Design method and device for indoor air parameters of spent fuel pool ventilation system

Abstract

The present invention provides a design method and device for indoor air parameters of a spent fuel pool ventilation system, the method comprising: S1: obtaining an indoor air temperature input value of a spent fuel pool hall, the indoor air temperature input value being an assumed indoor air temperature initial value or an indoor air temperature correction value obtained in step S3; S2: calculating an air supply volume calculated value according to the indoor air temperature input value, then calculating the absolute value of the difference between the air supply volume calculated value and the air supply volume design value, and judging whether the absolute value is greater than a first set threshold value, if so, correcting the indoor air temperature input value, obtaining an indoor air temperature correction value, and returning to step S1, if not, outputting the indoor air temperature input value as the indoor air temperature design value. The design method of the present invention can accurately obtain key indoor air parameters of a spent fuel pool ventilation system, and provide a reference for engineering design.

Description

Technical Field

[0001] The invention specifically relates to a design method and device for indoor air parameters of a spent fuel pool ventilation system. Background Art

[0002] After the spent fuel assemblies of a nuclear power plant are unloaded from the reactor, they still have a certain amount of residual reaction and need to be stored in the spent fuel pool in the nuclear island plant for a short period of time (generally 5 to 20 years). After their decay heat and radioactivity are reduced to an appropriate level, they can be transported out and transferred to the reprocessing plant for final treatment. Due to the existence of the spent fuel pool, the hall of the spent fuel pool presents a special thermal environment of high temperature and high humidity, and the surface condensation problem of its enclosure structure (including the roof and walls) will be more prominent. The surface condensation of the enclosure structure of the spent fuel pool hall will not only affect the appearance of the building and reduce the service life of the building, but also have an adverse effect on the normal use of related equipment in the spent pool. At the same time, it will generate cold radiation to the staff in the hall. Wet materials are prone to breeding mold and other microorganisms, which are harmful to human health.

[0003] In order to prevent the condensation on the surface of the enclosure structure of the spent fuel plant hall from having an adverse effect on the equipment and personnel working environment in the spent fuel pool, it is necessary to analyze the condensation characteristics of the enclosure structure of the spent fuel pool hall under different design conditions based on heat transfer theory and condensation principles, and to provide corresponding preventive measures for the condensation problem of the enclosure structure of the spent fuel pool hall.

[0004] One measure to prevent condensation is to lower the air dew point temperature, which requires the installation of a spent fuel pool ventilation system. In order to ensure that there is no condensation, researchers need to design the spent fuel pool ventilation system and understand the state of the indoor environment under ventilation. The most critical design parameters include the indoor temperature design value and the indoor air relative humidity design value. At present, the calculation of the fuel pool ventilation system for anti-condensation generally adopts the estimation method, which has the problem of single calculation method and inaccurate calculation results. Summary of the invention

[0005] The technical problem to be solved by the present invention is to provide a simple and accurate design method for indoor air parameters of a spent fuel pool ventilation system in view of the above-mentioned deficiencies in the prior art.

[0006] The technical solution adopted to solve the technical problem of the present invention is:

[0007] The present invention provides a method for designing indoor air parameters of a spent fuel pool ventilation system, comprising:

[0008] S1: Obtaining an input value of the indoor air temperature of the spent fuel pool hall, wherein the input value of the indoor air temperature is an assumed initial value of the indoor air temperature or a corrected value of the indoor air temperature obtained in step S3;

[0009] S2: Calculate the air supply volume calculated value according to the indoor air temperature input value, then calculate the absolute value of the difference between the air supply volume calculated value and the air supply volume design value, and determine whether the absolute value is greater than a first set threshold value. If so, correct the indoor air temperature input value to obtain the indoor air temperature correction value, and return to step S1. If not, output the indoor air temperature input value as the indoor air temperature design value.

[0010] Optionally, the air supply volume is calculated using formula (1):

[0011]

[0012] Where:

[0013] Q s ——air supply volume, m 3 / s;

[0014] W——heat load in the spent fuel pool hall, W;

[0015] θ i ——Indoor air temperature input value, °C;

[0016] θ s ——Supply air dry bulb temperature, °C;

[0017] ρ s ——Density of supply air, kg / m 3 ;

[0018] c p ——Specific heat of supply air, J / (kg·℃).

[0019] Optionally, the heat load W in the spent fuel pool hall is calculated using formula (2):

[0020] W=W1+W2+W3 (2)

[0021] Where:

[0022] W1——Convection evaporation heat transfer of the water surface of the spent fuel pool, W;

[0023] W2——radiation heat transfer of the water surface of the spent fuel pool, W;

[0024] W3——Wall heat exchange, W.

[0025] Optionally, the convective evaporation heat transfer W1 of the water surface of the spent fuel pool in formula (2) is calculated according to formula (3):

[0026] W1=α1A w (t w -θi ) (3)

[0027] Where:

[0028] α1——Convection heat transfer coefficient of the spent fuel pool water surface, W / (m 2 ℃), the value is 6.5;

[0029] A w ——Heat dissipation area of ​​the spent fuel pool water surface, m 2 ;

[0030] t w ——Water temperature of the spent fuel pool surface, °C, 45~55°C;

[0031] The radiation heat transfer W2 of the water surface of the spent fuel pool in formula (2) is calculated according to formula (4):

[0032] W2=σEA w [(t w +273.15) 4 -(θ i +273.15) 4 ] (4)

[0033] Where:

[0034] σ——blackbody radiation constant, taken as 5.67×10 -8 W / (m 2 ·K 4 );

[0035] E——comprehensive emissivity of radiation heat transfer;

