after the model of the main valve 4 is selected, h2 is a fixed value.

[0121] Therefore, according to Formulas Eight to Eleven, Formula Twelve is obtained after arrangement:

[0122]

[0123] Wherein, T is the ambient temperature, with the unit of °C; ρ2 is the density of the refrigerant, with the unit of kg / m 3 ; π is the pi; d1 is the flow aperture of the main valve 4, with the unit of m; P1 is the condensation pressure, with the unit of MPa; P2 is the evaporation pressure, with the unit of MPa.

[0124] Therefore, through Formula Twelve, the opening of the main valve 4 can be calculated according to the ambient temperature.

[0125] In this embodiment, the method for obtaining the opening of the auxiliary valve 5 is as follows:

[0126] S141. Taking the ambient temperature as a variable, simulate and calculate the refrigerating capacity of the compressor 1, and obtain the frequency of the compressor 1 at the current ambient temperature according to the refrigerating capacity;

[0127] S142. Simulate multiple times, linearly process the ambient temperature and the frequency of the compressor 1 based on multiple simulation results, so as to obtain the frequency of the compressor 1 at the current ambient temperature according to the actual ambient temperature;

[0128] S143. Taking the ambient temperature as a variable, simulate and calculate the refrigerant flow rate passing through the main valve 4;

[0129] Perform multiple simulations, linearly process the ambient temperature and the refrigerant flow rate through the main valve 4 based on multiple simulation results, so as to obtain the refrigerant flow rate through the main valve 4 at the current ambient temperature according to the actual ambient temperature;

[0130] S144. Obtain the displacement of the compressor 1;

[0131] S145. According to the displacement of the compressor 1, as well as the frequency of the compressor 1 and the refrigerant flow rate through the main valve 4 at the current ambient temperature, obtain the refrigerant flow rate through the auxiliary valve 5 at the current ambient temperature;

[0132] S146. Obtain the refrigerant density, and according to the refrigerant density and the refrigerant flow rate through the auxiliary valve 5 at the current ambient temperature, obtain the flow coefficient two;

[0133] S147. Obtain the condensation pressure at the current ambient temperature and the evaporation pressure of the cooling system 100, and obtain the pressure difference two;

[0134] S148. According to the above-mentioned flow coefficient two and pressure difference two, obtain the opening degree of the auxiliary valve 5.

[0135] According to Formula One, the frequency of the compressor 1 can be obtained. After the components of the entire cooling system 100 are determined, the displacement of the compressor 1 can be obtained. In the design or operation analysis of the compressor 1, the suction gas density is a known parameter. Therefore, the refrigerant flow rate through the auxiliary valve 5 can be obtained through the following Formula Thirteen and Formula Fourteen.

[0136]

[0137] m2 = m3 - m1 (Formula Fourteen)

[0138] Wherein, Vp is the displacement of the compressor 1, with the unit of m 3 / r; H is the frequency of the compressor 1, with the unit of Hz; ρ3 is the suction gas density, with the unit of kg / m 3 ; m2 is the auxiliary valve 5, with the unit of g / s; m3 is the compressor 1 flow rate, with the unit of g / s; m1 is the main valve 4 flow rate, with the unit of g / s.

[0139] Meanwhile, based on the application principles of Formula Nine, Formula Ten, and Formula Eleven, the formula can be sorted out, and the opening degree of the auxiliary valve 5 can be obtained, as shown in Formula Fifteen:

[0140]

[0141] Wherein, T is the ambient temperature, with the unit of °C; ρ2 is the density of the refrigerant, with the unit of kg / m 3 ; π is the pi; d2 is the flow aperture of the auxiliary valve 5, with the unit of m; P1 is the condensation pressure, with the unit of MPa; P2 is the evaporation pressure, with the unit of MPa.

[0142] Thus, according to Equation XV, the opening degree of the main valve 4 can be calculated based on the ambient temperature.

