CN117268821A - Liquid cooling system flow redundancy and extension fault judging method - Google Patents
Liquid cooling system flow redundancy and extension fault judging method Download PDFInfo
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- 238000001816 cooling Methods 0.000 title claims abstract description 31
- 239000007788 liquid Substances 0.000 title claims abstract description 26
- 238000000034 method Methods 0.000 title claims abstract description 20
- 239000000110 cooling liquid Substances 0.000 claims description 35
- 238000012360 testing method Methods 0.000 claims description 24
- LYCAIKOWRPUZTN-UHFFFAOYSA-N Ethylene glycol Chemical compound OCCO LYCAIKOWRPUZTN-UHFFFAOYSA-N 0.000 claims description 11
- 239000002826 coolant Substances 0.000 claims description 10
- PEDCQBHIVMGVHV-UHFFFAOYSA-N Glycerine Chemical compound OCC(O)CO PEDCQBHIVMGVHV-UHFFFAOYSA-N 0.000 claims description 9
- DNIAPMSPPWPWGF-UHFFFAOYSA-N Propylene glycol Chemical compound CC(O)CO DNIAPMSPPWPWGF-UHFFFAOYSA-N 0.000 claims description 9
- 238000005259 measurement Methods 0.000 claims description 6
- 238000001514 detection method Methods 0.000 claims description 5
- 230000036541 health Effects 0.000 claims description 5
- 230000008859 change Effects 0.000 claims description 4
- 238000012966 insertion method Methods 0.000 claims description 4
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 4
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- 239000000243 solution Substances 0.000 description 5
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- 239000007864 aqueous solution Substances 0.000 description 3
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- 230000005856 abnormality Effects 0.000 description 2
- 230000002706 hydrostatic effect Effects 0.000 description 2
- 230000006872 improvement Effects 0.000 description 2
- 230000002238 attenuated effect Effects 0.000 description 1
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- 238000004140 cleaning Methods 0.000 description 1
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- WGCNASOHLSPBMP-UHFFFAOYSA-N hydroxyacetaldehyde Natural products OCC=O WGCNASOHLSPBMP-UHFFFAOYSA-N 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
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- G—PHYSICS
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- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
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Abstract
The invention discloses a liquid cooling system flow redundancy and extension fault judging method, which comprises the following steps: step 1, measuring inlet pressure and temperature, outlet pressure and temperature and first flow of a measured unit in a liquid cooling system; calculating the pressure difference between the inlet and the outlet of the unit to be tested and the actual resistance coefficient of the unit to be tested; step 2, calculating a coefficient A; step 3, establishing a relation formula between the second flow Q' and the pressure difference delta P based on the coefficient A; step 4, substituting a relation formula between the second flow Q' and the pressure difference delta P after correcting the coefficient A; and step 5, comparing the second flow Q' with the first flow Q detected by the flow sensor to obtain relevant fault judgment information. The invention can obtain more accurate fault judgment information, thereby improving the task reliability of the tested unit.
Description
Technical Field
The invention relates to the field of liquid cooling system fault judging methods, in particular to a liquid cooling system flow redundancy and extension fault judging method.
Background
The failure of the liquid cooling system is basically that some error exists, measures for eliminating the error result are needed to be taken to tolerate the error, and common means are that resources required by normal design, namely additional resources, are replaced by higher task reliability and safety so as to realize that the system meets fault tolerance criteria. The added hardware is used to improve the reliability of the system, such as redundancy design, for example, the sensor for judging the flow of the cooling liquid in the cooling liquid equipment fails, the flow is wrongly reported to be abnormal, the whole equipment stops working, if the failure cannot be toleratedThe barrier adopts a redundant design, for example, two flow sensors with the same specification are connected in parallel, when one flow sensor is abnormal, the system automatically compares with the other flow sensor and automatically switches to the backup flow sensor, so that the normal operation of the whole equipment is ensured. The failure rate lambda of the flow sensor is 0.5X10 －6 The flow sensor is in a hot standby state to meet the online switching. The basic failure rate lambda of the two flow sensors after parallel connection is 1.0 multiplied by 10 －6 The basic failure rate is doubled; the failure rate lambda of the task is (2/3) multiplied by 0.5 multiplied by 10 －6 ≈0.33×10 －6 Compared with one flow sensor, the task reliability is improved by 50%. It is known that this trades for task reliability by increasing the basic failure rate.