[0036] The comprehensive emissivity E of radiation heat transfer in formula (4) is calculated according to formula (5):

[0037]

[0038] Where:

[0039] ε w ——The radiation emissivity of the spent fuel pool surface is 0.96;

[0040] ε wall ——The radiation emissivity of the concrete wall is 0.94;

[0041] The wall heat transfer W3 in formula (2) is calculated according to formula (6):

[0042]

[0043] A wall ——Wall heat dissipation area, m 2 ;

[0044] α i ——Convection heat transfer coefficient in the spent fuel pool hall, W / (m 2 ℃), the value is 5.0;

[0045] α e ——Convection heat transfer coefficient outside the spent fuel pool hall, W / (m 2 ℃), the value is 15~25.0;

[0046] δ wall ——wall thickness, m;

[0047] λ wall ——Thermal conductivity of the wall, W / (m·℃);

[0048] θ e ——Outdoor ambient air temperature, ℃.

[0049] Optionally, the specific heat of the supply air c p Calculated using formula (7):

[0050] c p =1006.4+2014x (7)

[0051] Where:

[0052] x——humidity content of supply air, kg;

[0053] In formula (7), when the air dry bulb temperature is θ, the air relative humidity is Atmospheric pressure is P ai When , the humidity content of the supply air is calculated using formula (8):

[0054]

[0055] Where:

[0056] ——Relative humidity of supply air, %;

[0057] p″ θ ——The saturated water vapor pressure corresponding to the dry bulb temperature of the supply air is θ, 9.8×10 4 Pa;

[0058] p ai ——Indoor atmospheric pressure, Pa. The summer environmental conditions are 100430Pa~100480Pa; the winter environmental conditions are 102130Pa~102180Pa.

[0059] Optionally, in formula (8), when the air dry bulb temperature is θ, the wet bulb temperature is τ, and the atmospheric pressure is P aiThe relative humidity of the supply air is Calculated using formula (9):

[0060] Where:

[0061] ——Relative humidity of supply air, %;

[0062] p″ τ ——The saturated water vapor pressure corresponding to the air wet bulb temperature is τ, 9.8×10 4 Pa;

[0063] p″ θ ——The saturated water vapor pressure corresponding to the dry bulb temperature of the supply air is θ, 9.8×10 4 Pa;

[0064] p ai ——Indoor atmospheric pressure, Pa. The summer environmental conditions are 100430Pa~100480Pa; the winter environmental conditions are 102130Pa~102180Pa.

[0065] Optionally, in formula (1), the density of the supply air ρ s Calculated by formula (10):

[0066]

[0067] Where:

[0068] ρ s ——Density of supply air, kg / m 3 ;

[0069] p sv ——Supply air water vapor pressure,

[0070] ——Relative humidity of supply air, %;

[0071] ——Supply air (dry bulb) temperature is θ s Saturated water vapor pressure at ℃,

[0072] p sd ——Dry air pressure of supply air, p sd =P ai -p sv

[0073] R d ——Gas constant of dry air, value is 287.14, J / (kg·K);

[0074] R v ——The gas constant of water vapor is 461.53, J / (kg·K);

[0075] T s ——The dry bulb temperature of the supply air is θ s Thermodynamic temperature value corresponding to ℃, K, T s =θ s +273.15.

[0076] Optionally, it also includes:

[0077] S3: Obtaining an input value of indoor air relative humidity of the spent fuel pool, wherein the input value of indoor air relative humidity is an assumed initial value of indoor air relative humidity or a corrected value of indoor air relative humidity obtained in step S4;

[0078] S4: Calculate the calculated value of the indoor air relative humidity after the water surface of the spent fuel pool evaporates according to the indoor air relative humidity input value and the indoor air temperature design value output in step S2, then calculate the absolute value of the difference between the calculated value of the indoor air relative humidity and the input value of the indoor air relative humidity, and determine whether the absolute value is greater than a second set threshold value. If so, correct the input value of the indoor air relative humidity to obtain a corrected value of the indoor air relative humidity, and return to step S3. If not, output the calculated value of the indoor air relative humidity as the design value of the indoor air relative humidity.

[0079] Optionally, in step S4, the specific process of calculating the calculated value of the indoor air relative humidity according to the indoor air relative humidity input value and the indoor air temperature design value obtained in step S2 is as follows:

[0080] S4.1: Calculate the evaporation coefficient E of the pool surface using formula (11) w :

[0081]

[0082] Where:

[0083] E w —Evaporation coefficient of the pool surface, kg / (m 2 s);

[0084] v—air velocity at a height of 0.5m to 1.0m above the pool surface, m / s;

[0085] p″ w —air saturated water vapor pressure corresponding to water temperature, Pa;

[0086] —Water vapor pressure of indoor air near the water surface, Pa,

[0087] ——Input value of indoor air relative humidity;

[0088] ——The design value of indoor air temperature (dry bulb temperature) is θ i Saturated water vapor pressure at ℃;

[0089] S4.2: Evaporation coefficient E of the pool surface calculated according to formula (11) w , use formula (12) to calculate the water surface evaporation Q w :

[0090] Q w =E w A w (12)

[0091] Where:

[0092] Q w ——water surface evaporation, kg / s;

[0093] E w ——Evaporation coefficient of the pool surface, kg / (m 2 s);

[0094] A w ——Water surface heat dissipation area, m 2 ;

[0095] S4.3: Calculated water surface evaporation Q according to formula (12) w , use formula (13) to calculate the indoor air humidity x after water surface evaporation i :

[0096]

[0097] Where:

[0098] x i ——The humidity content of indoor air after evaporation from water surface, kg;

[0099] Q w ——water surface evaporation, kg / s;

[0100] Q s ——Design value of air supply volume, m 3 / s;

[0101] ρ s ——Density of supply air, kg / m 3 ;

[0102] x s ——humidity content of supply air, kg;

[0103] S4.4: The humidity x of the indoor air after the water evaporates, calculated according to formula (13) i , use formula (14) to calculate the relative humidity of indoor air after water surface evaporation

[0104] ——Relative humidity of indoor air after evaporation of water surface;

[0105] x i ——The humidity content of indoor air after evaporation from water surface, kg;

[0106] p ai ——Indoor atmospheric pressure, Pa, summer environmental conditions are 100430Pa~100480Pa; winter environmental conditions are 102130Pa~102180Pa;

[0107] ——The design value of indoor air temperature (dry bulb temperature) is θ i Saturated water vapor pressure at ℃.