[0143] Thus, by obtaining the starting parameters of the compressor 1 frequency, the fan 6 wind speed, the heating block 7 heating power, the main valve 4 opening degree, and the auxiliary valve 5 opening degree according to the ambient temperature, the cooling system 100 and the quality inspection system 200 can be started according to the starting parameters to perform quality inspection on the cooling system 100. Generally, due to system errors and / or measurement errors in actual equipment, when comparing whether the cold plate 3 temperature, the superheat degree, and the condensing coil temperature are consistent, it is necessary to compensate for the system errors and / or measurement errors. Further, each item in the quality inspection data has a preset numerical range, and it is determined whether any item in the quality inspection data is within the preset numerical range. If so, the cooling system 100 is qualified; if not, the cooling system 100 is unqualified. Let the quality inspection error range of the cold plate 3 be [-T1, T1], the quality inspection error range of the condensing coil temperature be [-T2, T2], and the quality inspection error range of the superheat degree be [-T3, T3]. Then, when the quality inspection temperature of the cold plate 3 is within the interval [T1 set - T1, T1 set + T1], the quality inspection temperature of the condensing coil temperature is within the interval [T2 set - T2, T2 set + T2], and the superheat degree is within the interval [T3 set - T3, T3 set + T3], and the cold plate 3 temperature, the superheat degree, and the condensing coil temperature are consistent within the error range, the product is qualified.

[0144] In this embodiment, it further includes the step of: obtaining the identification information on the cooling system 100 and matching the identification information to the quality inspection data. That is, the cooling system 100 has identification information such as two-dimensional code or bar code or NFC or RFID, etc. By obtaining the identification information, the quality inspection system 200 can give a quality inspection result corresponding to the cooling system 100.

[0145] Such as Figure 2 and Figure 3As shown, in this embodiment, a quality inspection system 200 for a refrigerant direct cooling laser cooling system 100 is also disclosed, which includes a feeding mechanism 10, a fan 6, a heating block 7, an ambient temperature sensor 8, a sensor assembly, and a controller 9; the feeding mechanism 10 can drive the cooling system 100 to switch between the feeding position and the quality inspection position; the fan 6 is located above the quality inspection position and can switch between the working position 1 and the standby position 1, and is used to dissipate heat from the condenser 2 of the cooling system 100 at the working position 1. The fan 6 realizes the position switching through the action of the first pushing mechanism 11; the heating block 7 is located on one side of the quality inspection position and can switch between the working position 2 and the standby position 2, and is used to closely adhere to the cold plate 3 of the cooling system 100 at the working position 2. The heating block 7 realizes the position switching through the action of the second pushing mechanism 12; the ambient temperature sensor 8 is used to detect the ambient temperature; the sensor assembly is used to detect the temperature data of the cooling system 100 at the quality inspection position; the controller 9 stores preset information. The controller 9 controls the operation of the cooling system 100 and the quality inspection system 200 according to the ambient temperature and the preset information. The controller 9 also judges whether the cooling system 100 is qualified according to the temperature data fed back by the sensor assembly. Further, the sensor assembly includes a first temperature sensor 13, a second temperature sensor 14, a third temperature sensor 15, and a fourth temperature sensor 16, which are respectively used to detect the temperature at the outlet of the evaporator, the temperature at the inlet of the evaporator, the temperature of the condenser, and the temperature of the cold plate 3.

[0146] In this embodiment, the feeding mechanism 10 is a belt mechanism, a roller mechanism, or a cylinder pushing mechanism. The cooling system 100 is placed on the feeding mechanism 10, so that the feeding mechanism 10 drives the cooling system 100 to the quality inspection position of the quality inspection system 200. On the movement path of the cooling system 100, a barcode scanner 17 is provided on the cooling system 100 to obtain the number of the cooling system 100, so that the subsequent data corresponds to the number of the quality inspection product. The cooling system 100 is provided with a distance sensor or a pressure sensor at the quality inspection position. When the cooling system 100 triggers the distance sensor or the pressure sensor at the quality inspection position, the fan 6 is driven to move from top to bottom so that it can be aligned with the condenser 2 to dissipate heat from the condenser 2; at the same time, the heating block 7 moves to closely adhere to the cold plate 3, so that the heating block 7 can heat the cold plate 3 well. When the cooling system 100 arrives, the reserved wire harness of the quality inspection system 200 is used to connect the cooling system 100 to realize the product to be inspected. Then turn on the machine, and the controller 9 obtains the ambient temperature. After calculating the start parameters, the cooling system 100 and the quality inspection system 200 are started, so as to judge whether the cooling system 100 is qualified. The controller 9 is a controller component with a central processing unit and can be directly used by the staff of the quality inspection system 200.

[0147] To ensure the quality inspection stability of the cooling system 100, a clamping mechanism 18 is also provided on the loading mechanism 10. After the cooling system 100 is in place, the cooling system 100 can be clamped by the clamping mechanism 18, thereby avoiding or reducing quality inspection errors. The clamping mechanism 18 is composed of a clamping cylinder. The clamping mechanism 18 clamps the cooling system 100 at the loading position to move to the quality inspection position along with the drive of the loading mechanism 10.