The existing various flow sensors are large in size, and a long enough flow is required to be reserved on the inlet pipe section and the outlet pipe section so as to meet the flow detection precision requirement. For some special cold liquid equipment or cooling units for military use or civil use, the space is often limited, the installation of two parallel flows cannot be met, whether corresponding flows can be calculated through the existing or other sensors which do not occupy space in the equipment or not can be set, and the method is used as a redundancy design method, and meanwhile, the basic failure rate of the equipment is not influenced or is very small, the design cost is reduced, and the method is worthy of trying.
In addition, when the flow abnormality occurs, whether the flow sensor is in a problem or the coolant flow is truly abnormal, and under the condition that a second flow sensor is not needed, whether the actual flow condition is verified through a second path can be increased, so that the accuracy of fault judgment is improved, and unnecessary false alarms are avoided. The task reliability and health management of the system are improved by optimizing the existing resources or adding less resources, and the improvement is worth.
Disclosure of Invention
The invention provides a liquid cooling system flow redundancy and extension fault judging method, which utilizes the measured liquid temperature, pressure, flow and the like to analyze and obtain relevant judgment so as to solve the problem of poor accuracy of the liquid cooling system fault judging method of the liquid cooling system in the prior art.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
a liquid cooling system flow redundancy and extension fault judging method comprises the following steps:
step 1, measuring the inlet pressure P of a unit to be measured in a liquid cooling system by a pressure sensor and a temperature sensor 1 Inlet temperature T 1 Outlet pressure P 2 And outlet temperature T 2 And measuring a first flow rate Q of the cooling liquid flowing out of the unit under test by a flow sensor;
calculating the pressure difference delta P=P between the inlet and outlet ends of the unit under test 1 - P 2 And uses the flow resistance formula Δp=λ Real world ·ρ·V 2 Calculating the actual resistance coefficient lambda of the measured unit Real world =2·（P 1 - P 2 ）/（ρ·V 2 ) Wherein: ρ is the average density of the coolant at the test temperature; v is the average flow velocity of the flow detection part, and is obtained by converting the first flow Q;
step 2, calculating coefficient a=3600·pi·r 2 ·（2/（λ Real world ·ρ）） 0.5 Where r is the equivalent radius at the flow sensor, and the pipe diameters of the inlet end and the outlet end of the unit to be measured are usually kept the same as the flow sensor;
step 3, establishing a relation formula between the second flow Q' and the pressure difference delta P: q' =a·Δp 0.5 ；
Step 4, dividing the cooling liquid into a plurality of groups according to the temperature control range of the cooling liquid in the tested unit, performing actual measurement tests according to the temperature range, so as to obtain a coefficient A at different cooling liquid temperatures, correcting the coefficient A through an insertion method or fitting function relation, and substituting the corrected coefficient A into a relation formula between the second flow Q' and the pressure difference delta P;
and 5, comparing the second flow Q' with the first flow Q detected by the flow sensor to obtain relevant fault judgment information, wherein the judgment is as follows:
when the first flow Q is used as a tested unit to display flow, the flow is suddenly displayed abnormally, and the second flow Q 'is normal, the tested unit is not stopped, the flow display is switched to the second flow Q', and the fault or disconnection information of the flow sensor is pushed;
when the first flow Q is close to the lower limit protection value or smaller than the normal value, and the second flow Q' is used as the reference flow and is equal to the first flow Q, the tested unit is controlled to stop, and meanwhile, the flow alarm signal is pushed.