[0108] The present invention also provides a device for designing indoor air parameters of a spent fuel pool ventilation system, comprising: a first acquisition module and a first processing module.

[0109] The first acquisition module is used to obtain an input value of the indoor air temperature of the spent fuel pool hall, wherein the input value of the indoor air temperature is an assumed initial value of the indoor air temperature or a corrected value of the indoor air temperature input by the first processing module;

[0110] The first processing module is connected to the first acquisition module, and is used to calculate the supply air volume calculated value based on the indoor air temperature input value, then calculate the absolute value of the difference between the supply air volume calculated value and the supply air volume design value, and determine whether the absolute value is greater than a first set threshold value. If so, the indoor air temperature input value is corrected and input into the first acquisition module as the indoor air temperature correction value. If not, the indoor air temperature input value is output as the indoor air temperature design value.

[0111] Optionally, it further includes: a second acquisition module and a second processing module,

[0112] The second acquisition module is used to obtain an input value of indoor air relative humidity of the spent fuel pool, wherein the input value of indoor air relative humidity is an assumed initial value of indoor air relative humidity or a corrected value of indoor air relative humidity input by the second processing module;

[0113] The first processing module is connected to the first processing module and the second acquisition module respectively, and is used to calculate the calculated value of the indoor air relative humidity after the water surface of the spent fuel pool evaporates according to the indoor air relative humidity input value and the indoor air temperature design value, and then calculate the absolute value of the difference between the calculated value of the indoor air relative humidity and the indoor air relative humidity input value, and judge whether the absolute value is greater than a second set threshold value. If so, the indoor air relative humidity input value is corrected and input into the second acquisition module as the indoor air relative humidity correction value. If not, the indoor air relative humidity calculated value is output as the indoor air relative humidity design value.

[0114] In the present invention, the initial conditions are first set, and then through iterative calculation, the indoor air design parameters of the spent fuel pool ventilation system can be simply and accurately obtained. The calculation input and calculation output can also be exchanged to obtain other desired results, providing a reference for engineering design. BRIEF DESCRIPTION OF THE DRAWINGS

[0115] Figure 1 A flow chart for designing the indoor air temperature of the spent fuel pool ventilation system according to the present invention;

[0116] Figure 2 A flow chart for designing the relative humidity of indoor air in the spent fuel pool ventilation system according to the present invention.

[0117] Figure 3 This is a block diagram of a device for designing indoor air parameters of a spent fuel pool ventilation system provided in Example 3 of the present invention. DETAILED DESCRIPTION

[0118] The following will be combined with the accompanying drawings in the present invention to clearly and completely describe the technical solutions in the invention. Obviously, the described embodiments are part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments in the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of the present invention.

[0119] In the description of the present invention, it should be noted that the directions or positional relationships indicated by “upper” and the like are based on the directions or positional relationships shown in the accompanying drawings and are only for the convenience and simplification of the description. They do not indicate or imply that the device or element referred to must have a specific direction, be constructed and operated in a specific direction. Therefore, they cannot be understood as limitations on the present invention.

[0120] In the description of the present invention, the terms “first” and “second” are used for descriptive purposes only and should not be understood as indicating or implying relative importance.

[0121] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "connect", "set", "install", "fix" and the like should be understood in a broad sense, for example, it can be a fixed connection or a detachable connection, or an integral connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be the internal communication of two components. For those skilled in the art, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0122] The present invention provides a method for designing indoor air parameters of a spent fuel pool ventilation system, comprising:

[0123] S1: Obtaining an input value of the indoor air temperature of the spent fuel pool hall, wherein the input value of the indoor air temperature is an assumed initial value of the indoor air temperature or a corrected value of the indoor air temperature obtained in step S3;

[0124] S2: Calculate the air supply volume calculated value according to the indoor air temperature input value, then calculate the absolute value of the difference between the air supply volume calculated value and the air supply volume design value, and determine whether the absolute value is greater than a first set threshold value. If so, correct the indoor air temperature input value to obtain the indoor air temperature correction value, and return to step S1. If not, output the indoor air temperature input value as the indoor air temperature design value.

[0125] The present invention also provides a device for designing indoor air parameters of a spent fuel pool ventilation system, comprising: a first acquisition module and a first processing module.

[0126] The first acquisition module is used to obtain an input value of the indoor air temperature of the spent fuel pool hall, wherein the input value of the indoor air temperature is an assumed initial value of the indoor air temperature or a corrected value of the indoor air temperature input by the first processing module;

[0127] The first processing module is connected to the first acquisition module, and is used to calculate the supply air volume calculated value based on the indoor air temperature input value, then calculate the absolute value of the difference between the supply air volume calculated value and the supply air volume design value, and determine whether the absolute value is greater than a first set threshold value. If so, the indoor air temperature input value is corrected and input into the first acquisition module as the indoor air temperature correction value. If not, the indoor air temperature input value is output as the indoor air temperature design value.