[0148] In addition, in this embodiment, the quality inspection system 200 is also provided with a position sensor 19, which can be used to detect whether the fan 6 and the heating block 7 are in place. That is to say, after detecting that the fan 6 and the heating block 7 are in place, after ensuring that the fan 6 and the heating block 7 can perform normal actions, the quality inspection of the cooling system 100 is carried out.

[0149] Thus, the quality inspection of the cooling system 100 is realized through the following process:

[0150] Connect the power cord of the quality inspection system 200 to the distribution box, turn on the air switch, turn on the key switch, power on the device, and the controller 9 calculates the frequency of the compressor 1, the rotation speed of the fan 6, the opening degree of the main valve 4, and the opening degree of the auxiliary valve 5 according to the data collected by the ambient temperature sensor, and prepares to quality inspect the cooling system 100. Then place the cooling system 100 on the loading mechanism 10 of the quality inspection system 200, and use the barcode scanner 17 to obtain the identification information of the cooling mechanism. The barcode scanner 17 transmits the signal wirelessly to the controller 9, and the controller 9 records the number, corresponding to the data in the quality inspection process. Next, place the cooling system 100 at the loading position, clamp the cooling system 100 through the clamping mechanism 18, and electrically connect the relevant wire harnesses between the cooling system 100 and the quality inspection system 200. Then press the automatic detection button on the operation panel of the quality inspection system 200, and the loading mechanism 10 drives the cooling system 100 to the quality inspection position. After arriving, the pressing cylinder of the fan 6 lowers the fan 6, and the heating block 7 is also pressed against the cold plate 3 under the push of the cylinder. Then each actuator moves to the calculated parameters, that is, the compressor 1 to the calculated frequency, the fan 6 to the calculated rotation speed, the main valve 4 to the calculated opening degree, and the auxiliary valve 5 to the calculated opening degree. After the preparation is completed, the controller 9 controls the heating block 7 to start heating, and officially enters the test, and the controller 9 records the data. Finally, the controller 9 records the temperature data of the cold plate 3, the temperature data of the condenser, and the superheat data, compares the three data, and judges whether each data is within the corresponding set range. If the above conditions are met, the product is qualified; if the above conditions are not met, the product is judged unqualified.

[0151] Thus, through this embodiment, batch detection of the laser refrigerant direct cooling system 100 can be achieved. By means of algorithms, the environmental adaptability of the quality inspection system 200 can be improved, enabling accurate quality inspection of the cooling system 100 in various temperature environments, and automatic detection of the cooling system 100 with automatic recording of detection data. Furthermore, this embodiment adopts an automated detection method, effectively improving the quality inspection efficiency, greatly enhancing the production efficiency, having stronger environmental adaptability and accuracy, achieving full inspection of the cooling system 100, and improving the production yield.

[0152] The above is only the preferred embodiment of the present invention. It should be noted that the above preferred embodiment should not be regarded as a limitation of the present invention. The protection scope of the present invention should be defined by the scope of the claims. For those of ordinary skill in the art, without departing from the spirit and scope of the present invention, several improvements and refinements can be made, and these improvements and refinements should also be regarded as within the protection scope of the present invention.

Claims

1. A quality inspection method for a refrigerant direct-cooling laser cooling system, characterized in that, Including: Obtain the ambient temperature, set startup parameters according to the ambient temperature, and turn on the quality inspection system and the cooling system according to the startup parameters; After turning on the quality inspection system and the cooling system, obtain quality inspection data, where the quality inspection data includes cold plate temperature, superheat degree, and condensing coil temperature; Compare whether the cold plate temperature, superheat degree, and condensing coil temperature are consistent. If they are consistent, the cooling system is qualified; if not, the cooling system is unqualified.

2. The quality inspection method of a refrigerant direct cooling laser cooling system according to claim 1, characterized in that, The startup parameters include compressor frequency, fan wind speed, heating block heating power, main valve opening degree, and auxiliary valve opening degree.

3. The quality inspection method of a refrigerant direct cooling laser cooling system according to claim 2, characterized in that Taking the ambient temperature as a variable, simulate and calculate the refrigerating capacity of the compressor, and obtain the compressor frequency at the current ambient temperature according to the refrigerating capacity; Simulate multiple times, linearly process the ambient temperature and the compressor frequency based on multiple simulation results, so as to obtain the compressor frequency at the current ambient temperature according to the actual ambient temperature.