Further, step 5 further includes: by a first flow Q and a two-terminal temperature difference Δt=t 1 - T 2 The real-time heat exchange quantity Q' of the tested unit is obtained, and the relation is established as follows:
Q”=Q·c·ρ·(T 1 - T 2 )
wherein: c is the specific heat capacity of the cooling liquid; ρ is the average density of the coolant at the test temperature;
comparing the real-time heat exchange quantity Q' with the rated heat exchange quantity of the unit to be tested, and outputting a real-time heat exchange quantity change trend as a data source for health management; when the measured unit works fully, and the real-time heat exchange quantity Q' deviates from the rated heat exchange quantity lower limit value, the capacity attenuation of the measured unit is indicated.
Further, the unit to be tested in the step 1 is a cold liquid device or a cooling unit, or a heat load; when the unit to be measured is a thermal load, the temperature difference delta T at two ends takes an absolute value; when a plurality of tested units are combined in parallel, a fault of one tested unit is obtained through the second flow Q 'and the real-time heat exchange quantity Q', and the fault is switched to the backup tested unit.
In a further step 1, the test temperature corresponding to the average density ρ of the coolant is the inlet temperature T 1 And outlet temperature T 2 And searching the data to obtain the corresponding density; or when the accuracy is not required, the inlet temperature T is adopted for the test temperature corresponding to the average density rho of the cooling liquid 1 Outlet temperature T 2 Either of the two.
In the further step 1, when a plurality of modules are used for switching in the unit to be tested, the flow resistance of each module should be ensured to be equivalent so as to avoid the influence of fluctuation of the flow during switching.
In the further step 1, the cooling liquid is water, or an ethylene glycol aqueous solution, or a propylene glycol aqueous solution, or a glycerol aqueous solution, or a No. 60 cooling liquid, or a No. 65 cooling liquid.
Compared with the prior art, the invention has the advantages that:
1. according to the invention, through physical detection of inlet and outlet pressure and temperature of the detected unit, the second flow Q' is converted and compared with the first flow Q, so that more accurate fault judgment information is obtained.
2. The second flow Q' is used as the redundant design of the flow sensor of the unit to be tested, and a set of flow sensor is not required to be additionally added as a backup, so that the task reliability of the unit to be tested is improved, and meanwhile, the basic reliability is not influenced or affected little.
3. The real-time heat exchange quantity Q 'is compared with the rated heat exchange quantity, and the real-time heat exchange quantity change trend is output, so that the real-time heat exchange quantity Q' can be used as a data source for health management.
4. The invention can perform local optimization on the existing software program to promote intelligent control of the product.
5. The invention has clear flow, simple function, easy realization and reduced hardware cost.
Drawings
Fig. 1 is a measurement schematic diagram of an embodiment of the present invention.
Detailed Description
The invention will be further described with reference to the drawings and examples.
The embodiment discloses a liquid cooling system flow redundancy and extension fault judging method, which comprises the following steps:
step 1, a measurement system is established as shown in fig. 1, an inlet pressure sensor 1 and an inlet temperature sensor 2 are installed on an inlet end pipeline of a unit to be measured 3 of the liquid cooling system, an outlet pressure sensor 5, an outlet temperature sensor 4 and a flow sensor 6 are installed on an outlet end pipeline of the unit to be measured 3, and the inlet pressure P of the unit to be measured is acquired by the inlet pressure sensor 1 and the inlet temperature sensor 2 1 Inlet temperature T 1 The outlet pressure sensor 5 and the outlet temperature sensor 4 collect the outlet pressure P of the tested unit 2 And outlet temperature T 2 And the flow sensor 6 collects the first coolant flowing out of the unit under test 3Flow Q. The inlet pressure sensor 1, the inlet temperature sensor 2, the outlet pressure sensor 5, the outlet temperature sensor 4 and the flow sensor 6 are respectively and electrically connected with the control unit 7 in a signal transmission way, and the respectively acquired data are respectively sent into the control unit 7 by the inlet pressure sensor 1, the inlet temperature sensor 2, the outlet pressure sensor 5, the outlet temperature sensor 4 and the flow sensor 6.