[0128] Embodiment 1:

[0129] like Figure 1 and Figure 2 As shown, this embodiment provides a method for designing indoor air parameters of a spent fuel pool ventilation system, comprising the following steps:

[0130] (S1): obtaining initial conditions, including: atmospheric pressure, supply air dry bulb temperature, supply air wet bulb temperature or supply air relative humidity;

[0131] (S2): Calculating the density of the supply air, the moisture content of the supply air, and the specific heat of the supply air;

[0132] (S3): obtaining an indoor air temperature input value, wherein the indoor air temperature input value is an assumed indoor air temperature initial value or an indoor air temperature correction value obtained in step (S6);

[0133] (S4): Calculate the heat load of the spent fuel pool hall according to the indoor air temperature input value of step (S3), including: water surface convection evaporation heat transfer, water surface radiation heat transfer and wall radiation heat transfer;

[0134] (S5): Calculating the air supply volume corresponding to the indoor air temperature input value in step (S3);

[0135] (S6): Compare the above-mentioned calculated air supply volume value with the designed air supply volume value. If the absolute value of the difference between the two is greater than the first set threshold, correct the indoor air temperature input value and return to step (S3). Otherwise, output the indoor air temperature input value as the designed indoor air temperature value.

[0136] In this embodiment, the first set threshold is 10% of the air supply volume design value. The indoor air temperature correction has a certain empirical component. Generally speaking, if the "air supply volume design value" is greater than the "air supply volume calculation value", the "indoor air temperature input value" is reduced; if the "air supply volume design value" is less than the "air supply volume calculation value", the "indoor air temperature input value" is increased.

[0137] (S7): Calculate the saturated water vapor pressure corresponding to the water temperature of the spent fuel pool;

[0138] (S8): Calculating the saturated water vapor pressure corresponding to the indoor air temperature design value outputted from step (S6);

[0139] (S9): obtaining an input value of indoor air relative humidity, where the input value of indoor air relative humidity is an assumed initial value of indoor air relative humidity or a corrected value of indoor air relative humidity obtained in step (S12);

[0140] (S10): Calculate the evaporation coefficient of the pool surface according to the saturated water vapor pressure obtained in step (S8) and the indoor air relative humidity input value in step (S9), and then obtain the water surface evaporation amount;

[0141] (S11): Calculating the indoor air humidity after water surface evaporation based on the water surface evaporation obtained in step (S10);

[0142] (S12): Calculate the indoor air relative humidity based on the indoor air moisture content after water surface evaporation obtained in step (S11), and compare it with the indoor air relative humidity input value in step (S9). If the difference between the two is greater than a second set threshold, correct the indoor air relative humidity input value and return to step (S9). Otherwise, the indoor air relative humidity input value is output as the indoor air relative humidity design value.

[0143] In this embodiment, the second set threshold is 5% of the indoor air relative humidity input value. Correcting the indoor air relative humidity input value has a certain empirical component. Generally speaking, if the "indoor air relative humidity calculation value" is greater than the "indoor air relative humidity input value", the "indoor air relative humidity input value" is increased; if the "indoor air relative humidity calculation value" is less than the "indoor air relative humidity input value", the "indoor air relative humidity input value" is reduced.

[0144] in:

[0145] (1): Use formula (1) to calculate the air supply volume in (S5):

[0146]

[0147] Where:

[0148] Q s ——air supply volume, m 3 / s;

[0149] W——heat load in the spent fuel pool hall, W;

[0150] θ i ——Indoor air temperature input value, °C;

[0151] θ s ——Supply air dry bulb temperature, °C;

[0152] ρ s ——Density of supply air, kg / m 3 ;

[0153] c p ——Specific heat of supply air, J / (kg·℃).

[0154] (1.2): In formula (1) (i.e., in step (S4)), the heat load W in the spent fuel pool hall is calculated using formula (2):

[0155] W=W1+W2+W3 (2)

[0156] Where:

[0157] W1——Convection evaporation heat transfer of the water surface of the spent fuel pool, W;

[0158] W2——radiation heat transfer of the water surface of the spent fuel pool, W;

[0159] W3——Wall heat exchange, W.

[0160] (1.2.1): The convective evaporation heat transfer W1 of the water surface of the spent fuel pool in formula (2) is calculated according to formula (3):

[0161] W1=α1A w (t w -θ i ) (3)

[0162] Where:

[0163] α1——Convection heat transfer coefficient of the spent fuel pool water surface, W / (m 2 ℃), the value is 6.5;

[0164] A w ——heat dissipation area of ​​the spent fuel pool water surface, m 2 ;

[0165] t w ——Water temperature of the spent fuel pool surface, °C, 45~55°C;

[0166] (1.2.2): The radiation heat transfer W2 of the water surface of the spent fuel pool in formula (2) is calculated according to formula (4):

[0167] W2=σEA w [(t w +273.15) 4 -(θ i +273.15) 4 ] (4)

[0168] Where:

[0169] σ——blackbody radiation constant, taken as 5.67×10 -8 W / (m 2 ·K 4 );

[0170] E——comprehensive emissivity of radiation heat transfer;

[0171] The comprehensive emissivity E of radiation heat transfer in formula (4) is calculated according to formula (5):

[0172]

[0173] Where:

[0174] ε w——The radiation emissivity of the spent fuel pool surface is 0.96;

[0175] ε wall ——The radiation emissivity of the concrete wall is 0.94;

[0176] (1.2.3): The wall heat transfer W3 in formula (2) is calculated according to formula (6):

[0177]

[0178] A wall ——Wall heat dissipation area, m 2 ;

[0179] α i ——Convection heat transfer coefficient in the spent fuel pool hall, W / (m 2 ℃), the value is 5.0;

[0180] α e ——Convection heat transfer coefficient outside the spent fuel pool hall, W / (m 2 ℃), the value is 15~25.0;

[0181] δ wall ——wall thickness, m;

[0182] λ wall ——Thermal conductivity of the wall, W / (m·℃);

[0183] θ e ——Outdoor ambient air temperature, ℃.