4. The quality inspection method of a refrigerant direct cooling laser cooling system according to claim 2, characterized in that, Taking the ambient temperature as a variable, simulate and calculate the heat power of the compressor; Simulate multiple times, linearly process the ambient temperature and the compressor heat power based on multiple simulation results, so as to obtain the compressor heat power at the current ambient temperature according to the actual ambient temperature; Obtain the heat power of the heating block, and obtain the total heat dissipation of the cooling system within a preset time according to the compressor heat power and the heating block heat power; Obtain the fan speed according to the total heat dissipation.

5. The quality inspection method of a refrigerant direct cooling laser cooling system according to claim 2, characterized in that Taking the ambient temperature as a variable, simulate and calculate the refrigerant flow rate through the main valve; Simulate multiple times, linearly process the ambient temperature and the refrigerant flow rate through the main valve based on multiple simulation results, so as to obtain the refrigerant flow rate through the main valve at the current ambient temperature according to the actual ambient temperature; Obtain the refrigerant density, and obtain flow coefficient one according to the refrigerant density and the refrigerant flow rate through the main valve at the current ambient temperature; Obtain the condensing pressure at the current ambient temperature and the evaporation pressure of the cooling system, and obtain pressure difference one between the two; Obtain the main valve opening degree according to the above flow coefficient one and pressure difference one.

6. The quality inspection method of a refrigerant direct cooling laser cooling system according to claim 2, characterized in that, Taking the ambient temperature as a variable, simulate and calculate the refrigerating capacity of the compressor, and obtain the compressor frequency at the current ambient temperature according to the refrigerating capacity; Simulate multiple times, linearly process the ambient temperature and the compressor frequency based on multiple simulation results, so as to obtain the compressor frequency at the current ambient temperature according to the actual ambient temperature; Taking the ambient temperature as a variable, simulate and calculate the refrigerant flow rate through the main valve; Simulate multiple times, linearly process the ambient temperature and the refrigerant flow rate through the main valve based on multiple simulation results, so as to obtain the refrigerant flow rate through the main valve at the current ambient temperature according to the actual ambient temperature; Obtain the compressor displacement; According to the compressor displacement, as well as the compressor frequency and the refrigerant flow rate through the main valve at the current ambient temperature, obtain the refrigerant flow rate through the auxiliary valve at the current ambient temperature; Obtain the refrigerant density, and obtain flow coefficient two according to the refrigerant density and the refrigerant flow rate through the auxiliary valve at the current ambient temperature; Obtain the condensing pressure at the current ambient temperature and the evaporation pressure of the cooling system, and obtain pressure difference two between the two; Obtain the auxiliary valve opening degree according to the above flow coefficient two and pressure difference two.

7. The quality inspection method of a refrigerant direct cooling laser cooling system according to claim 1, characterized in that, When comparing whether the cold plate temperature, superheat degree, and condensing coil temperature are consistent, compensate for system errors and / or measurement errors.

8. The quality inspection method of a refrigerant direct cooling laser cooling system according to claim 1, characterized in that, Each item in the quality inspection data has a preset numerical range. It is determined whether any item in the quality inspection data is within the preset numerical range. If so, the cooling system is qualified; if not, the cooling system is unqualified.

9. A quality inspection method for a refrigerant direct cooling laser cooling system according to claim 1, characterized in that, It further includes: Obtain the identification information on the cooling system and match the identification information to the quality inspection data.

10. A quality inspection system for a refrigerant direct cooling laser cooling system, characterized in that, It includes: A feeding mechanism that can drive the cooling system to switch between the feeding position and the quality inspection position; A fan located above the quality inspection position, which can switch between the working position 1 and the standby position 1, and is used to dissipate heat from the condenser of the cooling system at the working position 1; A heating block located on one side of the quality inspection position, which can switch between the working position 2 and the standby position 2, and is used to closely adhere to the cold plate of the cooling system at the working position 2; An ambient temperature sensor for detecting the ambient temperature; A sensor assembly for detecting the temperature data of the cooling system at the quality inspection position; A controller in which preset information is input. The controller controls the fan, the heating block, and the cooling system to work according to the ambient temperature and the preset information. The controller also determines whether the cooling system is qualified according to the temperature data fed back by the sensor assembly.

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