The control unit 7 calculates the differential pressure Δp=p across the inlet and outlet of the unit under test 3 based on the data sent from the respective sensors 1 - P 2 And uses the flow resistance formula Δp=λ Real world ·ρ·V 2 Calculating the actual resistance coefficient lambda of the measured unit 3 Real world =2·（P 1 - P 2 ）/（ρ·V 2 ) Wherein: ρ is the average density of the coolant at the test temperature, in kg/m 3 The method comprises the steps of carrying out a first treatment on the surface of the V is the average flow rate of the flow rate detection part, and is obtained by converting the first flow rate Q into the unit of m/s.
In this embodiment, the cooling liquid is water, or an aqueous ethylene glycol solution, or an aqueous propylene glycol solution, or an aqueous glycerol solution, or a cooling liquid No. 60, or a cooling liquid No. 65. The test temperature corresponding to the average density ρ of the cooling liquid is the inlet temperature T 1 And outlet temperature T 2 And searching the data to obtain the corresponding density; or when the accuracy is not required, the inlet temperature T is adopted for the test temperature corresponding to the average density rho of the cooling liquid 1 Outlet temperature T 2 Either of the two.
In this embodiment, when a plurality of modules are used for switching in the unit under test 3, the flow resistance of each module should be ensured to be equivalent, so as to avoid the influence of fluctuation of the flow during switching.
Step 2, the control unit 7 calculates a coefficient a=3600·pi·r 2 ·（2/（λ Real world ·ρ）） 0.5 Where r is the equivalent radius at the flow sensor 6, typically the inlet and outlet end pipe diameters of the unit under test 3 remain the same as the flow sensor 6 in mm.
Step 3, the control unit 7 establishes a relation formula between the second flow Q' and the differential pressure Δp: q' =a·Δp 0.5 .
And 4, when the control unit 7 needs more accurate flow requirements, such as flow accuracy + -0.5% - + -2.0%, the coefficient A needs to be properly corrected. The control unit 7 divides the cooling liquid into a plurality of groups according to the temperature control range of the cooling liquid in the measured unit 3, and performs actual measurement tests according to the temperature range, so as to obtain a coefficient A at different cooling liquid temperatures, then corrects the coefficient A through an insertion method or fitting function relation to obtain a corrected coefficient A, and substitutes the corrected coefficient A into a relation formula between the second flow Q' and the differential pressure delta P.
And 5, obtaining a second flow Q ' through a relation formula between the second flow Q ' substituted by the coefficient A after the correction in the step 4 and the pressure difference delta P, comparing the second flow Q ' with the first flow Q detected by the flow sensor 6, obtaining relevant fault judgment information, and judging as follows:
when the first flow Q is used as a tested unit to display flow and suddenly displays abnormality, such as 0 or lower than a lower limit protection value of the flow, and the second flow Q 'is normal, the tested unit 3 is not stopped, the control unit 7 switches the flow display to the second flow Q' and pushes the self fault or disconnection information of the flow sensor 6;
when the first flow Q is close to the lower limit protection value or smaller than the normal value and the second flow Q' is the reference flow which is equal to the first flow Q, the control unit 7 sends out a shut-down instruction of the tested unit to control the tested unit to shut down and push a flow alarm signal.
Therefore, the false alarm is reduced by converting the second flow Q' and comparing the second flow Q with the first flow Q to judge the fault.