[0184] (1.3): In formula (1) (i.e., in (S2)), the specific heat of the supply air c p Calculated using formula (7):

[0185] c p =1006.4+2014x (7)

[0186] Where:

[0187] x – humidity content of supply air, kg; the mass of water vapor contained in 1 kg of dry air is called the humidity content x of moist air (also called specific humidity).

[0188] (1.3.1): When the air dry bulb temperature is θ, the relative humidity is Atmospheric pressure is P ai When , the humidity x of the supply air in formula (7) (that is, in (S2)) is calculated using formula (8):

[0189]

[0190] Where:

[0191] ——Relative humidity of supply air, %;

[0192] p″ θ ——The saturated water vapor pressure corresponding to the dry bulb temperature of the supply air is θ, 9.8×10 4 Pa;

[0193] p ai ——Indoor atmospheric pressure, Pa. The summer environmental conditions are 100430Pa~100480Pa; the winter environmental conditions are 102130Pa~102180Pa.

[0194] (1.3.2): In formula (8), when the air dry bulb temperature is θ, the air relative humidity is Atmospheric pressure is P ai When the relative humidity of the supply air is Calculated using formula (9):

[0195]

[0196] Where:

[0197] ——Relative humidity of supply air, %;

[0198] p″ τ ——The saturated water vapor pressure corresponding to the air wet bulb temperature is τ, 9.8×10 4 Pa;

[0199] p″ θ ——The saturated water vapor pressure corresponding to the dry bulb temperature of the supply air is θ, 9.8×10 4 Pa;

[0200] p ai ——Indoor atmospheric pressure, Pa. The summer environmental conditions are 100430Pa~100480Pa; the winter environmental conditions are 102130Pa~102180Pa.

[0201] (1.4): In formula (1) (also in (S2)), the density of the supply air ρ s Calculated by formula (10):

[0202]

[0203] Where:

[0204] ρ s ——Density of supply air, kg / m 3 ;

[0205] p sv ——Supply air water vapor pressure,

[0206] ——Relative humidity of supply air, %;

[0207] ——Supply air (dry bulb) temperature is θ s Saturated water vapor pressure at ℃,

[0208] p sd ——Dry air pressure of supply air, p sd =P ai -p sv

[0209] R d ——Gas constant of dry air, value is 287.14, J / (kg·K);

[0210] R v ——The gas constant of water vapor is 461.53, J / (kg·K);

[0211] T s ——The dry bulb temperature of the supply air is θ s Thermodynamic temperature value corresponding to ℃, K, T s =θ s +273.15.

[0212] (2): The calculation process of the relative humidity of indoor air is as follows:

[0213] (2.1): Use formula (11) to calculate the evaporation coefficient E of the pool surface w :

[0214]

[0215] Where:

[0216] E w —Evaporation coefficient of the pool surface, kg / (m 2 s);

[0217] v—air velocity at a height of 0.5m to 1.0m above the pool surface, m / s;

[0218] p″ w —air saturated water vapor pressure corresponding to water temperature, Pa;

[0219] —Water vapor pressure of indoor air near the water surface, Pa,

[0220] ——Input value of indoor air relative humidity;

[0221] ——The design value of indoor air temperature (dry bulb temperature) is θ i Saturated water vapor pressure at ℃;

[0222] (2.2): The evaporation coefficient E of the pool surface calculated according to formula (11) w , use formula (12) to calculate the water surface evaporation Q w :

[0223] Q w =E w A w (12)

[0224] Where:

[0225] Q w ——water surface evaporation, kg / s;

[0226] E w ——Evaporation coefficient of the pool surface, kg / (m 2 s);

[0227] A w ——Water surface heat dissipation area, m 2 ;

[0228] (2.3): The water surface evaporation Q calculated according to formula (12) w , use formula (13) to calculate the indoor air humidity x after water surface evaporation i :

[0229]

[0230] Where:

[0231] x i ——The humidity content of indoor air after evaporation from water surface, kg;

[0232] Q w ——water surface evaporation, kg / s;

[0233] Q s ——Design value of air supply volume, m 3 / s;

[0234] ρ s ——Density of supply air, kg / m 3 ;

[0235] x s ——humidity content of supply air, kg;

[0236] (2.4): The humidity x of the indoor air after the water evaporates according to formula (13) i , use formula (14) to calculate the relative humidity of indoor air after water surface evaporation

[0237] ——Relative humidity of indoor air after evaporation of water surface;

[0238] x i ——The humidity content of indoor air after evaporation from water surface, kg;

[0239] p ai ——Indoor atmospheric pressure, Pa, summer environmental conditions are 100430Pa~100480Pa; winter environmental conditions are 102130Pa~102180Pa;

[0240] ——The design value of indoor air temperature (dry bulb temperature) is θ i Saturated water vapor pressure at ℃.

[0241] In the above formulas, the subscript i represents indoor air and the subscript s represents supply air. For example, the air dry bulb temperature θ and the supply air dry bulb temperature θ s , indoor air dry bulb temperature θ i .