Step 5 further comprises: by a first flow Q and a two-terminal temperature difference Δt=t 1 - T 2 The real-time heat exchange quantity Q' of the unit 3 to be tested is obtained, and the following relation is established:
Q”=Q·c·ρ·(T 1 - T 2 )
wherein: c is the specific heat capacity of the cooling liquid, and the unit is kj/(kg.K); ρ is the average density of the coolant at the test temperature in kg/m 3 。
Comparing the real-time heat exchange quantity Q' with the rated heat exchange quantity of the tested unit 3, and outputting a real-time heat exchange quantity change trend by the control unit 7 to serve as a data source for health management; when the measured unit 3 is fully loaded, and the real-time heat exchange quantity Q' deviates from the rated heat exchange quantity lower limit value, which indicates that the capacity of the measured unit 3 is attenuated, the control unit 7 outputs maintenance information, such as cleaning a heat exchanger and the like.
The tested unit 3 in the step 1 is a cold liquid device or a cooling unit or a heat load; when the measured unit 3 is a thermal load, the temperature difference delta T at two ends takes an absolute value; when a plurality of tested units 3 are combined in parallel, a fault of one tested unit is obtained through the second flow Q 'and the real-time heat exchange quantity Q', and the fault is switched to the backup tested unit.
This example is further illustrated as follows:
the flow sensor, or flowmeter, is a device commonly used in a cooling liquid device or a cooling unit and is used for detecting the flow of cooling liquid, and can be classified into a rotor type, a differential pressure type, a throttling type, a capacity type, an electromagnetic type, an ultrasonic type and the like according to the flow working principle. In this patent, the second flow rate Q' =a·Δp 0.5 The relationship between flow rate Q' and differential pressure Δp can be seen, similar to a differential pressure flow sensor, using flow continuity equation (law of conservation of mass) and bernoulli equation (law of conservation of energy) as a basis to obtain the differential pressure flow sensor incompressible fluid flow equation:
Q=C/(1-(d/D) 4 ) 0.5 ·A 0 ·(2ρΔP) 0.5
wherein: c refers to the outflow coefficient.
A 0 Finger plate hole open cross section area, m 2 。
D/D refers to the diameter ratio (D refers to the plate hole diameter, D refers to the sensor inlet diameter).
ρ is the density of the liquid in kg/m 3 。
It can be seen that the differential pressure flow sensor can also obtain a flow value by detecting the differential pressure across the plate orifice. The present embodiment differs from this in that: (1) the differential pressure type flow sensor detects the differential pressure at two ends of a plate hole of the differential pressure type flow sensor, and the differential pressure at two ends of an inlet and an outlet of a unit to be detected is detected in the embodiment; (2) the differential pressure flow sensor has no direct relation with the system resistance coefficient, but the present embodiment requires the actual resistance coefficient to be obtained.
The following is illustrative:
the measured unit 3 adopts 66% glycol water solution with volume ratio for a certain cooling unit, and rated flow rate Q Forehead (forehead) 20 m of 3 /h, inlet end temperature T 1 37 ℃ and outlet temperature T 2 For 30 ℃, the pipe diameter d=0.05m (radius r=0.025 m, equivalent diameter de=0.05m) was used for the inlet end, outlet end and flow sensor. Heat capacity (at 33.5 ℃ C.) C 1 =3.025 kj/(kg.k), density ρ 1 =1086.64kg/m 3 Kinematic viscosity μ 1 =3.83×10 -6 . Cooling capacity of the cooling unit:
Q”= Q forehead (forehead) ·C 1 ·ρ 1 ·(T 1 - T 2 )= 20×3.025×1086.64×7/3600≈127.831 kW
Average flow velocity V in pipe 1 =Q Forehead (forehead) /(π·r 2 )=(20/3600)/(3.14×0.025 2 )≈2.83 m/s。
Assuming a cooling unit internal tube length l=10m, a number of bends or valves n=20, a local drag coefficient ζ=1, an internal hydrostatic column Δp S =20000 Pa. Then
Reynolds number re=v 1 ·d/μ 1 =2.83×0.05/(3.83×10 -6 )=36945
Coefficient of resistance along path λ= 0.3164/Re 0.25 =0.0228
The frictional resistance Δpm=λ· (L/de) ·ρ along the course 1 ·V 1 2 /2=0.0228×(10/0.05)×1086.64×2.83 2 /2≈19842 Pa
Local resistance DeltaP e =N·ζ·ρ 1 ·V 1 2 /2=20×1×1086.64×2.83 2 /2≈87028 Pa
Total resistance Δp=Δpm+Δp e +ΔP S =19842+87028+20000=126870 Pa
This total resistance is the theoretically calculated internal flow resistance of the cooling unit.