[0242] In addition, the maximum content of water vapor in humid air is the saturated content, and the corresponding water vapor partial pressure is the saturated water vapor pressure. In the range of 0℃~100℃ and normal pressure, the saturated water vapor pressure p″ of each air in equations (8), (9), (10), (11) and (14) can be calculated according to the Gilles formula (equation (15)):

[0243]

[0244] Where:

[0245] p″ t ——The saturated water vapor pressure at air temperature t℃, 9.8×10 4 Pa;

[0246] t′——Thermodynamic temperature value corresponding to air temperature t℃, K, t′=t+273.15.

[0247] Embodiment 2:

[0248] In a power plant, the design value of ventilation volume in the spent fuel pool area is 14500m 3 / h, the final temperature design value of the pool hall and the indoor air relative humidity design value are calculated according to steps S1-S12 of Example 1 as follows:

[0249] S1: Input initial conditions: atmospheric pressure is 1.013×10 5 Pa, supply air dry bulb temperature is 20℃, supply air relative humidity is 90%;

[0250] S2: Calculate the air density of the supply air to be 1.2kg / m 3 , calculated according to formula (8) and (7) respectively: the humidity content of the supply air is 13.2 g / kg, and the specific heat of the supply air is 1.01 kJ / (kg·℃);

[0251] S3: Assume that the initial value of indoor air temperature is 30℃;

[0252] S4: According to formula (2), the heat load in the spent fuel pool hall is 45.5kW;

[0253] S5: According to formula (1), the air supply volume is calculated to be 13500m 3 / h;

[0254] S6: The difference between the calculated air volume and the designed air volume is within 10%, and the indoor air temperature output value is determined to be 30°C;

[0255] S7: According to formula (15), the saturated water vapor pressure corresponding to the water temperature of the spent fuel pool is 1.2×10 4 Pa;

[0256] S8: According to formula (15), the indoor air temperature is calculated to be 0.4×10 4 Pa;

[0257] S9: Assume that the initial value of indoor air relative humidity is 90%;

[0258] S10: According to formula (12), the evaporation rate of the water surface in the spent fuel pool is 397 kg / h;

[0259] S11: According to formula (14), the relative humidity of indoor air is 94%;

[0260] S12: The calculated value of the indoor air relative humidity is within 5% of the initial design value, and the output value of the indoor air relative humidity is determined to be 90%.

[0261] After the indoor air parameters are calculated using the above method, they can be used to assess the condensation risk in the pool hall, and to avoid possible condensation by adjusting parameters such as the air volume, temperature, and relative humidity of the supply air.

[0262] Embodiment 3:

[0263] like Figure 3 As shown, this embodiment provides a design device for indoor air parameters of a spent fuel pool ventilation system that implements the design method of embodiment 1, comprising: a first acquisition module 1 and a first processing module 2,

[0264] The first acquisition module 1 is used to obtain an input value of the indoor air temperature of the spent fuel pool hall, where the input value of the indoor air temperature is an assumed initial value of the indoor air temperature or a corrected value of the indoor air temperature input by the first processing module 2;

[0265] The first processing module 2 is connected to the first acquisition module 1, and is used to calculate the calculated value of the supply air volume according to the indoor air temperature input value, and then calculate the absolute value of the difference between the calculated value of the supply air volume and the design value of the supply air volume, and determine whether the absolute value is greater than the first set threshold value. If so, the indoor air temperature input value is corrected and input into the first acquisition module as the indoor air temperature correction value. If not, the indoor air temperature input value is output as the indoor air temperature design value.

[0266] In this embodiment, it also includes: a second acquisition module 3 and a second processing module 4,

[0267] The second acquisition module 3 is used to obtain an input value of the indoor air relative humidity of the spent fuel pool, where the input value of the indoor air relative humidity is an assumed initial value of the indoor air relative humidity or a corrected value of the indoor air relative humidity input by the second processing module 4;

[0268] The second processing module 4 is connected to the first processing module 2 and the second acquisition module 3 respectively, and is used to calculate the calculated value of the indoor air relative humidity after the water surface of the spent fuel pool evaporates according to the indoor air relative humidity input value and the indoor air temperature design value, and then calculate the absolute value of the difference between the calculated value of the indoor air relative humidity and the indoor air relative humidity input value, and determine whether the absolute value is greater than a second set threshold value. If so, the indoor air relative humidity input value is corrected and input into the second acquisition module 3 as the indoor air relative humidity correction value. If not, the calculated value of the indoor air relative humidity is output as the indoor air relative humidity design value.

[0269] It is to be understood that the above embodiments are merely exemplary embodiments used to illustrate the principles of the present invention, but the present invention is not limited thereto. For those of ordinary skill in the art, various modifications and improvements can be made without departing from the spirit and essence of the present invention, and these modifications and improvements are also considered to be within the scope of protection of the present invention.

Claims

1. A method for designing indoor air parameters of a spent fuel pool ventilation system, characterized in that: include: S1: Obtaining an input value of the indoor air temperature of the spent fuel pool hall, wherein the input value of the indoor air temperature is an assumed initial value of the indoor air temperature or a corrected value of the indoor air temperature obtained in step S3; S2: Calculate the air supply volume calculated value according to the indoor air temperature input value, then calculate the absolute value of the difference between the air supply volume calculated value and the air supply volume design value, and determine whether the absolute value is greater than a first set threshold value. If so, correct the indoor air temperature input value to obtain the indoor air temperature correction value, and return to step S1. If not, output the indoor air temperature input value as the indoor air temperature design value. The air supply volume is calculated using formula (1): Where: Q s ——air supply volume, m 3 / s; W——heat load in the spent fuel pool hall, W; θ i ——Indoor air temperature input value, °C; θ s ——Supply air dry bulb temperature, °C; ρ s ——Density of supply air, kg / m 3 ; c p ——Specific heat of supply air, J / (kg·℃); The heat load W in the spent fuel pool hall in formula (1) is calculated using formula (2): W=W1+W2+W3 (2) Where: W1——Convection evaporation heat transfer of the water surface of the spent fuel pool, W; W2——radiation heat transfer of the water surface of the spent fuel pool, W; W3——wall heat exchange, W; The convective evaporation heat transfer W1 of the water surface of the spent fuel pool in formula (2) is calculated according to formula (3): W1=α1A w (t w -θ i ) (3) Where: α1——Convection heat transfer coefficient of the spent fuel pool water surface, W / (m 2 ℃), the value is 6.5; A w ——heat dissipation area of ​​the spent fuel pool water surface, m 2 ; t w ——Water temperature of the spent fuel pool surface, °C, 45~55°C; The radiation heat transfer W2 of the water surface of the spent fuel pool in formula (2) is calculated according to formula (4): W2=σEA w [(t w +273.15) 4 -(θ i +273.15) 4 ] (4) Where: σ——blackbody radiation constant, taken as 5.67×10 -8 W / (m 2 ·K 4 ); E——comprehensive emissivity of radiation heat transfer; The comprehensive emissivity E of radiation heat transfer in formula (4) is calculated according to formula (5): Where: ε w ——The radiation emissivity of the spent fuel pool surface is 0.96; ε wall ——The radiation emissivity of the concrete wall is 0.94; The wall heat transfer W3 in formula (2) is calculated according to formula (6): A wall ——Wall heat dissipation area, m 2 ; α i ——Convection heat transfer coefficient in the spent fuel pool hall, W / (m 2 ℃), the value is 5.0; α e ——Convection heat transfer coefficient outside the spent fuel pool hall, W / (m 2 ℃), the value is 15~25.0; δ wall ——wall thickness, m; λ wall ——Thermal conductivity of the wall, W / (m·℃); θ e ——Outdoor ambient air temperature, ℃.

2. The method for designing indoor air parameters of the spent fuel pool ventilation system according to claim 1, characterized in that: The specific heat of the supply air in formula (1) is c p Calculated using formula (7): c p =1006.4+2014x (7) Where: x——humidity content of supply air, kg; In formula (7), when the air dry bulb temperature is θ, the air relative humidity is Atmospheric pressure is P ai When , the humidity content of the supply air is calculated using formula (8): Where: ——Relative humidity of supply air, %; p′ θ ′——the saturated water vapor pressure corresponding to the dry bulb temperature of the supply air is θ, 9.8×10 4 Pa; p ai ——Indoor atmospheric pressure, Pa. The summer environmental conditions are 100430Pa~100480Pa; the winter environmental conditions are 102130Pa~102180Pa.

3. The method for designing indoor air parameters of the spent fuel pool ventilation system according to claim 2, characterized in that: In formula (8), when the air dry bulb temperature is θ, the wet bulb temperature is τ, and the atmospheric pressure is P ai The relative humidity of the supply air is Calculated using formula (9): Where: ——Relative humidity of supply air, %; p τ ″——The saturated water vapor pressure corresponding to the air wet bulb temperature of τ, 9.8×10 4 Pa; p′ θ ′——the saturated water vapor pressure corresponding to the dry bulb temperature of the supply air is θ, 9.8×10 4 Pa; p ai ——Indoor atmospheric pressure, Pa. The summer environmental conditions are 100430Pa~100480Pa; the winter environmental conditions are 102130Pa~102180Pa.

4. The method for designing indoor air parameters of the spent fuel pool ventilation system according to claim 3, characterized in that: In formula (1), the density of the supply air ρ s Calculated by formula (10): Where: ρ s ——Density of supply air, kg / m 3 ; p sv ——Supply air water vapor pressure, ——Relative humidity of supply air, %; ——Supply air (dry bulb) temperature is θ s Saturated water vapor pressure at ℃, p sd ——Dry air pressure of supply air, p sd =P ai -p sv R d ——Gas constant of dry air, value is 287.14, J / (kg·K); R v ——The gas constant of water vapor is 461.53, J / (kg·K); T s ——The dry bulb temperature of the supply air is θ s Thermodynamic temperature value corresponding to ℃, K, T s =θ s +273.

15.

5. The method for designing indoor air parameters of a spent fuel pool ventilation system according to any one of claims 1 to 4, characterized in that: Also includes: S3: Obtaining an input value of indoor air relative humidity of the spent fuel pool, wherein the input value of indoor air relative humidity is an assumed initial value of indoor air relative humidity or a corrected value of indoor air relative humidity obtained in step S4; S4: Calculate the calculated value of the indoor air relative humidity after the water surface of the spent fuel pool evaporates according to the indoor air relative humidity input value and the indoor air temperature design value output in step S2, then calculate the absolute value of the difference between the calculated value of the indoor air relative humidity and the input value of the indoor air relative humidity, and determine whether the absolute value is greater than a second set threshold value. If so, correct the input value of the indoor air relative humidity to obtain a corrected value of the indoor air relative humidity, and return to step S3. If not, output the calculated value of the indoor air relative humidity as the design value of the indoor air relative humidity.