In practice, the pressure difference between the inlet and outlet ends is used to obtain accurate internal flow resistance, e.g. the inlet pressure P is detected 1 Outlet pressure p=1000000 Pa 2 =850000 Pa，The differential pressure Δp=150000 Pa. The flow resistance is 18.23% higher than the theoretical flow resistance, so the present patent confirms the differential pressure Δp with the measured value.
Actual drag coefficient lambda Real world =2·（P 1 - P 2 ）/（ρ 1 ·V 1 2 ）=2×150000/(1086.64×2.83 2 )≈34.4717
The actual drag coefficient is an equivalent composite drag coefficient, including the effects of on-path drag coefficient, local drag coefficient, and hydrostatic column.
Calculation coefficient a=3600·pi·r 2 ·（2/（λ Real world ·ρ）） 0.5 =3600×3.14159×0.025 2 ×（2/（34.4717×1086.64）） 0.5 ≈0.05165
Obtaining a second flow rate Q' =a·Δp 0.5 =0.05165ΔP 0.5
Substituting the differential pressure Δp=150000 Pa into the calculation, Q' = 0.05165 Δp 0.5 ≈20.0040 m 3 /h, and rated flow rate 20 m 3 And/h is equivalent.
The liquid supply temperature of the cooling unit is usually in a range, such as 20-30 ℃ at the outlet end. Due to temperature influence, the density and the actual resistance coefficient lambda of the cooling liquid Real world Etc. will have some variation, resulting in a deviation of the calculated coefficient a. If the deviation value is within the allowable range, no correction is performed; if the deviation value is unacceptable, the cooling liquid is equally divided into a plurality of groups according to the temperature range to carry out actual measurement tests, so that the coefficient A under different cooling liquid temperatures is obtained, and then the coefficient A is further corrected through an insertion method or a fitting function relation, wherein the correction method is not the protection content to be expressed in the patent and is not repeated.
In the second flow Q' calculation, there may be 2 ways: (1) the calculation coefficient a is obtained by external calculation, and then the formula Q' =a·Δp 0.5 Substituting the software to output; (2) from the first step, each step has software calculations and outputs.
The preferred embodiments of the present invention have been described in detail above with reference to the accompanying drawings, and the examples described herein are merely illustrative of the preferred embodiments of the present invention and are not intended to limit the spirit and scope of the present invention. The individual technical features described in the above-described embodiments may be combined in any suitable manner without contradiction, and such combination should also be regarded as the disclosure of the present disclosure as long as it does not deviate from the idea of the present invention. The various possible combinations of the invention are not described in detail in order to avoid unnecessary repetition.
The present invention is not limited to the specific details of the above embodiments, and various modifications and improvements made by those skilled in the art to the technical solution of the present invention should fall within the protection scope of the present invention without departing from the scope of the technical concept of the present invention, and the technical content of the present invention is fully described in the claims.
Claims (6)
1. A liquid cooling system flow redundancy and extension fault judging method is characterized by comprising the following steps:
step 1, measuring the inlet pressure P of a unit to be measured in a liquid cooling system by a pressure sensor and a temperature sensor 1 Inlet temperature T 1 Outlet pressure P 2 And outlet temperature T 2 And measuring a first flow rate Q of the cooling liquid flowing out of the unit under test by a flow sensor;
calculating the pressure difference delta P=P between the inlet and outlet ends of the unit under test 1 - P 2 And uses the flow resistance formula Δp=λ Real world ·ρ·V 2 Calculating the actual resistance coefficient lambda of the measured unit Real world =2·（P 1 - P 2 ）/（ρ·V 2 ) Wherein: ρ is the average density of the coolant at the test temperature; v is the average flow velocity of the flow detection part, and is obtained by converting the first flow Q;
step 2, calculating coefficient a=3600·pi·r 2 ·（2/（λ Real world ·ρ）） 0.5 Where r is the equivalent radius at the flow sensor, and the pipe diameters of the inlet end and the outlet end of the unit to be measured are usually kept the same as the flow sensor;
step 3, establishing a relation formula between the second flow Q' and the pressure difference delta P: q' =a·Δp 0.5 ；
Step 4, dividing the cooling liquid into a plurality of groups according to the temperature control range of the cooling liquid in the tested unit, performing actual measurement tests according to the temperature range, so as to obtain a coefficient A at different cooling liquid temperatures, correcting the coefficient A through an insertion method or fitting function relation, and substituting the corrected coefficient A into a relation formula between the second flow Q' and the pressure difference delta P;
and 5, comparing the second flow Q' with the first flow Q detected by the flow sensor to obtain relevant fault judgment information, wherein the judgment is as follows:
when the first flow Q is used as a tested unit to display flow, the flow is suddenly displayed abnormally, and the second flow Q 'is normal, the tested unit is not stopped, the flow display is switched to the second flow Q', and the fault or disconnection information of the flow sensor is pushed;
when the first flow Q is close to the lower limit protection value or smaller than the normal value, and the second flow Q' is used as the reference flow and is equal to the first flow Q, the tested unit is controlled to stop, and meanwhile, the flow alarm signal is pushed.
2. The method for judging flow redundancy and extension failure of a liquid cooling system according to claim 1, wherein the step 5 further comprises: by a first flow Q and a two-terminal temperature difference Δt=t 1 - T 2 The real-time heat exchange quantity Q' of the tested unit is obtained, and the relation is established as follows:
Q”=Q·c·ρ·(T 1 - T 2 )
wherein: c is the specific heat capacity of the cooling liquid; ρ is the average density of the coolant at the test temperature;
comparing the real-time heat exchange quantity Q' with the rated heat exchange quantity of the unit to be tested, and outputting a real-time heat exchange quantity change trend as a data source for health management; when the measured unit works fully, and the real-time heat exchange quantity Q' deviates from the rated heat exchange quantity lower limit value, the capacity attenuation of the measured unit is indicated.
3. The method for judging flow redundancy and extension failure of a liquid cooling system according to claim 2, wherein the unit to be tested in step 1 is a cooling liquid device or a cooling unit, or a thermal load; when the unit to be measured is a thermal load, the temperature difference delta T at two ends takes an absolute value; when a plurality of tested units are combined in parallel, a fault of one tested unit is obtained through the second flow Q 'and the real-time heat exchange quantity Q', and the fault is switched to the backup tested unit.
4. The method as claimed in claim 1, wherein in step 1, the test temperature corresponding to the average density ρ of the coolant is the inlet temperature T 1 And outlet temperature T 2 And searching the data to obtain the corresponding density; or when the accuracy is not required, the inlet temperature T is adopted for the test temperature corresponding to the average density rho of the cooling liquid 1 Outlet temperature T 2 Either of the two.
5. The method for judging flow redundancy and extension failure of liquid cooling system according to claim 1, wherein in step 1, when a plurality of modules are used for switching in the unit to be tested, flow resistance of each module is ensured to be equivalent, so as to avoid influence of fluctuation of flow during switching.
6. The method for judging flow redundancy and extension failure of a liquid cooling system according to claim 1, wherein in the step 1, the cooling liquid is water, or an aqueous ethylene glycol solution, or an aqueous propylene glycol solution, or an aqueous glycerol solution, or a No. 60 cooling liquid, or a No. 65 cooling liquid.
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| CN202311257100.8A CN117268821A (en) | 2023-09-26 | 2023-09-26 | Liquid cooling system flow redundancy and extension fault judging method |
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