6. The method for designing indoor air parameters of the spent fuel pool ventilation system according to claim 5, characterized in that: In step S4, the specific process of calculating the calculated value of the indoor air relative humidity according to the indoor air relative humidity input value and the indoor air temperature design value obtained in step S2 is as follows: S4.1: Calculate the evaporation coefficient E of the pool surface using formula (11) w : Where: E w —Evaporation coefficient of the pool surface, kg / (m 2 s); v—air velocity at a height of 0.5m to 1.0m above the pool surface, m / s; p" w —air saturated water vapor pressure corresponding to water temperature, Pa; —Water vapor pressure of indoor air near the water surface, Pa, ——Input value of indoor air relative humidity; ——The design value of indoor air temperature is θ i Saturated water vapor pressure at ℃; S4.2: Evaporation coefficient E of the pool surface calculated according to formula (11) w , use formula (12) to calculate the water surface evaporation Q w : Q w =E w A w (12) Where: Q w ——water surface evaporation, kg / s; E w ——Evaporation coefficient of the pool surface, kg / (m 2 s); A w ——Water surface heat dissipation area, m 2 ; S4.3: Calculated water surface evaporation Q according to formula (12) w , use formula (13) to calculate the indoor air humidity x after water surface evaporation i : Where: x i ——The humidity content of indoor air after evaporation from water surface, kg; Q w ——water surface evaporation, kg / s; Q s ——Design value of air supply volume, m 3 / s; ρ s ——Density of supply air, kg / m 3 ; x s ——humidity content of supply air, kg; S4.4: The humidity x of the indoor air after the water evaporates, calculated according to formula (13) i , use formula (14) to calculate the relative humidity of indoor air after water surface evaporation ——Relative humidity of indoor air after evaporation of water surface; x i ——The humidity content of indoor air after evaporation from water surface, kg; p ai ——Indoor atmospheric pressure, Pa, summer environmental conditions are 100430Pa~100480Pa; winter environmental conditions are 102130Pa~102180Pa; ——The design value of indoor air temperature is θ i Saturated water vapor pressure at ℃.

7. A design device for indoor air parameters of a spent fuel pool ventilation system, characterized in that: include: A first acquisition module and a first processing module, The first acquisition module is used to obtain an input value of the indoor air temperature of the spent fuel pool hall, wherein the input value of the indoor air temperature is an assumed initial value of the indoor air temperature or a corrected value of the indoor air temperature input by the first processing module; The first processing module is connected to the first acquisition module, and is used to calculate the air supply volume calculated value according to the indoor air temperature input value, and then calculate the absolute value of the difference between the air supply volume calculated value and the air supply volume design value, and determine whether the absolute value is greater than a first set threshold value. If so, the indoor air temperature input value is corrected and input into the first acquisition module as the indoor air temperature correction value. If not, the indoor air temperature input value is output as the indoor air temperature design value. The air supply volume is calculated using formula (1): Where: Q s ——air supply volume, m 3 / s; W——heat load in the spent fuel pool hall, W; θ i ——Indoor air temperature input value, °C; θ s ——Supply air dry bulb temperature, °C; ρ s ——Density of supply air, kg / m 3 ; c p ——Specific heat of supply air, J / (kg·℃); The heat load W in the spent fuel pool hall in formula (1) is calculated using formula (2): W=W1+W2+W3 (2) Where: W1——Convection evaporation heat transfer of the water surface of the spent fuel pool, W; W2——radiation heat transfer of the water surface of the spent fuel pool, W; W3——wall heat exchange, W; The convective evaporation heat transfer W1 of the water surface of the spent fuel pool in formula (2) is calculated according to formula (3): W1=α1A w (t w -θ i ) (3) Where: α1——Convection heat transfer coefficient of the spent fuel pool water surface, W / (m 2 ℃), the value is 6.5; A w ——heat dissipation area of ​​the spent fuel pool water surface, m 2 ; t w ——Water temperature of the spent fuel pool surface, °C, 45~55°C; The radiation heat transfer W2 of the water surface of the spent fuel pool in formula (2) is calculated according to formula (4): W2=σEA w [(t w +273.15) 4 -(θ i +273.15) 4 ] (4) Where: σ——blackbody radiation constant, taken as 5.67×10 -8 W / (m 2 ·K 4 ); E——comprehensive emissivity of radiation heat transfer; The comprehensive emissivity E of radiation heat transfer in formula (4) is calculated according to formula (5): Where: ε w ——The radiation emissivity of the spent fuel pool surface is 0.96; ε wall ——The radiation emissivity of the concrete wall is 0.94; The wall heat transfer W3 in formula (2) is calculated according to formula (6): A wall ——Wall heat dissipation area, m 2 ; α i ——Convection heat transfer coefficient in the spent fuel pool hall, W / (m 2 ℃), the value is 5.0; α e ——Convection heat transfer coefficient outside the spent fuel pool hall, W / (m 2 ℃), the value is 15~25.0; δ wall ——wall thickness, m; λ wall ——Thermal conductivity of the wall, W / (m·℃); θ e ——Outdoor ambient air temperature, ℃.

8. The design device for indoor air parameters of the spent fuel pool ventilation system according to claim 7, characterized in that: Also includes: a second acquisition module and a second processing module, The second acquisition module is used to obtain an input value of indoor air relative humidity of the spent fuel pool, wherein the input value of indoor air relative humidity is an assumed initial value of indoor air relative humidity or a corrected value of indoor air relative humidity input by the second processing module; The second processing module is connected to the first processing module and the second acquisition module respectively, and is used to calculate the calculated value of the indoor air relative humidity after the water surface of the spent fuel pool evaporates according to the indoor air relative humidity input value and the indoor air temperature design value, and then calculate the absolute value of the difference between the calculated value of the indoor air relative humidity and the indoor air relative humidity input value, and determine whether the absolute value is greater than a second set threshold value. If so, the indoor air relative humidity input value is corrected and input into the second acquisition module as the indoor air relative humidity correction value. If not, the indoor air relative humidity calculated value is output as the indoor air relative humidity design value.

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